WO2015099075A1 - 駆動装置 - Google Patents
駆動装置 Download PDFInfo
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- WO2015099075A1 WO2015099075A1 PCT/JP2014/084385 JP2014084385W WO2015099075A1 WO 2015099075 A1 WO2015099075 A1 WO 2015099075A1 JP 2014084385 W JP2014084385 W JP 2014084385W WO 2015099075 A1 WO2015099075 A1 WO 2015099075A1
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- WIPO (PCT)
- Prior art keywords
- rotation
- clutch
- gear
- internal combustion
- combustion engine
- Prior art date
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- 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
- F16H3/724—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 using external powered electric machines
- F16H3/725—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 using external powered electric machines with means to change ratio in the mechanical gearing
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- 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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- 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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
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- 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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
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- B60K6/38—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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 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 driveline clutches
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- B—PERFORMING OPERATIONS; TRANSPORTING
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- 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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 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
- B60K6/365—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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 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 with the gears having orbital motion
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- B—PERFORMING OPERATIONS; TRANSPORTING
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- 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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- 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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
- B60K6/38—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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 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 driveline clutches
- B60K6/387—Actuated clutches, i.e. clutches engaged or disengaged by electric, hydraulic or mechanical actuating means
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- 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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- 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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
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- 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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
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- F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight forward speeds
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
- F16H2200/0086—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising two reverse speeds
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
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- 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
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- 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
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- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/64—Electric machine technologies in electromobility
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- 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
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- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/70—Energy storage systems for electromobility, e.g. batteries
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- 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
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- 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
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- 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
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- Y10S903/00—Hybrid electric vehicles, HEVS
- Y10S903/902—Prime movers comprising electrical and internal combustion motors
- Y10S903/903—Prime movers comprising electrical and internal combustion motors having energy storing means, e.g. battery, capacitor
- Y10S903/904—Component specially adapted for hev
- Y10S903/909—Gearing
- Y10S903/91—Orbital, e.g. planetary gears
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- 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
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
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- Y10S903/902—Prime movers comprising electrical and internal combustion motors
- Y10S903/903—Prime movers comprising electrical and internal combustion motors having energy storing means, e.g. battery, capacitor
- Y10S903/904—Component specially adapted for hev
- Y10S903/912—Drive line clutch
- Y10S903/913—One way
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- 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
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- Y10S903/00—Hybrid electric vehicles, HEVS
- Y10S903/902—Prime movers comprising electrical and internal combustion motors
- Y10S903/903—Prime movers comprising electrical and internal combustion motors having energy storing means, e.g. battery, capacitor
- Y10S903/904—Component specially adapted for hev
- Y10S903/912—Drive line clutch
- Y10S903/914—Actuated, e.g. engaged or disengaged by electrical, hydraulic or mechanical means
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- 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
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S903/00—Hybrid electric vehicles, HEVS
- Y10S903/902—Prime movers comprising electrical and internal combustion motors
- Y10S903/903—Prime movers comprising electrical and internal combustion motors having energy storing means, e.g. battery, capacitor
- Y10S903/904—Component specially adapted for hev
- Y10S903/915—Specific drive or transmission adapted for hev
- Y10S903/917—Specific drive or transmission adapted for hev with transmission for changing gear ratio
- Y10S903/919—Stepped shift
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- 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
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S903/00—Hybrid electric vehicles, HEVS
- Y10S903/902—Prime movers comprising electrical and internal combustion motors
- Y10S903/903—Prime movers comprising electrical and internal combustion motors having energy storing means, e.g. battery, capacitor
- Y10S903/951—Assembly or relative location of components
Definitions
- the present invention relates to a drive device mounted on a vehicle or the like, and more particularly to a drive device that transmits rotation of at least one of a rotating electrical machine and an internal combustion engine to an oil pump.
- a rotating electrical machine (motor / generator) drive-coupled to an input shaft of a transmission mechanism is connected to a part of a general automatic transmission starter (for example, a torque converter).
- a general automatic transmission starter for example, a torque converter.
- an engine connecting clutch (starting clutch) that engages and disengages (engages or disengages) the engine connecting shaft that is drivingly connected to the internal combustion engine and the input shaft of the speed change mechanism.
- Such a drive device has two power transmission paths, a power transmission path for transmitting the rotation of the motor to the oil pump and a power transmission path for transmitting the rotation of the engine to the oil pump.
- a power transmission path for transmitting the rotation of the motor to the oil pump and a power transmission path for transmitting the rotation of the engine to the oil pump.
- Patent Document 1 There has been proposed a configuration in which rotation of at least one of a motor and an engine is transmitted to an oil pump by interposing a one-way clutch (see Patent Document 1).
- a clutch drum connected to the rotor of the motor and splined to the outer friction plate of the starting clutch, and the input shaft of the speed change mechanism (and further To the wheel).
- a flange-like carrier and a damper are interposed between the clutch drum and the input shaft, so that the rotor and the input shaft rotate integrally.
- a bearing is usually interposed between the carrier and the stepped planetary gear. Since the durability required for the bearing is determined by the dynamic load acting, if the dynamic load acting on the bearing can be reduced, the durability required for the bearing can be reduced. By reducing the durability required for the bearing, the bearing itself can be reduced in size and the number of stepped planetary gears can be reduced, and the drive device can be reduced in size and weight and cost can be reduced. It is desired to reduce the dynamic load.
- This drive device (1) is a drive device (1) having a rotating electrical machine (3) that is drivingly connected to wheels.
- one rotation transmission member is the pinion (64)
- the other rotation transmission member is the pinion (64).
- FIG. 5 is a schematic diagram showing a hybrid vehicle, where (a) is a case where a ring gear circumscribing a pinion is applied, (b) is a case where an oil pump and its rotation transmission mechanism are in a transmission mechanism, and (c) is a first one-way clutch. And the second one-way clutch are arranged side by side in the axial direction.
- the hybrid drive device 1 according to the first embodiment will be described with reference to FIGS. 1 to 3.
- the drive device according to the present embodiment is suitable for being mounted on a vehicle such as an FF (front engine / front drive) type, for example, and the horizontal direction in FIGS. 1 and 3 is the actual vehicle mounted state.
- the left-right direction or the left-right reverse direction
- the right side in the figure, which is the drive source side of the engine or the like is referred to as “front side”
- the left side in the figure is referred to as “rear side”.
- the drive connection refers to a state in which the rotating elements are connected so as to be able to transmit a driving force, and the rotating elements are connected so as to rotate integrally, or the rotating elements are connected via a clutch or the like.
- the transmission mechanism is an eight-speed automatic transmission, but is not limited to this.
- the automatic transmission is indicated by a skeleton.
- a hybrid vehicle (hereinafter simply referred to as “vehicle”) 100 includes a rotating electrical machine (motor / generator) 3 in addition to the internal combustion engine 2 as a drive source.
- a drive device 1 constituting a power train is disposed between a transmission mechanism L provided on a power transmission path L between the internal combustion engine 2 and the wheels, and between the transmission mechanism 7 and the internal combustion engine 2. 2, and an input portion 9 to which power from 2 is input, and a connection portion 14 that connects the input portion 9 and the internal combustion engine 2 while absorbing pulsation of the internal combustion engine 2.
- the internal combustion engine 2, the input unit 9, and the speed change mechanism 7 are arranged in this order on the same axis in the axial direction. That is, a motor / generator 3, a carrier 60, and a pinion 64 described later are arranged in a region between the internal combustion engine 2 and the transmission mechanism 7.
- the connecting portion 14 is provided with a damper 12 connected via a drive plate 11 to the crankshaft 2a of the internal combustion engine 2 that is drivingly connected to the wheel.
- the damper 12 is an input member as the input portion 9. However, it is connected to an engine connecting shaft 13. That is, the engine connecting shaft 13 is drivingly connected to the internal combustion engine 2 via the damper 12.
- the drive device 1 includes an engine connection shaft 13 as an input member that is drivingly connected to the internal combustion engine 2.
- the input unit 9 is drivingly connected to a clutch (engine connection clutch) K0 for connecting and disconnecting (enabling engagement) power transmission between the engine connecting shaft 13 and the input shaft 15 of the speed change mechanism 7 and a clutch drum 50.
- the motor / generator (rotary electric machine) 3 and the damper 16 are configured.
- the motor / generator (hereinafter simply referred to as “motor”) 3 includes a rotor 4 coupled to the clutch drum 50 and a stator 5 disposed to face the outer side in the radial direction of the rotor 4.
- the engine connecting shaft 13 is disposed on the same axis.
- the clutch K0 is constituted by a multi-plate clutch in which a plurality of friction plates, that is, an inner friction plate 17 and an outer friction plate 19 are accommodated in an internal space of the clutch drum 50. And is connected to the input shaft 15 of the speed change mechanism 7 through a drive. That is, the clutch K0 has the inner friction plates 17 drivingly connected to the transmission path L 1 of the internal combustion engine side of the transmission path L, and the outer friction plates 19 drivingly connected to the transmission path L 2 on the wheel side and with that, the clutch drum 50 is also drivingly connected to transmission path L 2 on the wheel side. Therefore, the clutch K0 can freely connect or release the internal combustion engine 2 and the transmission mechanism 7.
- a damper 16 is also provided between the motor 3 and the speed change mechanism 7. The vibrations of the internal combustion engine 2 are absorbed by the two dampers 12 and 16.
- the transmission mechanism 7 includes an input shaft 15 as an output member that is drivingly connected to the wheels. That is, the drive device 1 includes an input shaft 15 as an output member that is drivingly connected to the wheels.
- the speed change mechanism 7 includes a planetary gear (deceleration planetary gear) DP and a speed change planetary gear unit (planetary gear set) PU.
- the planetary gear DP includes a first sun gear S1, a first carrier CR1, and a first ring gear R1, and the first carrier CR1 and the pinion P2 and the first ring gear meshing with the first sun gear S1. This is a so-called double pinion planetary gear that has pinions P1 meshing with R1 in mesh with each other.
- the planetary gear unit PU has a second sun gear S2, a third sun gear S3, a second carrier CR2, and a second ring gear R2 as four rotating elements, and the second carrier CR2
- the rotation of the first sun gear S1 of the planetary gear DP is fixed with respect to the case 6.
- the first carrier CR1 is connected to the input shaft 15 so as to rotate in the same rotation as the rotation of the input shaft 15 (hereinafter referred to as “input rotation”), and the fourth clutch C ⁇ . 4 is connected. Further, the first ring gear R1 is decelerated by the input rotation being reduced by the fixed first sun gear S1 and the input first carrier CR1, and the first clutch C-1 And the third clutch C-3.
- the third sun gear S3 of the planetary gear unit PU is connected to the first brake B-1 and can be fixed to the case 6, and the fourth clutch C-4 and the third clutch Connected to C-3, the input rotation of the first carrier CR1 via the fourth clutch C-4, the reduced rotation of the first ring gear R1 via the third clutch C-3, Each can be entered freely.
- the second sun gear S2 is connected to the first clutch C-1, so that the reduced rotation of the first ring gear R1 can be input.
- the second carrier CR2 is connected to the second clutch C-2 to which the rotation of the input shaft 15 is input, and the input rotation can be freely input through the second clutch C-2.
- it is connected to the second brake B-2, and the rotation can be fixed via the second brake B-2.
- the second ring gear R2 is connected to a counter gear 8 that is rotatably supported with respect to a center support member fixed to the case 6.
- the counter gear 8 is connected to the left and right wheels via a differential gear or the like.
- the speed change mechanism 7 configured as described above includes the first to fourth clutches C-1 to C-4 and the first and second brakes B-1 and B-2 shown in the skeleton diagram of FIG. 2, the first forward speed (1st) to the eighth forward speed (8th), and the first reverse speed (Rev1) to the second reverse speed (Rev2) Is achieved.
- a plurality of friction engagement elements such as the clutches C-1 to C-4 and the brakes B-1 and B-2 in the transmission mechanism 7 are electronically controlled by a control unit (ECU) 20 as described above. Engagement / release is controlled by each engagement pressure supplied from the driven hydraulic control device 21.
- the clutch K0 is also controlled to be engaged / released by the engagement pressure supplied from the hydraulic control device 21.
- the hydraulic control device 21 also generates lubricating pressure for supplying lubricating oil for lubricating each part, and the inside of the speed change mechanism 7 and the inside of the input unit 9, particularly the inner friction plate 17 and the outer friction plate 19 of the clutch K0.
- the motor 3 is lubricated and cooled.
- the speed change mechanism 7 may be a stepped speed change mechanism that achieves, for example, forward 3 to 7 speeds, a belt type continuously variable transmission, a toroidal type continuously variable transmission, a cone ring type continuously variable transmission, or the like.
- a continuously variable transmission mechanism such as a transmission may be used, that is, any transmission mechanism can be applied to the drive device 1 of the present embodiment.
- the connection portion 14, the input portion 9 having the clutch K 0 and the motor 3, and the speed change mechanism 7 are sequentially arranged from the internal combustion engine 2 side to the wheel side.
- the control unit 20 controls the hydraulic control device 21 to engage the clutch K 0, and the motor 3 that is drivingly connected to the transmission path L 2 on the wheel side.
- the EV travel to travel only by the driving force, to release the clutch K0, so that the disconnect the transmission path L 2 of the transmission path L 1 and the wheel side of the internal combustion engine 2 side.
- a housing case 26 fixed to a transmission case (not shown) that houses the speed change mechanism 7, a clutch K0 and a motor 3, and a damper 16 described later are housed.
- the clutch K0 and the motor 3 are housed.
- the enclosed space of the housing case 26 is closed by a partition wall (case wall) 27 integrally attached to the housing case 26 on the internal combustion engine 2 side (one side) in the axial direction from the motor 3 and the clutch K0.
- a closed space partitioned from the connecting portion 14 is formed.
- the transmission case, the housing case 26 and the partition wall 27 constitute the case 6 described above.
- the engine coupling shaft 13 connected to the internal combustion engine 2 via the damper 12 of the connecting portion 14 and the input shaft 15 of the speed change mechanism 7 are arranged so as to coincide with each other.
- the engine connecting shaft 13 is located at the end opposite to the internal combustion engine 2 and is formed with a concave portion 13b whose center portion is recessed toward the internal combustion engine 2 side.
- the tip of the input shaft 15 on the internal combustion engine 2 side is formed. Is inserted into the recess 13b. That is, the engine connecting shaft 13 and the input shaft 15 form a single shaft shape in which the tip of the input shaft 15 is fitted in the recess 13 b and is relatively rotatable, and the outer peripheral surface of the input shaft 15 is circumferential.
- the outer peripheral surface of the input shaft 15 and the recess 13b of the engine connecting shaft 13 are sealed by a seal ring (seal member) d1 embedded in the direction.
- the engine connecting shaft 13 is rotatably supported with respect to the partition wall 27 by an angular ball bearing 90, a cylindrical portion 51d of the rotor hub 51, and a needle bearing b31. Details of the support structure of the rotor hub 51 for the partition wall 27 will be described later.
- the input shaft 15 is rotatably supported with respect to a sleeve member 25 disposed on the inner peripheral side of a partition wall 24 fixed to a mission case (not shown).
- a flange portion 13a and a sleeve portion 13c which are engine rotation transmission members, are integrally formed at the rear end portion on the transmission mechanism 7 side of the engine connecting shaft 13, and are formed on the outer peripheral surfaces of the flange portion 13a and the sleeve portion 13c.
- a clutch hub 49 to which a plurality of inner friction plates 17 of the clutch K0 are spline-engaged is fixed, and a hydraulic servo 40 to be described later is disposed. That is, the inner friction plate 17 is drivingly connected to the engine connecting shaft 13.
- the clutch K0 roughly includes the plurality of inner friction plates 17, the outer friction plates 19 arranged alternately with the inner friction plates 17, the clutch drum 50 with which the outer friction plates 19 are spline-engaged, and the plurality of inner friction plates 19.
- the clutch hub 49 which is a support member for supporting the friction plate 17, and a hydraulic servo 40 for engaging / disengaging (engaging or releasing) the inner friction plate 17 and the outer friction plate 19 are provided. .
- At least a part of the outer friction plate 19 and the inner friction plate 17 which are a plurality of friction plates is positioned so as to overlap the rotor 4 of the motor 3 when viewed from the radial direction.
- the entire outer friction plate 19 and the inner friction plate 17 are disposed radially inward of the rotor 4 so as to overlap the rotor 4 of the motor 3 when viewed from the radial direction.
- the clutch K0 is arranged so as to be aligned in the axial direction in the order of the partition wall 27, the rotor hub 51, at least a part of the outer friction plate 19 and the inner friction plate 17, and the damper 16.
- the clutch drum 50 is connected to a rotor hub 51 that holds the rotor 4 so as to be capable of rotational transmission, and is also connected to a damper 16 described later so as to be capable of rotational transmission. That is, the clutch drum 50 has a spline portion 50a on the outer peripheral surface that is spline-engaged with a spline portion 51c formed on the inner peripheral surface of a drum-shaped clamping portion (rotor holding portion) 51b of the rotor hub 51 described later. . Then, the rotor hub 51 and the clutch drum 50 are connected to each other so as to be able to transmit the rotation. The connecting portion between the clutch drum 50 and the damper 16 will be described later.
- the damper 16 is connected to the input shaft 15 of the speed change mechanism 7 so as to be able to transmit rotation, as will be described later. Therefore, the damper 16 is disposed on a member that connects the rotor 4 and the speed change mechanism 7. A plurality of outer friction plates 19 are splined inside the clutch drum 50. Accordingly, the outer friction plate 19 is drivingly connected to the input shaft 15 via the clutch drum 50 and the damper 16.
- the clutch hub 49 includes a drum-shaped drum portion 49a in which a plurality of inner friction plates 17 are spline-engaged, and an extending portion 49b extending radially inward from the end portion of the drum portion 49a. And the inner peripheral surface of the extension part 49b is being fixed to the outer peripheral surface of the sleeve part 13c by welding.
- the hydraulic servo 40 is disposed so as to be movable in the axial direction with respect to the cylinder portion 41 constituting the hydraulic cylinder 42 and the hydraulic cylinder 42, and the tip portion is disposed opposite to the inner friction plate 17 (or the outer friction plate 19).
- the hydraulic cylinder 42 includes a cylinder portion 41 and a tip side portion of an inner cylindrical portion 44c constituting a return portion 44 described later.
- the cylinder portion 41 is fitted on the outer peripheral surface of the flange portion 13a of the engine connecting shaft 13 via a seal ring 41a, and is positioned in the axial direction with respect to the flange portion 13a by a snap ring 41b.
- the return portion 44 has a plurality of convex portions 44a formed at a plurality of locations in the circumferential direction of the connecting portion 44d, which will be described later, abutting against the side surface of the clutch hub 49 fixed to the sleeve portion 13c of the engine connecting shaft 13, thereby 49 in the axial direction. Therefore, the cylinder portion 41 and the return portion 44 are positioned in the axial direction with respect to each other via the flange portion 13a, the sleeve portion 13c, and the clutch hub 49.
- the return portion 44 includes an outer cylindrical portion 44b, an inner cylindrical portion 44c, and a connecting portion 44d that connects one end portions of the outer cylindrical portion 44b and the inner cylindrical portion 44c so that the piston 43 side opens. Further, it is disposed between the clutch hub 49 and the sleeve portion 13c. A plurality of convex portions 44a formed on the connecting portion 44d are brought into contact with the extending portion 49b of the clutch hub 49, and the return spring 45 is elastically compressed between the connecting portion 44d and the piston 43. is doing. Accordingly, the connecting portion 44d corresponds to a return plate. Further, by causing the plurality of convex portions 44 a to contact the clutch hub 49, a gap is formed between the connecting portion 44 d and the extending portion 49 b of the clutch hub 49.
- the inner cylindrical portion 44c is disposed with a gap from the outer peripheral surface of the sleeve portion 13c.
- a convex portion 13d is formed on the outer peripheral surface of the end of the sleeve portion 13c on the flange portion 13a side, and the tip end portion of the inner cylindrical portion 44c is externally fitted to the convex portion 13d.
- a gap is formed between the inner peripheral surface and the outer peripheral surface excluding the convex portion 13d of the sleeve portion 13c facing the inner peripheral surface.
- the outer peripheral surface of the inner cylindrical portion 44c is a sliding portion 43a on which the piston 43 slides, and the inner peripheral surface of the outer cylindrical portion 44b is also a sliding portion 43b on which the piston 43 slides.
- the piston 43 slides with the sliding portions 43a and 43b via a seal ring.
- the hydraulic oil chamber 46 is moved between the hydraulic cylinder 42 constituted by the cylinder portion 41 and the tip side portion of the inner cylindrical portion 44c and the piston 43 from the outer cylindrical portion 44b, the inner cylindrical portion 44c and the connecting portion 44d.
- a cancel oil chamber 47 for canceling centrifugal hydraulic pressure is formed between the return portion 44 and the piston 43, respectively.
- the outer cylindrical portion 44b is disposed with a gap from the inner peripheral surface of the drum portion 49a of the clutch hub 49.
- a convex portion 49c is formed on the inner peripheral surface of the front end portion of the drum portion 49a, and the front end portion of the outer cylindrical portion 44b is fitted into the convex portion 49c so that the inner peripheral surface of the outer cylindrical portion 44b and the inner peripheral surface thereof are fitted.
- a gap is formed between the peripheral surface and the inner peripheral surface excluding the convex portion 49c of the drum portion 49a facing the peripheral surface.
- the gap between the inner cylindrical portion 44c and the sleeve portion 13c, the gap between the connecting portion 44d and the extending portion 49b, and the gap between the outer cylindrical portion 44b and the drum portion 49a communicate with each other, thereby returning the return portion.
- 44 and an oil passage a ⁇ b> 40 for supplying lubricating oil to the plurality of inner friction plates 17 and the outer friction plates 19 are formed between the hydraulic cylinder 42 and the clutch hub 49.
- the annular stator 5 of the motor 3 is fixed to the outer peripheral side of the clutch K0 and to the inner peripheral side of the housing case 26.
- the stator 5 is configured to include a stator core 5a and coil ends 5b and 5b that are coiled portions of the coil wound around the stator core 5a and project on both axial sides of the stator core 5a.
- an annular rotor 4 of the motor 3 is disposed oppositely with a predetermined gap.
- the rotor hub 51 that holds the rotor 4 includes a drum-like clamping part (rotor holding part) 51b that crimps and clamps the rotor core 4a of the rotor 4, a flange-like support part 51a that supports the clamping part 51b, and the support part A sleeve-shaped cylindrical portion 51d connected to the inner peripheral side of 51a is configured, and the sandwiching portion 51b and the support portion 51a are integrated, and the support portion 51a and the cylindrical portion 51d are welded together.
- an integral rotor hub 51 is formed as a whole.
- the cylindrical portion 51d is rotatably supported by an angular ball bearing (rotor bearing) 90 with respect to the partition wall 27 integrally attached to the housing case 26, and is provided between the flange portion 13a of the engine connecting shaft 13. Also supported by the thrust bearing b2 in the axial direction.
- a thrust bearing b3 is provided between the flange portion 13a of the engine connecting shaft 13 and a connecting member 63 described later, and a carrier (second rotation transmitting member, which connects the connecting member 63, a damper 16 described later and the input shaft 15).
- a thrust bearing b4 is provided between the damper connecting portion 60) and a thrust bearing b5 is provided between the carrier 60 and the sleeve member 25, and each member is positioned in the axial direction.
- the angular ball bearing 90 is composed of two ball bearings b11 and b12 fitted on the outer peripheral side of the cylindrical portion 51d.
- Inner races 91a and 91b of the ball bearings b11 and b12 are respectively provided with nuts (fastening members) 92 that are screwed into male threads on the outer peripheral side of the cylindrical portion 51d from the internal combustion engine 2 side in the axial direction toward the transmission mechanism 7 side.
- the rotor hub 51 is fastened to the rotor hub 51 by being sandwiched between the inner surface of the support portion 51 a of the rotor hub 51.
- each of the ball bearings b11 and b12 is held on the partition wall 27 by sandwiching the support member 28 of the partition wall 27 between the projection 93a provided on the internal combustion engine 2 side in the axial direction and the snap ring 94. It is fixed against.
- the rotor hub 51 and the rotor 4 are rotatably supported with respect to the partition wall 27 by the angular ball bearing 90 being fastened by the nut 92.
- the support member 28 that supports the angular ball bearing 90 is disposed so as to cover the outer peripheral side of the angular ball bearing 90, and the stator is disposed on the outer peripheral side of the support member 28 so as to face the rotor 31.
- a (detection coil) 32 is fixed to a cylindrical pedestal 27 a protruding from the partition wall 27 with a bolt 33.
- the rotor 31 is fixed to the inner peripheral side of the rotor hub 51 that supports the rotor 4 of the motor 3. Therefore, the rotor 31 and the stator 32 constitute a resolver 30 that detects the rotation state of the motor 3.
- the clutch drum 50 connected to the rotor hub 51 so as to be capable of rotational transmission includes a spline portion 50a spline-engaged with the rotor hub 51 formed on at least a part of the outer peripheral surface in the axial direction, and the damper 16 side. It has a bent portion 50b that is bent so that the end portion is located radially outside of the spline portion 50a at a part of the circumferential direction.
- a comb-like clutch-side engagement portion 50c is formed at a part in the circumferential direction at the tip of the bent portion 50b.
- the damper 16 is arranged radially inward of the stator 5 so that at least a part thereof overlaps with the coil end 5 b of the stator 5 when viewed from the radial direction of the motor 3.
- the dampers 16 are arranged so as to be arranged in the axial direction in the order of the partition wall 27, the rotor hub 51, the outer friction plate 19 and the inner friction plate 17 of the clutch K0, and at least a part of the spring 163 described below.
- Such a damper 16 is disposed in an annular damper shell 160, a disk-shaped driven plate 162 having a plurality of openings 161 in the circumferential direction, and a plurality of openings 161, respectively.
- the damper shell 160 has a pair of shell members 160 a and 160 b arranged so as to sandwich the driven plate 162.
- the shell members 160a and 160b have notches 164a and 165a at positions corresponding to the openings 161 of the driven plate 162, respectively, and holding portions 164 and 165 formed so as to swell in the axial direction.
- each spring 163 is hold
- At least one of the pair of shell members 160a and 160b (in the example shown, the shell member 160a on the transmission mechanism 7 side) is engaged with the clutch-side engagement portion 50c at a part of the outer circumferential edge.
- a comb-like damper-side engaging portion 166 that can transmit the rotation of the clutch drum 50 is formed.
- the damper side engaging portion 166 is prevented from coming off in the axial direction with respect to the clutch side engaging portion 50c by the snap ring 167 in a state in which the damper side engaging portion 166 is engaged with the clutch side engaging portion 50c.
- the bent portion 50 b of the clutch drum 50 is bent along the holding portion 165 of the shell member 160 b on the internal combustion engine 2 side of the damper shell 160.
- the pair of shell members 160a and 160b are joined by a rivet 168 on the other side in the circumferential direction, that is, on the radially outer side of the damper side engaging portion 166 at the circumferential position where the damper side engaging portion 166 is not formed. ing.
- the clutch drum 50 and the damper 16 transmit rotation on the inside in the radial direction of the rivet 168 that connects the pair of shell members 160a and 160b.
- rotation transmission is performed by the clutch side engaging portion 50c and the damper side engaging portion 166 that are formed in a comb shape.
- the damper 16 is connected to the input shaft 15 by a carrier 60 so as to be able to transmit rotation.
- the carrier 60 includes a disk-shaped disk portion (damper support portion) 61 that supports the damper 16 on the radially inner side of the damper 16, and a disk portion 61 that extends in the axial direction from the inner peripheral edge of the disk portion 61. And a cylindrical sleeve portion 62 formed integrally.
- the disc portion 61 has the damper 16 fitted on the outer peripheral surface thereof, and the inner peripheral surface of the driven plate 162 is fixed by welding or the like.
- the damper 16 is disposed such that the axial center position is offset from the axial center position of the disc portion 61 toward the connecting member 63 described later.
- the sleeve portion 62 is in spline engagement with the input shaft 15.
- the rotation output from the driven plate 162 of the damper 16 is transmitted to the input shaft 15 via the carrier 60.
- the rotor 4 of the motor 3 is drivingly connected to the input shaft 15 of the speed change mechanism 7 via the rotor hub 51, the clutch drum 50, the damper 16 and the carrier 60. That is, the carrier 60 is arranged in the power transmission path from the motor 3 to the wheels.
- the internal combustion engine 2 is drivingly connected to the input shaft 15 via the engine connecting shaft 13, the clutch K 0, the damper 16 and the carrier 60.
- a one-way clutch portion (rotation selection portion) F is disposed so as to be interposed between the sleeve portion 13 c of the engine connecting shaft 13 and the sleeve portion 62 of the carrier 60. Yes.
- the higher (not lower) rotation of the motor 3 and the internal combustion engine 2 is output from a connecting member (tubular member) 63 as an output member of the one-way clutch portion F.
- the one-way clutches F1 and F2 and the connecting member 63 constituting the one-way clutch portion F are disposed on the clutch K0 side with respect to the disc portion 61.
- the connecting member 63 is drivingly connected to the oil pump 80 as will be described later.
- a first one-way clutch F1 and needle bearings b21 and b22 are arranged at both ends between a sleeve portion 13c, which is an engine-side cylindrical portion of the engine rotation transmission member, and the connecting member 63. Furthermore, at least a part of the first one-way clutch F1 overlaps between the sleeve portion 62, which is the rotor-side cylindrical portion of the rotor rotation transmission member, and the connecting member 63 when viewed from the radial direction (this embodiment). , Approximately the same position in the axial direction), the second one-way clutch F2 and needle bearings b23 and b24 are arranged at both ends thereof.
- the sleeve portion 62 has a spline portion 62a that is spline-engaged with the input shaft 15 of the speed change mechanism 7 on the inner peripheral surface, and a cylindrical surface 62b that is in contact with the inner race of the second one-way clutch F2. Yes. Since the sleeve portion 62 has a certain amount of axial dimension in order to form the spline portion 62a, the second one-way clutch F2 can be efficiently arranged on the outer peripheral surface using this.
- a sleeve portion 13c that is always driven and connected to the internal combustion engine 2 is arranged on the outer peripheral side of the first one-way clutch F1, and an input shaft 15 that is always driven and connected to the motor 3 is arranged on the inner peripheral side of the second one-way clutch F2.
- the first one-way clutch F1 is disengaged when the rotation of the sleeve portion 13c is lower than that of the connecting member 63
- the second one-way clutch F2 is when the rotation of the sleeve portion 62 is lower than that of the connecting member 63. Is disengaged.
- the rotation of the internal combustion engine 2 is transmitted to the sleeve portion 13c by the engine connecting shaft 13, and the rotation of the internal combustion engine 2 is transmitted to the sleeve portion 62 through the rotation of the rotor 4 of the motor 3 and the clutch K0.
- One-way clutches F ⁇ b> 1 and F ⁇ b> 2 transmit the higher rotation (not lower) of the motor 3 and the internal combustion engine 2 to the connecting member 63.
- a clutch K0 is disposed on the radially outer side of the first one-way clutch F1 and the second one-way clutch F2.
- the first friction plates are arranged radially inward of the plurality of friction plates so as to overlap at least part of the inner friction plates 17 and the outer friction plates 19 which are the plurality of friction plates of the clutch K0.
- a one-way clutch F1 and a second one-way clutch F2 are arranged.
- the first one-way clutch F1 and the second one-way clutch F2 are arranged radially inward of the hydraulic servo 40 so as to overlap at least a part of the hydraulic servo 40 when viewed from the radial direction. Is done.
- the first one-way clutch F1 and the second one-way clutch F2 are disposed radially inward of the cancel oil chamber 47 so as to overlap at least a part of the cancel oil chamber 47 when viewed from the radial direction.
- the piston 43 when viewed from the radial direction, the piston 43 is disposed radially outward of the first one-way clutch F1 and the second one-way clutch F2 so as to overlap at least part of the first one-way clutch F1 and the second one-way clutch F2.
- a sliding portion 43 a that slides relative to the hydraulic cylinder 42 is disposed. As described above, the sliding portion 43a is the outer peripheral surface of the inner cylindrical portion 44c of the return portion 44.
- the first one-way clutch F1 and the second one-way clutch F2 It arrange
- the clutch K0, the first one-way clutch F1, and the second one-way clutch F2 are in a space surrounded by the support portion 51a and the clamping portion 51b of the rotor hub 51, the damper 16, and the disc portion 61. Will be placed.
- the partition wall 27, which is a case wall, the support portion 51a of the rotor hub 51, the clutch K0, and the damper 16 are arranged in this order from the internal combustion engine 2 side. For this reason, the damper 16 is not affected by the partition wall 27, and the degree of freedom of installation of the damper 16 can be increased.
- the damper 16 can be damped by securing the stroke amount of the damper 16. It becomes easy to improve the nature.
- the motor 3 is connected to the end of the input shaft 15 of the speed change mechanism 7.
- resonance may occur depending on the number of rotations. .
- resonance may occur at 2500 rpm. For this reason, such a resonance can be suppressed by providing the damper 16 between the motor 3 and the speed change mechanism 7 and increasing the radial dimension of the damper 16.
- a damper 16 is provided between the motor 3 and the speed change mechanism 7 in addition to the damper 12 between the internal combustion engine 2 and the input unit 9.
- the vibrations of the internal combustion engine 2 are absorbed by the two dampers 12 and 16.
- the number of dampers that absorb the vibration of the internal combustion engine 2 is one, there is a possibility that a muffled sound may be generated without completely absorbing this vibration. In this case, it is conceivable to absorb the vibration by slipping the clutch K0. However, if the clutch K0 is slipped in this way, the fuel efficiency is lowered.
- the damper 16 is arranged so that at least a part thereof overlaps with the coil end 5b of the stator 5 when viewed from the radial direction of the motor 3, the axial dimension of the apparatus can be further suppressed.
- the damper shell 160 of the damper 16 can be connected to the clutch drum 50 on the radially inner side of the rivet 168 that joins the pair of shell members 160a and 160b, the radial direction of the clutch side engaging portion 50c of the clutch drum 50 The size can be reduced and the device can be downsized.
- the damper 16 can be brought closer to the rotor 4 in the axial direction. Miniaturization can be achieved.
- through holes 61 a are formed at a plurality of locations in the circumferential direction of the disc portion 61.
- a pinion (first rotation transmission member) 64 is rotatably supported by a needle bearing (bearing) 65 in each through hole 61a. Therefore, the pinion 64 is disposed so as to penetrate the disc portion 61.
- the pinion 64 has a shaft portion 64a that is rotatably supported by a needle bearing 65, and gears 66a and 66b are fixed to both ends of the shaft portion 64a, respectively.
- the pinion 64 includes a shaft portion 64a, a gear (first gear) 66b formed at one end portion of the shaft portion 64a, and a gear (second gear) 66a formed at the other end portion of the shaft portion 64a.
- the shaft portion 64a and the gears 66a and 66b are formed by integrating different members.
- the present invention is not limited to this.
- at least one of the gears 66a and 66b and the shaft portion 64a May be formed integrally with one member.
- a gear (fourth gear) 63 a formed on the outer peripheral surface of the end of the connecting member 63 is connected to the gear 66 a closer to the connecting member 63 than the disc portion 61.
- a gear (third gear) 71a formed on a sprocket 71 for transmitting rotation to the oil pump 80 described below is meshed with the gear 66b on the opposite side of the speed change mechanism 7 from the inner peripheral side. Yes. That is, a plurality of pinions 64 are arranged so as to mesh with each outer periphery of one gear 71a and one gear 63a.
- the oil pump 80 (see FIG. 1) will be described.
- the oil pump 80 is separate from the input shaft 15 of the speed change mechanism 7 which is a first shaft member that can be driven and connected to the internal combustion engine 2 via the clutch K0 and the damper 16, and is a transmission shaft arranged in parallel with the input shaft 15.
- (Drive shaft) 81 is disposed on the transmission mechanism 7 side of the motor 3 and disposed on the outer periphery of the transmission case. That is, the oil pump 80 is provided in the transmission mechanism 7. And it is rotationally driven by the transmission shaft 81 rotating. The rotation of the pinion 64 is transmitted to the transmission shaft 81 by the rotation transmission mechanism 70.
- the rotation transmission mechanism 70 includes sprockets 71 and 72 and a chain 73 that meshes with each of the sprockets 71 and 72, and the rotation of the sprocket 71 is transmitted to the sprocket 72 via the chain 73.
- the sprocket 71 is rotatably supported by the ball bearing 74 on the outer peripheral surface of the sleeve member 25, and the rotation of the connecting member 63 is transmitted through the pinion 64 and the like as described above.
- the sprocket 72 is fixed to the transmission shaft 81, and the transmission shaft 81 rotates together with the sprocket 72.
- the sprockets 71 and 72 and the chain 73 are disposed adjacent to the damper 16 and the disc portion 61 on the transmission mechanism 7 side.
- the central portions of the sprockets 71 and 72 where the swing of the chain 73 increases are adjacent to the damper 16.
- the damper 16 is disposed offset to the connecting member 63 side with respect to the disc portion 61, so that the portion where the swing of the chain 73 increases and the damper 16 do not interfere with each other. Can be arranged with a gap.
- a gap can be secured without moving the rotation transmission mechanism 70 to the speed change mechanism 7 side, an increase in the size of the apparatus can be suppressed.
- the transmission shaft 81 is rotatably supported by the housing case 26 and transmits rotation to the oil pump 80.
- the oil pump 80 is a so-called inscribed gear pump, a drive gear that is drivingly connected to the transmission shaft 81, a driven gear that is meshed with the outer periphery thereof, and a pump body that covers the drive gear and the driven gear from the outer peripheral side. And a pump cover for closing the pump body.
- the first one-way clutch F1 is disengaged when the rotation of the engine connecting shaft 13 (that is, the internal combustion engine 2) becomes lower than the rotation of the connecting member 63, and the engine connecting shaft
- the oil pump 80 is engaged with the internal combustion engine 2 via the pinion 64 and the rotation transmission mechanism 70 and driven by the driving force of the internal combustion engine 2.
- the second one-way clutch F2 is disengaged, and the rotation of the rotor hub 51 is the same as the rotation of the connecting member 63.
- the oil pump 80 is drivingly connected to the motor 3 through the pinion 64 and the rotation transmission mechanism 70 and is driven by the driving force of the motor 3. That is, the oil pump 80 can be drive-coupled via the first one-way clutch F1 and the second one-way clutch F2 so that the rotational speed of the engine coupling shaft 13 (that is, the internal combustion engine 2) or the rotor hub 51 (motor 3) is higher. .
- Such oil pump 80 the clutch is arranged closer to be drivingly connected to the transmission path L 1 of the internal combustion engine 2 side of the K0 clutch K0 also drivingly coupled to transmission path L 2 of the speed change mechanism 7 side than the (Refer to FIG. 1). Further, if the clutch K0 is engaged, since the transmission path L 1 and pathways L 2 is drivingly connected, together with an internal combustion engine 2 and the motor 3 is the same rotation, the oil pump 80 is driven by the rotation Will be.
- the oil pump 80 that is drivingly connected to the engine connecting shaft 13 via the first one-way clutch F1 or is connected to the rotor hub 51 via the second one-way clutch F2 is in the EV traveling state, 3 or by the inertial force of the vehicle via the speed change mechanism 7 in the coasting state (during engine braking) and by the driving force of the motor 3 or the internal combustion engine 2 during the hybrid traveling.
- the vehicle in the coast state (during engine braking), the vehicle is driven by the inertial force of the vehicle via the speed change mechanism 7.
- the first oil pump 80 starts from the state before the clutch K0 is engaged (that is, when the vehicle is stopped). Since the one-way clutch F1 is engaged, it is driven by the driving force of the internal combustion engine 2.
- the engagement pressure of the clutch K ⁇ b> 0 from the hydraulic control device 21 passes through an oil passage a ⁇ b> 11 formed in the axial direction on the input shaft 15 through a portion not shown based on a command of the control unit 20. Supplied.
- the oil passage a11 is closed at the end of the input shaft 15 on the internal combustion engine 2 side.
- the oil passage a11 communicates with the oil passage a13 of the flange portion 13a via a radial oil passage a12 formed through the input shaft 15.
- the oil passage a ⁇ b> 13 communicates with the hydraulic oil chamber 46 of the hydraulic servo 40.
- lubricating oil for lubricating the clutch K0 is supplied through an oil passage a21 formed in the input shaft 15 in the axial direction and different from the oil passage a11 described above.
- the oil passage a21 communicates with the oil passage a23 of the sleeve portion 13c through a space in which the radial oil passage a22 formed through the input shaft 15 and the thrust bearing b3 exist.
- the oil passage a40 is formed between the return portion 44 and the hydraulic cylinder 42 and the clutch hub 49, and the oil passage a23 communicates with the oil passage a40.
- the lubricating oil splashed from the oil passage a22 is guided to the oil passage a40 through the oil passage 23a while lubricating the thrust bearing b3, and from a plurality of through holes 49d formed in the drum portion 49a of the clutch hub 49.
- a plurality of inner friction plates 17 and outer friction plates 19 are supplied.
- An oil passage a41 that connects the oil passage a40 and the cancel oil chamber 47 is formed in a part of the inner cylindrical portion 44c. Therefore, the lubricating oil supplied through the oil passages a21 to a23 as described above is also led to the cancel oil chamber 47.
- These oil passages a21 to a23 supply oil to the clutch K0 from the radially inner side of the clutch K0, that is, the lubricating oil is scattered from the radially inner side to the outer side of the inner friction plate 17 and the outer friction plate 19.
- the lubricating oil flowing from the through hole 49d of the clutch hub 49 is lubricated and cooled between the inner friction plate 17 and the outer friction plate 19, and is collected in an oil pan (not shown).
- the clutch K0 is opened to the atmosphere with respect to the housing case 26 without the inner friction plate 17 and the outer friction plate 19 being oil-tight (non-oil-tight), and the inner friction plate 17 and the outer friction plate
- This is a wet multi-plate clutch in which the plate 19 is disposed in the air.
- Part of the lubricating oil scattered from the oil passage a22 is a needle bearing b22, a first one-way clutch F1, a needle bearing b21, a needle bearing b24, a second one-way clutch F2, a needle bearing b23, and a thrust bearing. Also guided to b4, they are lubricated.
- lubricating oil for lubricating the motor 3 is supplied to an oil passage a31 formed in the input shaft 15 in the axial direction in parallel with the oil passage a21.
- the oil passage a31 is open at the end of the input shaft 15 on the internal combustion engine 2 side, and passes through an oil passage a32 of the engine connecting shaft 13 and an oil passage a33 formed through the oil passage a32 in a radial direction. It is discharged to the inner peripheral side of the cylindrical portion 51d.
- the lubricating oil discharged to the inner peripheral side of the cylindrical portion 51d is guided to the angular ball bearing 90 and lubricates it.
- the lubricating oil that has lubricated the angular ball bearing 90 in this way is guided to the inside of the rotor hub 51.
- the lubricating oil guided to the inside of the rotor hub 51 cools the motor 3 through an oil passage a34 formed in the rotor hub 51. That is, in the present embodiment, the motor 3 is cooled by oil that lubricates the inside of the housing case 26.
- a seal ring 27b is provided between the partition wall 27 and the engine connecting shaft 13 to prevent the lubricating oil introduced as described above from leaking to the internal combustion engine 2 side of the partition wall 27.
- the second one-way clutch F2 is disposed so as to overlap at least a part of the first one-way clutch F1 when viewed from the radial direction of the motor 3, and the first one-way clutch F1 and Since the second one-way clutch F2 is arranged so as to overlap at least a part of the plurality of inner friction plates 17 and the outer friction plates 19 of the clutch K0, it has a structure having two one-way clutches F1, F2, Axial dimension can be reduced.
- the first one-way clutch F1 and the second one-way clutch F2 are arranged so as to overlap at least a part of the hydraulic servo 40 when viewed from the radial direction of the motor 3.
- the first one-way clutch F1 and the second one-way clutch F2 are arranged so as to overlap at least a part of the cancel oil chamber 47, the axial dimension of the apparatus can be further suppressed.
- the sliding portion 43a of the piston 43 is disposed radially outward of the first one-way clutch F1 and the second one-way clutch F2, the axial direction is used to ensure the moving distance of the piston 43.
- the sliding portion 43a which requires a certain length, can be arranged by effectively using the radially outer space of the first one-way clutch F1 and the second one-way clutch F2, and the axial dimension of the apparatus can be further suppressed.
- the sliding part 43a is arrange
- the space of the sleeve part 13c in the radial direction outer side The sliding portion 43a can be arranged by effectively utilizing the above, and the axial dimension of the apparatus can be further suppressed.
- the sleeve portion 13c which is the engine-side cylindrical portion, constitutes the outer race of the first one-way clutch F1 and the needle bearings b21 and b22.
- the sleeve portion 13c has a shape that is long in the axial direction, and a space that is long in the axial direction also exists radially outward.
- an inner cylindrical portion 44c having a sliding portion 43a is arranged on the outer side in the radial direction of the sleeve portion 13c.
- the sliding portion 43a which requires a certain length in the axial direction, radially outward of the sleeve portion 13c, the space radially outward of the sleeve portion 13c that is long in the axial direction can be used effectively.
- the axial distance of the sliding portion 43a can be secured.
- An oil passage a40 for supplying lubricating oil to the plurality of inner friction plates 17 and the outer friction plates 19 is formed between the return portion 44 and the hydraulic cylinder 42 that form the cancel oil chamber 47 and the clutch hub 49. Therefore, it is possible to provide an oil passage a40 that supplies lubricating oil to the plurality of inner friction plates 17 and the outer friction plates 19 while suppressing the axial dimension of the apparatus. That is, when such an oil passage is different from the above, the axial dimension of the apparatus may be increased in order to form this passage. On the other hand, the axial dimension of the apparatus can be suppressed by forming the oil passage a40 by utilizing the gap between the cancel oil chamber 47 and the clutch hub 49 as in the present embodiment.
- the oil pump 80 is connected to the engine connecting shaft 13 that is drivingly connected to the internal combustion engine 2, the first one-way clutch F 1, the connecting member 63, the pinion 64, the rotation transmission mechanism 70, and the transmission shaft.
- the oil pump 80 can be driven by the driving force of the internal combustion engine 2 because it is arranged so as to be drive-coupled via the engine 81.
- the vehicle starts with the driving force of the internal combustion engine 2 while engaging the clutch K0.
- the lubricating oil can be sufficiently supplied to the inner friction plate 17 and the outer friction plate 19 of the clutch K0.
- a mechanism including a sprocket and a chain is used as a rotation transmission mechanism that transmits drive from the engine connecting shaft 13 to the transmission shaft 81 of the oil pump 80.
- a mechanism including a plurality of gears is used.
- Other mechanisms such as a mechanism including a pulley and a belt may be used.
- the rotation output member is a gear or a pulley.
- the oil pump 80 is disposed on the transmission shaft 81, which is a separate shaft from the input shaft 15, but the oil pump may be disposed coaxially with the input shaft 15. Even in this case, by offsetting the damper 16 toward the connecting member 63 with respect to the disc portion 61, the oil pump can be disposed close to the damper 16, and the apparatus can be downsized.
- FIG. 4 is a cross-sectional view schematically showing the input unit 9A of the present embodiment with a part thereof omitted.
- the hydraulic servo 40A is arranged so as to be shifted in the axial direction from the first one-way clutch F1 and the second one-way clutch F2, and the oil pump 80A is arranged coaxially with the input shaft 15 of the transmission mechanism 7.
- the same components are denoted by the same reference numerals, and overlapping descriptions are omitted or simplified, and parts different from those in the first embodiment are described. The explanation is centered.
- the hydraulic servo 40A is arranged to be shifted in the axial direction from the first one-way clutch F1 and the second one-way clutch F2 to the internal combustion engine 2 (see FIG. 1) side.
- the end of the internal combustion engine 2 side of the clutch drum 50A that is rotatably connected to the rotor hub 51 and the damper 16 extends radially inward, and a cylinder portion 41A that constitutes a hydraulic cylinder is integrally formed. Yes.
- the radially inner end portion of the cylinder portion 41A is further extended toward the speed change mechanism 7 (see FIG.
- a return portion (return plate) 44A is fixed to the end portion so as to be positioned with respect to the cylinder portion 41A.
- a return spring (not shown) is arranged between the return portion 44A and the piston 43A.
- a hydraulic oil chamber 46 is formed between the cylinder portion 41A and the piston 43A, and a cancel oil chamber 47 is formed between the return portion 44A and the piston 43A.
- oil passages are formed as follows. First, an oil passage a11 formed in the axial direction on the input shaft 15 is passed through a radial oil passage a12 formed through the input shaft 15, an oil passage a13 formed through the engine connecting shaft 13, and a sleeve portion 410. And is connected to an oil passage a14 communicating with the hydraulic oil chamber 46.
- the engagement pressure is supplied to the hydraulic oil chamber 46 through the oil passages a11 to a14, the piston 43A moves forward in the axial direction against the urging force of the return spring, and the inner friction plate 17 and the outer friction plate 17 The plate 19 is engaged.
- the oil passage a21 formed in the axial direction on the input shaft 15 different from the oil passage a11 described above, the oil passage a24 in the radial direction formed through the input shaft 15 and the oil formed through the engine connecting shaft 13 are formed.
- the oil passage a26 is formed through the passage a25 and the sleeve portion 410 and communicates with the cancel oil chamber 47. Accordingly, the oil is guided to the cancel oil chamber 47 through the oil passages a21, a24 to a26.
- the oil pump 80A is disposed on a transmission shaft 81A that is coaxially disposed with the input shaft 15 of the transmission mechanism 7 that is a first shaft member that is drivingly connected to the internal combustion engine 2 via the clutch K0 and the damper 16. Therefore, it is arranged closer to the speed change mechanism 7 than the motor 3.
- the rotation from the connecting member 63 is transmitted to the transmission shaft 81 ⁇ / b> A via a pinion 64 disposed so as to penetrate the disc portion 61.
- the second one-way clutch F2 is arranged so as to overlap with at least a part of the first one-way clutch F1 when viewed from the radial direction of the motor 3, and the first one-way clutch F1. Since the second one-way clutch F2 is disposed so as to overlap at least a part of the plurality of inner friction plates 17 and the outer friction plates 19 of the clutch K0, the structure has two one-way clutches F1 and F2. The axial dimension of can be suppressed.
- the oil pumps 80 and 80A are configured as inscribed gear pumps.
- the present invention is not limited to this, and the oil pump may have any structure.
- a crescent type internal gear pump, a vane pump, an external gear pump and the like are also conceivable.
- an electric oil pump (not shown) is provided in addition to the oil pump 80, but the motor is stopped while the vehicle in which the internal combustion engine 2 is stopped (idle stop) is stopped. 3, the oil pump 80 is driven and the neutral state is formed by releasing the clutch or brake of the speed change mechanism 7, so that the hydraulic pressure can be supplied to the hydraulic control device 21, so that the electric oil pump can be eliminated. .
- the bearings arranged close to both ends of the first and second one-way clutches F1 and F2 are needle bearings.
- the present invention is not limited to this, and any bearing such as a ball bearing is used. There may be.
- the angular ball bearing 90 as a rotor bearing which rotatably supports the cylinder part 51d of the rotor hub 51 was demonstrated, it is not restricted to this, For example, other things, such as a tapered roller bearing, are mentioned. Different bearings may be used. In this case, as a matter of course, a bearing such as an angular ball bearing 90 is preferable which has a high support accuracy even if the rotor 4 of the motor 3 does not have a double-sided structure.
- the rotation of the clutch drums 50 and 50A is transmitted to the input shaft 15 via the damper 16, but a configuration in which the damper 16 is omitted can also be applied to the drive device 1 of the present embodiment.
- a driving apparatus 1 according to a third embodiment will be described with reference to FIGS. 5 and 6.
- the damper 16 is omitted, the rotor hub 51 is disposed not on the internal combustion engine 2 side of the clutch K0 but on the transmission mechanism 7 side, and the object supported by the carrier 60 is not the damper 16 but the rotor hub 51.
- the drive device 1 of the present embodiment includes a speed change mechanism 7 provided on a power transmission path L between the internal combustion engine 2 and the wheels, and between the speed change mechanism 7 and the internal combustion engine 2. And an input portion 9B to which power from the internal combustion engine 2 is input, and a connection portion 14 that connects the input portion 9B and the internal combustion engine 2 while absorbing pulsation of the internal combustion engine 2 Has been.
- the internal combustion engine 2, the input unit 9B, and the speed change mechanism 7 are arranged in this order on the same axis in the axial direction.
- the input unit 9B includes a clutch K0 that connects / disconnects power transmission between the engine connecting shaft 13 and the input shaft 15 of the speed change mechanism 7 (can be engaged), and a motor 3 that is drivingly connected to the clutch drum 50. It is prepared for.
- the clutch K0 is constituted by a multi-plate clutch in which an inner friction plate 17 and an outer friction plate 19 which are a plurality of friction plates are housed in an internal space of the clutch drum 50.
- the clutch drum 50 includes a rotor hub 51 and a carrier 60. Is connected to the input shaft 15 of the speed change mechanism 7 via the shaft.
- no damper is provided between the motor 3 and the speed change mechanism 7, and the vibration of the internal combustion engine 2 is absorbed by one damper 12. For this reason, compared with the case where another damper is provided in addition to the damper 12, the drive device 1 can be reduced in size and weight.
- the engine connecting shaft 13 is rotatably supported by a ball bearing 95 with respect to the partition wall 27.
- the input shaft 15 is rotatably supported with respect to a sleeve member 25 disposed on the inner peripheral side of a partition wall 24 fixed to a mission case (not shown).
- the clutch K ⁇ b> 0 is arranged so as to be aligned in the axial direction in the order of the partition wall 27, at least a part of the outer friction plate 19 and the inner friction plate 17, and the rotor hub 51.
- the clutch drum 50 is connected to a rotor hub 51 that holds the rotor 4 so as to be able to transmit rotation.
- the clutch drum 50 has, on the outer peripheral surface, a spline portion 50a that is spline-engaged with a spline portion 51c formed on the inner peripheral surface of a drum-shaped clamping portion (rotor holding portion) 51b of the rotor hub 51 described later. Then, the rotor hub 51 and the clutch drum 50 are connected to each other so as to be able to transmit the rotation.
- a plurality of outer friction plates 19 are splined inside the clutch drum 50. Therefore, the outer friction plate 19 is drivingly connected to the input shaft 15 via the clutch drum 50, the rotor hub 51, and the carrier 60.
- the cylinder portion 41 is joined to the outer peripheral surface of the flange portion 13a of the engine connecting shaft 13 by welding, bonding, or the like without using a seal ring or a snap ring, and the shaft portion is connected to the flange portion 13a. Positioned in the direction.
- the rotor hub 51 that holds the rotor 4 includes a drum-shaped sandwiching portion 51b that crimps and sandwiches the rotor core 4a of the rotor 4, and a flange-shaped support portion 51a that supports the sandwiching portion 51b. .
- the rotor hub 51 is connected to the input shaft 15 by a carrier 60 so as to be able to transmit rotation.
- the carrier 60 is formed integrally with the disc portion 61 extending in the axial direction from the inner peripheral edge of the disc portion 61 and a disc-like disc portion 61 that supports the rotor hub 51 on the radially inner side of the rotor hub 51. And a cylindrical sleeve portion 62.
- the disc portion 61 has a rotor hub 51 fitted on the outer peripheral surface thereof, and the inner peripheral portion of the support portion 51a is fixed to the end portion of the outer peripheral portion of the disc portion 61 that is offset toward the connecting member 63 by welding or the like.
- the rotor 31 is fixed to the end of the outer peripheral portion of the disc portion 61 on the transmission mechanism 7 side.
- a stator (detection coil) 32 is fixed to the housing case 26 with a bolt 33 so as to face the rotor 31.
- the rotor 31 and the stator 32 constitute a resolver 30 that detects the rotation state of the motor 3.
- the sleeve portion 62 is in spline engagement with the input shaft 15.
- the rotor 4 of the motor 3 is drivingly connected to the input shaft 15 of the speed change mechanism 7 via the rotor hub 51 and the carrier 60.
- the internal combustion engine 2 is drivingly connected to the input shaft 15 via the engine connecting shaft 13, the clutch K 0, the rotor hub 51 and the carrier 60.
- Lubricating oil for lubricating the motor 3 is supplied to an oil passage a31 formed in the input shaft 15 in the axial direction parallel to the oil passage a21.
- the end of the input shaft 15 on the internal combustion engine 2 side of the oil passage a31 is opened, and the engine connecting shaft 13 is opened via an oil passage a35 that is opened in the recess 13b of the engine connecting shaft 13 and penetrates in the radial direction. It is discharged to the outer peripheral side. Part of the lubricating oil discharged to the outer peripheral side of the engine connecting shaft 13 is guided to the ball bearing 95 and lubricates it.
- the other part of the lubricating oil discharged to the outer peripheral side of the engine connecting shaft 13 passes through an oil passage a36 formed in the partition wall 27, and further cools the motor 3 through an oil passage a34 formed in the rotor hub 51. That is, in the present embodiment, the motor 3 is cooled by oil that lubricates the inside of the housing case 26.
- a seal ring 27b is provided between the partition wall 27 and the engine connecting shaft 13 to prevent the lubricating oil introduced as described above from leaking to the internal combustion engine 2 side of the partition wall 27.
- the dynamic load of the needle bearing 65 depends on the cumulative rotational speed. For this reason, if the situation where the pinion 64 rotates is reduced, the cumulative number of rotations can be reduced, and the dynamic load on the needle bearing 65 can be reduced. As a result, the number of rollers of the needle bearing 65 can be reduced or the size of the rollers themselves can be reduced as compared with the prior art.
- the EV 3 travels when the rotational speed of the motor 3 is higher than the rotational speed of the internal combustion engine 2, the startup of the internal combustion engine 2, and the internal combustion engine.
- both the pinion 64 and the carrier 60 rotate from the motor 3. Is transmitted, the differential rotation (relative rotation) does not occur between the pinion 64 and the carrier 60, the relative rotation speed becomes zero, and the pinion 64 and the carrier 60 rotate together. Therefore, when the oil pumps 80 and 80A are driven by the motor 3, the rotation of the motor and the internal combustion engine are transmitted by transmitting the rotation of the motor to the carrier and the rotation of the internal combustion engine to the stepped planetary gear.
- the number of rotations can be reduced. For this reason, the dynamic load by the relative rotation of the pinion 64 and the carrier 60 can be reduced, and the number of rollers of the needle bearing can be reduced or the size of the roller itself can be reduced as compared with the prior art.
- the carrier 60 is arranged in the power transmission path from the motor 3 to the wheels. That is, the motor 3 is drivingly connected to the wheels via the rotor hub 51, the carrier 60, the input shaft 15, and the speed change mechanism 7.
- the second one-way clutch F ⁇ b> 2 is drivingly connected to a member on the wheel side of the carrier 60, here the input shaft 15. That is, the motor 3 is drivingly connected to the second one-way clutch F2 via the carrier 60.
- the drive device 1 can be downsized.
- the clutch K0 is disposed between the engine connecting shaft 13 and the carrier 60 in the power transmission path, that is, closer to the internal combustion engine 2 than the carrier 60.
- the second one-way clutch F2 is arranged so as to overlap at least a part of the first one-way clutch F1 when viewed from the radial direction of the motor 3, and the first one-way clutch Since the F1 and the second one-way clutch F2 are arranged so as to overlap at least a part of the plurality of inner friction plates 17 and the outer friction plates 19 of the clutch K0, the structure has two one-way clutches F1 and F2. The axial dimension of the device can be suppressed.
- the first one-way clutch F1 and the second one-way clutch F2 are arranged so as to overlap at least a part of the hydraulic servo 40 when viewed from the radial direction of the motor 3.
- the first one-way clutch F1 and the second one-way clutch F2 are arranged so as to overlap at least a part of the cancel oil chamber 47, the axial dimension of the apparatus can be further suppressed.
- the sliding portion 43a of the piston 43 is disposed radially outward of the first one-way clutch F1 and the second one-way clutch F2, the axial direction is used to ensure the moving distance of the piston 43.
- the sliding portion 43a which requires a certain length, can be arranged by effectively using the radially outer space of the first one-way clutch F1 and the second one-way clutch F2, and the axial dimension of the apparatus can be further suppressed.
- the sliding part 43a is arrange
- the space of the sleeve part 13c in the radial direction outer side The sliding portion 43a can be arranged by effectively utilizing the above, and the axial dimension of the apparatus can be further suppressed.
- the sleeve portion 13c which is the engine-side cylindrical portion, constitutes the outer race of the first one-way clutch F1 and the needle bearings b21 and b22.
- the sleeve portion 13c has a shape that is long in the axial direction, and a space that is long in the axial direction also exists radially outward.
- an inner cylindrical portion 44c having a sliding portion 43a is arranged on the outer side in the radial direction of the sleeve portion 13c.
- the sliding portion 43a which requires a certain length in the axial direction, radially outward of the sleeve portion 13c, the space radially outward of the sleeve portion 13c that is long in the axial direction can be used effectively.
- the axial distance of the sliding portion 43a can be secured.
- An oil passage a40 for supplying lubricating oil to the plurality of inner friction plates 17 and the outer friction plates 19 is formed between the return portion 44 and the hydraulic cylinder 42 that form the cancel oil chamber 47 and the clutch hub 49. Therefore, it is possible to provide an oil passage a40 that supplies lubricating oil to the plurality of inner friction plates 17 and the outer friction plates 19 while suppressing the axial dimension of the apparatus. That is, when such an oil passage is different from the above, the axial dimension of the apparatus may be increased in order to form this passage. On the other hand, the axial dimension of the apparatus can be suppressed by forming the oil passage a40 by utilizing the gap between the cancel oil chamber 47 and the clutch hub 49 as in the present embodiment.
- the oil pump 80 is connected to the engine connecting shaft 13 that is drivingly connected to the internal combustion engine 2, the first one-way clutch F 1, the connecting member 63, the pinion 64, the rotation transmission mechanism 70, and the transmission shaft.
- the oil pump 80 can be driven by the driving force of the internal combustion engine 2 because it is arranged so as to be drive-coupled via the engine 81.
- the vehicle starts with the driving force of the internal combustion engine 2 while engaging the clutch K0.
- the lubricating oil can be sufficiently supplied to the inner friction plate 17 and the outer friction plate 19 of the clutch K0.
- a mechanism including a sprocket and a chain is used as a rotation transmission mechanism that transmits drive from the engine connecting shaft 13 to the transmission shaft 81 of the oil pump 80.
- the mechanism includes a plurality of gears.
- Other mechanisms such as a mechanism and a mechanism including a pulley and a belt may be used.
- the rotation output member is a gear or a pulley.
- the oil pump 80 is disposed on the transmission shaft 81, which is a separate shaft from the input shaft 15, but the oil pump may be disposed coaxially with the input shaft 15. Even in this case, by offsetting the damper 16 toward the connecting member 63 with respect to the disc portion 61, the oil pump can be disposed close to the damper 16, and the apparatus can be downsized.
- a drive device 1 according to a fourth embodiment will be described with reference to FIG.
- the clutch hub 49 is attached to the outer peripheral portion of the flange portion 13 a of the engine connecting shaft 13. Since other configurations and operations are the same as those of the third embodiment, the same reference numerals are given to the same configurations, and detailed description thereof is omitted.
- a drive device 1 according to a fifth embodiment will be described with reference to FIG.
- the clutch hub 49 is attached to the outer peripheral portion of the flange portion 13 a of the engine connecting shaft 13. Further, the engine connecting shaft 13 does not have the sleeve portion 13c, and the second one-way clutch F2 is provided on the outer peripheral side of the engine connecting shaft 13. Further, the rotor hub 51 includes an inner cylindrical portion 51e having an open end on the transmission mechanism 7 side, and the inner cylindrical portion 51e is provided on the outer peripheral side of the first one-way clutch F1. Since other configurations and operations are the same as those of the third embodiment, the same reference numerals are given to the same configurations, and detailed description thereof is omitted.
- the clutch hub 49 is attached to the outer peripheral portion of the flange portion 13 a of the engine connecting shaft 13. Further, the engine connecting shaft 13 does not have the sleeve portion 13c, and the second one-way clutch F2 is provided on the outer peripheral side of the engine connecting shaft 13. Further, the rotor hub 51 includes an inner cylindrical portion 51e having an open end on the internal combustion engine 2 side, and the inner cylindrical portion 51e is provided on the outer peripheral side of the first one-way clutch F1.
- the rotor hub 51 is drivingly connected to the inner peripheral portion of the carrier 60, and the input shaft 15 is drivingly connected to the outer peripheral portion of the carrier 60.
- the connecting member 63 includes a gear (third gear) 63a that meshes with the gear 66b from the inner peripheral side.
- the sprocket 71 is drivably coupled to a gear (fourth gear) 71a that meshes with the gear 66a from the inner peripheral side. Since other configurations and operations are the same as those of the third embodiment, the same reference numerals are given to the same configurations, and detailed description thereof is omitted.
- the engine connecting shaft 13 has a cylindrical shape and is provided on the outer peripheral side of the first one-way clutch F1.
- the clutch hub 49 is attached to the outer peripheral portion of the flange portion 13 a of the engine connecting shaft 13.
- the rotor hub 51 is drivingly connected to the inner peripheral portion of the carrier 60, and the input shaft 15 is drivingly connected to the outer peripheral portion of the carrier 60.
- the connecting member 63 includes a gear (third gear) 63a that meshes with the gear 66b from the inner peripheral side.
- the sprocket 71 is drivably coupled to a gear (fourth gear) 71a that meshes with the gear 66a from the inner peripheral side. Since other configurations and operations are the same as those of the third embodiment, the same reference numerals are given to the same configurations, and detailed description thereof is omitted.
- the clutch hub 49 is attached to the outer peripheral portion of the flange portion 13 a of the engine connecting shaft 13. Further, the engine connecting shaft 13 does not have the sleeve portion 13c, and the second one-way clutch F2 is provided on the outer peripheral side of the engine connecting shaft 13. Further, the rotor hub 51 includes an inner cylindrical portion 51e having an open end on the internal combustion engine 2 side, and the inner cylindrical portion 51e is provided on the outer peripheral side of the first one-way clutch F1. The rotor hub 51 is drivingly connected to a gear (fourth gear) 51f that meshes with the gear 66a from the inner peripheral side.
- the input shaft 15 is drivably coupled to a gear (third gear) 15a that meshes with the gear 66b from the inner peripheral side.
- the connecting member 63 is drivingly connected to the inner peripheral portion of the carrier 60
- the sprocket 71 is drivingly connected to the outer peripheral portion of the carrier 60.
- the carrier 60 corresponds to the first rotation transmission member
- the pinion 64 corresponds to the second rotation transmission member. Since other configurations are the same as those of the third embodiment, the same reference numerals are given to the same configurations, and detailed description thereof is omitted.
- the rotation of the motor 3 is transmitted to the gear 66a of the pinion 64 via the rotor hub 51, and is transmitted to the input shaft 15 from the gear 66b of the pinion 64.
- the pinion 64 is interposed in the power transmission path from the motor 3 to the input shaft 15, and the carrier 60 is interposed in the power transmission path from the one-way clutch portion F to the oil pump 80.
- a differential rotation (relative to the pinion 64 and the carrier 60).
- the pinion 64 and the carrier 60 rotate together without causing rotation), so that the dynamic load due to the relative rotation between the pinion 64 and the carrier 60 can be reduced.
- the connecting member 63 is drivingly connected to the inner peripheral portion of the carrier 60, and the sprocket 71 is drivingly connected to the outer peripheral portion of the carrier 60.
- the carrier 60 corresponds to the first rotation transmission member
- the pinion 64 corresponds to the second rotation transmission member. Since other configurations are the same as those of the third embodiment, the same reference numerals are given to the same configurations, and detailed description thereof is omitted.
- the rotation of the motor 3 is transmitted to the gear 66a of the pinion 64 via the rotor hub 51, and is transmitted to the input shaft 15 from the gear 66b of the pinion 64.
- the pinion 64 is interposed in the power transmission path from the motor 3 to the input shaft 15, and the power transmission path from the one-way clutch portion F to the oil pump 80 is also present.
- a carrier 60 is interposed. Also in this case, since the rotation from the motor 3 is transmitted to both the pinion 64 and the carrier 60 when the oil pump 80 is driven by the motor 3, a differential rotation (relative to the pinion 64 and the carrier 60). The pinion 64 and the carrier 60 rotate together without causing rotation), so that the dynamic load due to the relative rotation between the pinion 64 and the carrier 60 can be reduced.
- the clutch hub 49 is attached to the outer peripheral portion of the flange portion 13 a of the engine connecting shaft 13. Further, the engine connecting shaft 13 does not have the sleeve portion 13c, and the second one-way clutch F2 is provided on the outer peripheral side of the engine connecting shaft 13. Further, the rotor hub 51 includes an inner cylindrical portion 51e having an open end on the transmission mechanism 7 side, and the inner cylindrical portion 51e is provided on the outer peripheral side of the first one-way clutch F1. The rotor hub 51 is drivably coupled to a gear (third gear) 51f that meshes with the gear 66b from the inner peripheral side.
- the input shaft 15 is drivingly connected to a gear (fourth gear) 15a meshing with the gear 66a from the inner peripheral side.
- the connecting member 63 is drivingly connected to the outer peripheral portion of the carrier 60, and the sprocket 71 is drivingly connected to the inner peripheral portion of the carrier 60.
- the carrier 60 corresponds to the first rotation transmission member
- the pinion 64 corresponds to the second rotation transmission member. Since other configurations are the same as those of the third embodiment, the same reference numerals are given to the same configurations, and detailed description thereof is omitted.
- the engine connecting shaft 13 has a cylindrical shape and is provided on the outer peripheral side of the first one-way clutch F1.
- the clutch hub 49 is attached to the outer peripheral portion of the flange portion 13 a of the engine connecting shaft 13.
- the rotor hub 51 is drivably coupled to a gear (third gear) 71a that meshes with the gear 66b from the inner peripheral side.
- the input shaft 15 is drivingly connected to a gear (fourth gear) 63a that meshes with the gear 66a from the inner peripheral side.
- the connecting member 63 is drivingly connected to the outer peripheral portion of the carrier 60, and the sprocket 71 is drivingly connected to the inner peripheral portion of the carrier 60.
- the carrier 60 corresponds to the first rotation transmission member
- the pinion 64 corresponds to the second rotation transmission member. Since other configurations are the same as those of the third embodiment, the same reference numerals are given to the same configurations, and detailed description thereof is omitted.
- the rotation of the motor 3 is transmitted to the gear 66b of the pinion 64 via the rotor hub 51, and is transmitted to the input shaft 15 from the gear 66a of the pinion 64.
- the pinion 64 is interposed in the power transmission path from the motor 3 to the input shaft 15, and the power transmission path from the one-way clutch portion F to the oil pump 80 is also present.
- a carrier 60 is interposed. Also in this case, since the rotation from the motor 3 is transmitted to both the pinion 64 and the carrier 60 when the oil pump 80 is driven by the motor 3, a differential rotation (relative to the pinion 64 and the carrier 60). Rotation), the relative rotation speed becomes zero, and the pinion 64 and the carrier 60 rotate together, so that the dynamic load due to the relative rotation between the pinion 64 and the carrier 60 can be reduced.
- the first rotation transmission member has a state driven by the internal combustion engine 2 and a state driven by the motor 3. Thereby, according to the drive device 1 of the first to eleventh embodiments described above, it can be applied to the hybrid vehicle 100 in which both the internal combustion engine 2 and the motor 3 are mounted.
- the oil pumps 80 and 80A are driven by the internal combustion engine 2 through the first rotation transmission member, and the first rotation transmission member is provided. And a state driven by the motor 3. Thereby, according to the drive device 1 of the first to eleventh embodiments described above, it can be applied to the hybrid vehicle 100 in which both the internal combustion engine 2 and the motor 3 are mounted.
- the driving device 1 of the first to eleventh embodiments described above has a one-way clutch portion F that transmits the rotation of the internal combustion engine 2 and the motor 3 that has a higher rotation speed to the first rotation transmission member. It has.
- the one-way clutch portion F selects the rotation with the higher rotation speed out of the rotations of the internal combustion engine 2 and the motor 3 and selects the first rotation. Since the rotation is transmitted to the rotation transmitting member, a sufficient amount of oil discharged from the oil pumps 80 and 80A can be secured without interference between the rotation of the internal combustion engine 2 and the motor 3.
- the first rotation transmission member is the pinion 64 and the second rotation transmission member is the carrier 60, which meshes with the gear 66b and the oil pumps 80, 80A.
- the gears 71a and 63a which are always driven and connected to each other, and the gear 66a and the one-way clutch portion F that transmits the rotation of the internal combustion engine 2 and the motor 3 having the higher rotational speed to the pinion 64.
- Gears 63a and 71a As a result, according to the driving device 1 of the first to seventh embodiments described above, the pinion 64 can transmit the rotation of the internal combustion engine 2 and the motor 3 with higher rotational speeds to the oil pumps 80 and 80A. .
- the one-way clutch portion F is disengaged when the rotational speed on the internal combustion engine 2 side is lower than that of the gear 63a.
- F1 and a second one-way clutch F2 that is disengaged when the rotational speed on the motor 3 side is lower than that of the gear 63a.
- the driving device 1 of the first to eleventh embodiments described above includes the connecting member 63 that is coaxially connected to the gear 63a, the first one-way clutch F1 is disposed on the outer peripheral side of the connecting member 63, and the connecting member A second one-way clutch F ⁇ b> 2 is disposed on the inner peripheral side of 63.
- the second one-way clutch F2 is overlapped with at least a part of the first one-way clutch F1 when viewed from the radial direction of the motor 3. Since it can arrange
- the driving device 1 of the first to eleventh embodiments described above includes the input shaft 15 that is drivingly connected to the second rotation transmission member, and includes the speed change mechanism 7 provided with the oil pumps 80 and 80A.
- the transmission shaft 81 of the pumps 80 and 80 ⁇ / b> A is disposed on the outer peripheral side of the input shaft 15.
- the drive device 1 of the first to eleventh embodiments described above includes the clutch K0 that can switch the connection state of the internal combustion engine 2 and the motor 3 between the engagement state and the release state.
- the gears 63a, 71a, 15a, 51f mesh with the gears 66a, 66b from the inner peripheral side has been described.
- the present invention is not limited to this.
- the gears 63a and 71a may be formed by ring gears and meshed with the gears 66a and 66b from the outer peripheral side.
- the oil pumps 80 and 80A are provided outside the transmission mechanism 7 .
- the present invention is not limited to this.
- FIG. As shown in (b), the oil pump 80 and the rotation transmission mechanism 70 may be accommodated in the casing of the transmission mechanism 7.
- the first one-way clutch F1 and the second one-way clutch F2 are arranged so as to overlap at least partially when viewed from the radial direction.
- the present invention is not limited to this.
- the first one-way clutch F1 and the second one-way clutch F2 may be arranged side by side in the axial direction.
- the pinion 64 rotatably supports the carrier 60 by the needle bearing 65.
- the present invention is not limited to this. Instead, a slide bearing may be used, or the pinion 64 may be directly supported by the through hole 61a of the carrier 60 without providing a bearing.
- This drive device can be used for vehicles such as passenger cars and trucks, and is particularly suitable for use in transmission of at least one of a rotating electric machine and an internal combustion engine to an oil pump.
Abstract
Description
オイルポンプ(80,80A)と、
前記オイルポンプ(80,80A)に駆動連結されると共に、内燃エンジン(2)と前記回転電機(3)との少なくとも一方により駆動される第1回転伝達部材(64,60)と、
前記車輪と駆動連結されると共に、前記回転電機(3)により駆動される第2回転伝達部材(60,64)と、を備え、
前記第1回転伝達部材(64,60)と前記第2回転伝達部材(60,64)のうち、一方の回転伝達部材がピニオン(64)であり、他方の回転伝達部材が前記ピニオン(64)を回転自在に支持するキャリア(60)であり、
前記オイルポンプ(80,80A)が前記回転電機(3)により駆動される場合に、前記ピニオン(64)及び前記キャリア(60)が一体回転することを特徴とする。
以下、第1の実施形態に係るハイブリッド式の駆動装置1を、図1ないし図3に沿って説明する。なお、本実施形態に係る駆動装置は、例えばFF(フロントエンジン・フロントドライブ)タイプ等の車両に搭載されて好適なものであり、図1及び図3中における左右方向が実際の車両搭載状態における左右方向(或いは左右逆方向)に対応するが、説明の便宜上、エンジン等の駆動源側である図中右方側を「前方側」、図中左方側を「後方側」というものとする。
第2の実施形態に係る駆動装置1を、図4に沿って説明する。図4は、本実施形態の入力部9Aを、一部を省略して模式的に示した断面図である。なお、本実施形態の場合、油圧サーボ40Aを第1ワンウェイクラッチF1及び第2ワンウェイクラッチF2から軸方向にずらして配置すると共に、オイルポンプ80Aを変速機構7の入力軸15と同軸上に配置している点が、上述の第1の実施形態と異なる。その他の構成及び作用は、第1の実施形態と同様であるため、以下、同様の構成には同じ符号を付し、重複する説明を省略または簡略にして、第1の実施形態と異なる部分を中心に説明する。
第3の実施形態に係る駆動装置1を、図5及び図6に沿って説明する。本実施形態の場合、ダンパ16を省略すると共に、ロータハブ51をクラッチK0の内燃エンジン2側ではなく変速機構7側に配置し、キャリア60が支持する対象がダンパ16ではなくロータハブ51である点が、上述の第1の実施形態と異なる。その他の構成及び作用は、第1の実施形態と同様であるため、以下、同様の構成には同じ符号を付し、重複する説明を省略または簡略にして、第1の実施形態と異なる部分を中心に説明する。
第4の実施形態に係る駆動装置1を、図7(a)に基づいて説明する。本実施形態では、クラッチハブ49がエンジン連結軸13のフランジ部13aの外周部に取り付けられている。その他の構成及び作用は、第3の実施形態と同様であるため、同様の構成には同じ符号を付し、詳細な説明を省略する。
第5の実施形態に係る駆動装置1を、図7(b)に基づいて説明する。本実施形態では、クラッチハブ49がエンジン連結軸13のフランジ部13aの外周部に取り付けられている。また、エンジン連結軸13はスリーブ部13cを有さず、エンジン連結軸13の外周側に第2ワンウェイクラッチF2が設けられている。更に、ロータハブ51は変速機構7側が開放端となる内側円筒部51eを備え、該内側円筒部51eが第1ワンウェイクラッチF1の外周側に設けられている。その他の構成及び作用は、第3の実施形態と同様であるため、同様の構成には同じ符号を付し、詳細な説明を省略する。
第6の実施形態に係る駆動装置1を、図8(a)に基づいて説明する。本実施形態では、クラッチハブ49がエンジン連結軸13のフランジ部13aの外周部に取り付けられている。また、エンジン連結軸13はスリーブ部13cを有さず、エンジン連結軸13の外周側に第2ワンウェイクラッチF2が設けられている。更に、ロータハブ51は内燃エンジン2側が開放端となる内側円筒部51eを備え、該内側円筒部51eが第1ワンウェイクラッチF1の外周側に設けられている。
第7の実施形態に係る駆動装置1を、図8(b)に基づいて説明する。本実施形態では、エンジン連結軸13が円筒状であり、第1ワンウェイクラッチF1の外周側に設けられている。クラッチハブ49は、エンジン連結軸13のフランジ部13aの外周部に取り付けられている。ロータハブ51がキャリア60の内周部に駆動連結されると共に、入力軸15がキャリア60の外周部に駆動連結されている。連結部材63は、ギヤ66bに内周側から噛合するギヤ(第3のギヤ)63aを備えている。スプロケット71は、ギヤ66aに内周側から噛合するギヤ(第4のギヤ)71aに駆動連結されている。その他の構成及び作用は、第3の実施形態と同様であるため、同様の構成には同じ符号を付し、詳細な説明を省略する。
第8の実施形態に係る駆動装置1を、図9(a)に基づいて説明する。本実施形態では、クラッチハブ49がエンジン連結軸13のフランジ部13aの外周部に取り付けられている。また、エンジン連結軸13はスリーブ部13cを有さず、エンジン連結軸13の外周側に第2ワンウェイクラッチF2が設けられている。更に、ロータハブ51は内燃エンジン2側が開放端となる内側円筒部51eを備え、該内側円筒部51eが第1ワンウェイクラッチF1の外周側に設けられている。また、ロータハブ51は、ギヤ66aに内周側から噛合するギヤ(第4のギヤ)51fに駆動連結されている。入力軸15は、ギヤ66bに内周側から噛合するギヤ(第3のギヤ)15aに駆動連結されている。連結部材63がキャリア60の内周部に駆動連結されると共に、スプロケット71がキャリア60の外周部に駆動連結されている。この場合、上述した第1~第7の実施形態と異なり、キャリア60が第1回転伝達部材に相当すると共に、ピニオン64が第2回転伝達部材に相当する。その他の構成は、第3の実施形態と同様であるため、同様の構成には同じ符号を付し、詳細な説明を省略する。
第9の実施形態に係る駆動装置1を、図9(b)に基づいて説明する。本実施形態では、エンジン連結軸13が円筒状であり、第1ワンウェイクラッチF1の外周側に設けられている。クラッチハブ49は、エンジン連結軸13のフランジ部13aの外周部に取り付けられている。ロータハブ51は、ギヤ66aに内周側から噛合するギヤ(第4のギヤ)51fに駆動連結されている。入力軸15は、ギヤ66bに内周側から噛合するギヤ(第3のギヤ)15aに駆動連結されている。連結部材63がキャリア60の内周部に駆動連結されると共に、スプロケット71がキャリア60の外周部に駆動連結されている。この場合、上述した第1~第7の実施形態と異なり、キャリア60が第1回転伝達部材に相当すると共に、ピニオン64が第2回転伝達部材に相当する。その他の構成は、第3の実施形態と同様であるため、同様の構成には同じ符号を付し、詳細な説明を省略する。
第10の実施形態に係る駆動装置1を、図10(a)に基づいて説明する。本実施形態では、クラッチハブ49がエンジン連結軸13のフランジ部13aの外周部に取り付けられている。また、エンジン連結軸13はスリーブ部13cを有さず、エンジン連結軸13の外周側に第2ワンウェイクラッチF2が設けられている。更に、ロータハブ51は変速機構7側が開放端となる内側円筒部51eを備え、該内側円筒部51eが第1ワンウェイクラッチF1の外周側に設けられている。また、ロータハブ51は、ギヤ66bに内周側から噛合するギヤ(第3のギヤ)51fに駆動連結されている。入力軸15は、ギヤ66aに内周側から噛合するギヤ(第4のギヤ)15aに駆動連結されている。連結部材63がキャリア60の外周部に駆動連結されると共に、スプロケット71がキャリア60の内周部に駆動連結されている。この場合、上述した第1~第7の実施形態と異なり、キャリア60が第1回転伝達部材に相当すると共に、ピニオン64が第2回転伝達部材に相当する。その他の構成は、第3の実施形態と同様であるため、同様の構成には同じ符号を付し、詳細な説明を省略する。
第11の実施形態に係る駆動装置1を、図10(b)に基づいて説明する。本実施形態では、エンジン連結軸13が円筒状であり、第1ワンウェイクラッチF1の外周側に設けられている。クラッチハブ49は、エンジン連結軸13のフランジ部13aの外周部に取り付けられている。ロータハブ51は、ギヤ66bに内周側から噛合するギヤ(第3のギヤ)71aに駆動連結されている。入力軸15は、ギヤ66aに内周側から噛合するギヤ(第4のギヤ)63aに駆動連結されている。連結部材63がキャリア60の外周部に駆動連結されると共に、スプロケット71がキャリア60の内周部に駆動連結されている。この場合、上述した第1~第7の実施形態と異なり、キャリア60が第1回転伝達部材に相当すると共に、ピニオン64が第2回転伝達部材に相当する。その他の構成は、第3の実施形態と同様であるため、同様の構成には同じ符号を付し、詳細な説明を省略する。
2 内燃エンジン
3 モータ(回転電機)
7 変速機構
15 入力軸
15a ギヤ(第3のギヤ、第4のギヤ)
51f ギヤ(第3のギヤ、第4のギヤ)
60 キャリア(第1回転伝達部材、第2回転伝達部材)
63 連結部材(筒状部材)
63a ギヤ(第3のギヤ、第4のギヤ)
64 ピニオン(第1回転伝達部材、第2回転伝達部材)
64a 軸部
65 ニードルベアリング(軸受)
66a ギヤ(第2のギヤ)
66b ギヤ(第1のギヤ)
71a ギヤ(第3のギヤ、第4のギヤ)
80,80A オイルポンプ
81 伝達軸(駆動軸)
F ワンウェイクラッチ部(回転選択部)
F1 第1ワンウェイクラッチ
F2 第2ワンウェイクラッチ
K0 クラッチ
Claims (11)
- 車輪に駆動連結される回転電機を有する駆動装置において、
オイルポンプと、
前記オイルポンプに駆動連結されると共に、内燃エンジンと前記回転電機との少なくとも一方により駆動される第1回転伝達部材と、
前記車輪と駆動連結されると共に、前記回転電機により駆動される第2回転伝達部材と、を備え、
前記第1回転伝達部材と前記第2回転伝達部材のうち、一方の回転伝達部材がピニオンであり、他方の回転伝達部材が前記ピニオンを回転自在に支持するキャリアであり、
前記オイルポンプが前記回転電機により駆動される場合に、前記ピニオン及び前記キャリアが一体回転する、
ことを特徴とする駆動装置。 - 前記第1回転伝達部材は、前記内燃エンジンにより駆動される状態と、前記回転電機により駆動される状態と、を有する、
ことを特徴とする請求項1記載の駆動装置。 - 前記オイルポンプは、前記第1回転伝達部材を介することにより前記内燃エンジンによって駆動される状態と、前記第1回転伝達部材を介することにより前記回転電機によって駆動される状態と、を有する、
ことを特徴とする請求項2記載の駆動装置。 - 前記内燃エンジンと前記回転電機との回転のうち、回転速度が高い方の回転を前記第1回転伝達部材に伝達する回転選択部を備える、
ことを特徴とする請求項3記載の駆動装置。 - 前記ピニオンは、軸部と、前記軸部の一端部に形成された第1のギヤと、前記軸部の他端部に形成された第2のギヤと、を備え、
前記キャリアは、軸受を介して前記軸部を回転自在に支持する、
ことを特徴とする請求項1乃至4のいずれか1項に記載の駆動装置。 - 第1回転伝達部材がピニオンで、第2回転伝達部材はキャリアであり、
前記第1のギヤに噛合すると共に、前記オイルポンプに常時駆動連結される第3のギヤと、
前記第2のギヤに噛合すると共に、前記内燃エンジンと前記回転電機との回転のうち、回転速度が高い方の回転を前記ピニオンに伝達する回転選択部に駆動連結される第4のギヤと、を備える、
ことを特徴とする請求項5記載の駆動装置。 - 前記回転選択部は、前記第4のギヤよりも前記内燃エンジン側の回転速度が低くなった際に非係合となる第1ワンウェイクラッチと、前記第4のギヤよりも前記回転電機側の回転速度が低くなった際に非係合となる第2ワンウェイクラッチと、を備える、
ことを特徴とする請求項6記載の駆動装置。 - 前記第4のギヤに同軸で連結される筒状部材を備え、
前記筒状部材の外周側に、前記第1ワンウェイクラッチが配置され、
前記筒状部材の内周側に、前記第2ワンウェイクラッチが配置される、
ことを特徴とする請求項7記載の駆動装置。 - 前記オイルポンプが前記内燃エンジンにより駆動される場合に、前記ピニオン及び前記キャリアは相対回転する、
ことを特徴とする請求項1乃至8のいずれか1項に記載の駆動装置。 - 前記第2回転伝達部材に駆動連結される入力軸を有すると共に、前記オイルポンプが設けられる変速機構を備え、
前記オイルポンプの駆動軸は、前記入力軸の外周側に配置される、
ことを特徴とする請求項1乃至9のいずれか1項に記載の駆動装置。 - 前記内燃エンジンと前記回転電機との連結状態を、係合状態と解放状態とに切換自在なクラッチを備える、
ことを特徴とする請求項1乃至10のいずれか1項に記載の駆動装置。
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