US20180304896A1 - Driving apparatus for vehicle and vehicle - Google Patents
Driving apparatus for vehicle and vehicle Download PDFInfo
- Publication number
- US20180304896A1 US20180304896A1 US15/769,176 US201615769176A US2018304896A1 US 20180304896 A1 US20180304896 A1 US 20180304896A1 US 201615769176 A US201615769176 A US 201615769176A US 2018304896 A1 US2018304896 A1 US 2018304896A1
- Authority
- US
- United States
- Prior art keywords
- input
- driving apparatus
- gear
- electric motor
- input paths
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
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Classifications
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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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/021—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing
- F16H37/022—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing the toothed gearing having orbital motion
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W30/00—Purposes of road vehicle drive control systems not related to the control of a particular sub-unit, e.g. of systems using conjoint control of vehicle sub-units, or advanced driver assistance systems for ensuring comfort, stability and safety or drive control systems for propelling or retarding the vehicle
- B60W30/18—Propelling the vehicle
- B60W30/19—Improvement of gear change, e.g. by synchronisation or smoothing gear shift
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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
- B60K1/00—Arrangement or mounting of electrical propulsion units
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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
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/02—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of clutch
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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
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
- B60K17/06—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing
- B60K17/08—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing of mechanical type
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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
- 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
- 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
- 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
- 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
- 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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- 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
- B60K6/40—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; 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 assembly or relative disposition of components
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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
- B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; 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 the architecture of the hybrid electric vehicle
- B60K6/48—Parallel type
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- B—PERFORMING OPERATIONS; TRANSPORTING
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- 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
- B60K6/50—Architecture of the driveline characterised by arrangement or kind of transmission units
- B60K6/54—Transmission for changing ratio
- B60K6/547—Transmission for changing ratio the transmission being a stepped gearing
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- B60L15/00—Methods, circuits, or devices for controlling the traction-motor speed of electrically-propelled vehicles
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- B60L15/2054—Methods, circuits, or devices for controlling the traction-motor speed of electrically-propelled vehicles for control of the vehicle or its driving motor to achieve a desired performance, e.g. speed, torque, programmed variation of speed by controlling transmissions or clutches
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- B60L50/16—Electric propulsion with power supplied within the vehicle using propulsion power supplied by engine-driven generators, e.g. generators driven by combustion engines with provision for separate direct mechanical propulsion
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- B60W20/00—Control systems specially adapted for hybrid vehicles
- B60W20/10—Controlling the power contribution of each of the prime movers to meet required power demand
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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- 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
- F16H3/727—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 with at least two dynamo electric machines for creating an electric power path inside the gearing, e.g. using generator and motor for a variable power torque path
- F16H3/728—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 with at least two dynamo electric machines for creating an electric power path inside the gearing, e.g. using generator and motor for a variable power torque path with means to change ratio in the mechanical gearing
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K5/00—Casings; Enclosures; Supports
- H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
- H02K5/16—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields
- H02K5/173—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using bearings with rolling contact, e.g. ball bearings
- H02K5/1732—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using bearings with rolling contact, e.g. ball bearings radially supporting the rotary shaft at both ends of the rotor
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/62—Hybrid vehicles
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/64—Electric machine technologies in electromobility
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/7072—Electromobility specific charging systems or methods for batteries, ultracapacitors, supercapacitors or double-layer capacitors
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/72—Electric energy management in electromobility
Definitions
- the present invention relates to a driving apparatus for vehicle and a vehicle.
- Patent Literature 1 discloses a discontinuous change of a speed reduction ratio produced by using a combination of a continuously variable transmission and a two-speed sub-transmission at the time of switching between two stages of high and low speeds.
- an object of the present invention is to solve the aforementioned issue by providing a driving apparatus for vehicle and a vehicle each preventing discomfort felt by a user as a result of speed change shock, or a discontinuous change of acceleration.
- a driving apparatus for vehicle comprising:
- continuously variable adjustment of output of the one system is achieved by adjusting each input from the two systems connected to the Ravigneaux planetary gear in an opened state of each of the friction clutch and the friction brake.
- a vehicle comprising:
- a driving apparatus for vehicle that includes a Ravigneaux planetary gear, a friction clutch, and a friction brake, wherein input paths of two systems and an output path of one system are provided for the Ravigneaux planetary gear;
- a controller provided on the vehicle to perform continuously variable control of output of the one system by controlling a rotation direction, a rotation speed, and torque of each input from the two systems connected to the Ravigneaux planetary gear in an opened state of each of the friction clutch and the friction brake.
- continuously variable adjustment of output of one system is achievable by adjusting each input of two systems. Accordingly, discomfort felt by a user as a result of speed change shock or a discontinuous change of acceleration is avoidable.
- FIG. 1 is a schematic configuration view of a driving apparatus for vehicle according to a first embodiment of the present invention
- FIG. 2 is an alignment chart of an operation state (variable speed, reverse rotation) of the driving apparatus for vehicle according to the first embodiment
- FIG. 3 is an alignment chart of an operation state (fixed reduction ratio, reverse rotation) of the driving apparatus for vehicle according to the first embodiment
- FIG. 4 is an alignment chart of an operation state (variable speed, normal rotation) of the driving apparatus for vehicle according to the first embodiment
- FIG. 5 is an alignment chart of an operation state (fixed reduction ratio, normal rotation) of the driving apparatus for vehicle according to the first embodiment
- FIG. 6 is a schematic configuration view of a driving apparatus for vehicle according to a modified example of the first embodiment of the present invention.
- FIG. 7 is a schematic configuration view of a driving apparatus for vehicle according to a different modified example of the first embodiment of the present invention.
- FIG. 8 is a schematic configuration view of a driving apparatus for vehicle according to a further different modified example of the first embodiment of the present invention.
- FIG. 9 is a schematic configuration view of a vehicle including the driving apparatus for vehicle according to the first embodiment of the present invention.
- FIG. 10 is a schematic configuration view of a driving apparatus for vehicle according to a still further different modified example of the first embodiment of the present invention.
- FIG. 11 is a schematic configuration view of a driving apparatus for vehicle according to a still further different modified example of the first embodiment of the present invention.
- a driving apparatus for vehicle 513 includes a Ravigneaux planetary gear 501 , a friction clutch 502 , a friction brake 503 , and a control mechanism 316 .
- Input paths of two systems and an output path of one system are provided for the Ravigneaux planetary gear 501 in this configuration.
- Continuously variable adjustment (control) of output of the one system is achievable by adjusting (controlling) a rotation direction, a rotation speed, and torque of each input of the two systems connected to the Ravigneaux planetary gear 501 in an opened state of each of the friction clutch 502 and the friction brake 503 .
- a vehicle 591 (see FIG. 9 ) equipped with the driving apparatus for vehicle 513 according to the first embodiment includes a vehicle-side controller (e.g., engine control unit (ECU)) 590 described below to perform the foregoing control.
- ECU engine control unit
- a continuously variable sub-transmission is adopted instead of the two-speed sub-transmission to solve the conventional issue. This point is hereinafter detailed.
- the Ravigneaux planetary gear 501 includes a first sun gear 504 , a second sun gear 505 , a first pinion gear 506 , a second pinion gear 507 , a ring gear 508 , and a pinion carrier 509 .
- Relative rotations of the second pinion gear 507 and the first pinion gear 506 are regulated by the identical pinion carrier 509 .
- the first sun gear 504 engages with the first pinion gear 506 via the second pinion gear 507 .
- the second sun gear 505 engages with the first pinion gear 506 .
- the first pinion gear 506 is a gear elongated in the axial direction, and engages with the second sun gear 505 on the downstream side of an engagement portion between the first pinion gear 506 and the second pinion gear 507 .
- the first pinion gear 506 and the ring gear 508 engage with each other.
- the ring gear 508 is disposed outside the first pinion gear 506 .
- a first input path of the input paths of the two systems is connected to the second sun gear 505 , while a second input path is connected to the first sun gear 504 .
- the output path of the one system is connected to the ring gear 508 .
- the first input path of the input passes of the two systems in FIG. 1 is defined by connection between the second sun gear 505 and a first output shaft 515 of an engine 510 provided as an example of an internal combustion engine.
- the second input path thereof is defined by connection between a rotation shaft 516 integrally rotating with a rotor 511 a of an electric motor 511 , and the first sun gear 504 .
- the upstream side of a second output shaft 517 provided as the output path of the one system is connected to the ring gear 508 , while the downstream side of the second output shaft 517 is connected to a transmission 512 .
- a stator 511 b for the rotor 511 a of the electric motor 511 is fixed to a fixed end (case of driving apparatus for vehicle 513 ) 520 .
- the rotor 511 a rotates relative to the stator 511 b.
- the friction clutch 502 and the friction brake 503 are also connected to the rotation shaft 516 integrally rotating with the rotor 511 a of the electric motor 511 . Accordingly, driving is achievable by closing of the friction clutch 502 or the friction brake 503 only with the engine 510 even when electric input from the electric motor 511 becomes zero as a result of no supply of power from a battery.
- the friction clutch 502 and the friction brake 503 are configured to be controlled (closed or opened) by closing control under the control mechanism 316 .
- the control mechanism 316 herein is a hydraulic piston or an electric actuator, for example, which independently closes or opens the friction clutch 502 and/or the friction brake 503 .
- the friction clutch 502 transmits torque by an axial press against disks 341 and driven plates 343 alternately overlapped with each other.
- a pressing action is achievable by a direct press with a hydraulic piston or by a press with an electric actuator via a bearing.
- the friction brake 503 stops rotation by an axial press against disks 344 and driven plates 345 alternately overlapped on each other.
- a pressing action is achievable by a direct press with a hydraulic piston or by a press with an electric actuator via a bearing.
- the friction clutch 502 regulates relative rotations of the rotation shaft 516 and the pinion carrier 509 of the Ravigneaux planetary gear 501
- the friction brake 503 regulates relative rotations of the pinion carrier 509 of the Ravigneaux planetary gear 501 and the fixed end (case of driving apparatus for vehicle 513 ) 520 .
- the pinion carrier 509 is connected to a driving ring 342 described below.
- the friction clutch 502 and the friction brake 503 have following configurations as illustrated in FIG. 1 .
- the annular disks 341 for the friction clutch 502 are connected to an outer surface of an input side member 340 which is concentrically connected to the rotation shaft 516 of the electric motor 511 and integrally rotates with the rotation shaft 516 .
- the driving ring 342 whose rotation axis center is disposed concentrically with the rotation shaft 516 , includes on the inner surface side thereof the annular driven plates 343 for the friction clutch 502 facing the disks 341 .
- the driving ring 342 is restricted in the axial direction of the rotation shaft 516 .
- the annular disks 344 for the friction brake 503 are connected to the outer surface side of the driving ring 342 .
- the annular driven plates 345 for the friction brake 503 are connected to the inner circumferential surface of the fixed end (case of driving apparatus for vehicle 513 ) 520 at positions facing the annular disks 344 .
- the driven plates 345 are restricted in the rotation direction with respect to the fixed end 520 , but are movable in the axial direction of the rotation shaft 516 .
- the annular disks 341 for the friction clutch 502 and the annular driven plates 343 for the friction clutch 502 are alternately disposed with a clearance left between each other.
- the annular disks 344 for the friction brake 503 and the annular driven plates 345 for the friction brake 503 are alternately disposed with a clearance left between each other.
- the disks 341 and the driven plates 343 disposed adjacent to each other for the friction clutch 502 are allowed to contact with each other with pressure or separate from each other to achieve relative rotation regulation by axial forward or backward movement using a hydraulic piston or an electric actuator, for example, under the closing control by the control mechanism 316 .
- the disks 344 and the annular driven plates 345 disposed adjacent to each other for the friction brake 503 are allowed to contact with each other with pressure or separate from each other to achieve relative rotation regulation.
- the disks 344 and the driven plates 345 for the friction brake 503 are allowed to achieve forward and backward movement in the axial direction, while the driving ring 342 is restricted in the axial direction.
- the friction clutch 502 is configured to regulate relative rotations of any two elements selected from the first sun gear 504 , the second sun gear 505 , the pinion carrier 509 , and the ring gear 508 .
- the friction brake 503 is configured to regulate relative rotations of the pinion carrier 509 and a fixed end (case of driving apparatus for vehicle 513 ) 520 .
- to regulate refers to any action of forward or backward movement of components in the axial direction by driving of the control mechanism 316 to shift one of the components in the axial direction for contact with each other and thereby achieving connection between the components, to shift one of the components in the axial direction for separation from each other and thereby achieving disconnection between the components, or to shift one of the components in the axial direction for approach to each other and thereby achieving slip between the components with contact therebetween (half-clutch).
- FIG. 2 is an alignment chart of an operation state (variable speed, reverse rotation) of the driving apparatus for vehicle 513 .
- FIG. 3 is an alignment chart of an operation state (fixed reduction ratio, reverse rotation) of the driving apparatus for vehicle 513 .
- FIG. 4 is an alignment chart of an operation state (variable speed, normal rotation) of the driving apparatus for vehicle 513 .
- FIG. 5 is an alignment chart of an operation state (fixed reduction ratio, normal rotation) of the driving apparatus for vehicle 513 .
- FIGS. 2 to 5 herein is an alignment chart showing a mechanical relationship between rotation speeds and torques of respective rotation elements in the driving apparatus for vehicle 513 .
- Four vertical lines in a horizontal-axis X direction in each of the alignment charts in FIGS. 2 to 5 represent a gear ratio relationships of rotation elements, i.e., the second sun gear 505 , the pinion carrier 509 , the ring gear 508 , and the first sun gear 504 of the Ravigneaux planetary gear 501 in this order from the left in the chart, respectively.
- Each of the four vertical lines indicates two-dimensional coordinates expressing a relative rotation speed in the vertical-axis Y direction.
- One dotted oblique line indicates rotation speeds, i.e., respective rotation speeds of the electric motor 511 and the engine 510 provided as an example of an internal combustion engine connected to the output shaft.
- FIG. 2 illustrates a continuously variable transmission mode of the driving apparatus for vehicle 513 .
- the engine 510 and the electric motor 511 have a relationship of reversed rotation directions.
- the second sun gear 505 (input) and the ring gear 508 (output) have a relationship of reversed rotation directions.
- a value of output from the ring gear 508 is adjustable by any speed reduction ratio obtained by adjusting the rotation speed of the electric motor 511 connected to the first sun gear 504 via the rotation shaft 516 and the rotation speed of the engine 510 connected to the second sun gear 505 via the first output shaft 515 in a free state of the pinion carrier 509 without closing of the friction clutch 502 and the friction brake 503 by the control mechanism 316 .
- the rotation direction, the rotation speed, and the torque output from the ring gear 508 are determined in accordance with the rotation directions, the rotation speeds, and the torque of the engine 510 and the electric motor 511 (as for relationship between rotation speeds and torques, see dotted line indicating linear relationship on alignment chart).
- the respective rotation directions, the rotation speeds, and the torques of the engine 510 and the electric motor 511 herein are not determined simply by the single driving apparatus for vehicle 513 .
- the operation states of the engine 510 and the electric motor 511 are determined and controlled based on comprehensive determination made by the controller (engine control unit (ECU) or the like) 590 at the side of the vehicle equipped with the driving apparatus for vehicle 513 based on a request from a user with reference to respective degrees of efficiency of the engine 510 and the electric motor 511 , a state of a battery, or other conditions.
- the controller engine control unit (ECU) or the like
- FIG. 3 shows a fixed speed reduction ratio mode of the driving apparatus for vehicle 513 .
- the second sun gear 505 (input) and the ring gear 508 (output) have a relationship of reversed rotation directions.
- the speed reduction ratio is fixed when the pinion carrier 509 is fixed by closing of the friction brake 503 under the control mechanism 316 . Accordingly, a rotation speed of the electric motor 511 connected to the first sun gear 504 and a value of output from the ring gear 508 are determined when the rotation speed of the engine 510 connected to the second sun gear 505 is determined.
- FIG. 4 shows a continuously variable transmission mode of the driving apparatus for vehicle 513 , where the second sun gear 505 (input) and the ring gear 508 (output) have a relationship of rotations in the same direction.
- the rotation direction of output from the ring gear 508 is equalized when the rotation direction of the electric motor 511 connected to the first sun gear 504 is equalized with the rotation direction of the engine 510 connected to the second sun gear 505 by equalization of the rotation directions of the engine 510 and the electric motor 511 in a free state of the pinion carrier 509 without closing of the friction clutch 502 and the friction brake 503 by the control mechanism 316 .
- a value of output from the ring gear 508 is adjustable by any speed reduction ratio obtained by adjusting the rotation speed of the electric motor 511 connected to the first sun gear 504 and the rotation speed of the engine 510 connected to the second sun gear 505 .
- input and output rotate in the same direction when the engine 510 and the electric motor 511 rotate in the same rotation direction.
- the normal rotation and reverse rotation, and adjustment of the rotation speed of the electric motor 511 are achievable by using the controller (e.g., inverter) 590 .
- FIG. 5 shows a fixed speed reduction ratio mode of the driving apparatus for vehicle 513 , where the second sun gear 505 (input) and the ring gear 508 (output) have a relationship of rotations in the same direction.
- the speed reduction ratio is fixed to 1 by connection between the pinion carrier 509 and the first sun gear 504 via the friction clutch 502 connected to the pinion carrier 509 by driving of the control mechanism 316 .
- a rotation speed of the electric motor 511 connected to the first sun gear 504 and a value of output from the ring gear 508 are determined when the rotation speed of the engine 510 connected to the second sun gear 505 is determined.
- the transmission 512 may be configured by a pair of pulleys 311 b (only one of pulleys 311 b is shown, and the other pulley is not shown) capable of adjusting a distance between opposed sheave surfaces 311 a , and a band-shaped member 311 c such as a belt or a chain laid between the pair of pulleys 311 b.
- the issue of speed change shock or a feeling of discontinuity of acceleration can be solved by making at least continuous (smooth) adjustment of input of the two systems.
- discontinuous elements such as a friction clutch and a friction brake.
- the user may be shocked, for example, at the time of an instantaneous stop (brake) of a driving electric motor, for example.
- the first embodiment adopting the continuously variable sub-transmission can eliminate speed change shock caused by a speed change of the sub-transmission, or discomfort felt by a user as a result of a discontinuous change of acceleration.
- the driving apparatus for vehicle 513 functions as a continuously variable sub-transmission when combined with the existing transmission 512 . Accordingly, a transmission gear ratio range (ratio coverage) of the existing transmission 512 expands, wherefore traveling performance and fuel consumption of the vehicle can improve.
- the driving apparatus for vehicle 513 functioning as a continuously variable sub-transmission achieves smooth operation. Furthermore, addition of the electric motor 511 can improve fuel consumption of the vehicle.
- the input paths of the two systems may be constituted by a first input path defined by connection between the second sun gear 505 and the electric motor 511 , and a second input path defined by connection between the first sun gear 504 and the engine 510 provided as an example of an internal combustion engine to make connection between the friction brake 503 and the ring gear 508 , and between the output 517 and the pinion carrier 509 .
- the control mechanism 316 is capable of shifting the disks and the driven plates forward and backward in the axial direction to perform closing control of the friction clutch 502 and the friction brake 503 . According to this modified example, effects similar to the effects of the first embodiment can be obtained.
- the input paths of the two systems may be constituted by a first input path defined by connection between the second sun gear 505 and the first electric motor 511 provided as a first electric motor, and a second input path defined by connection between the first sun gear 504 and a second electric motor 531 .
- a stator 531 b for the rotor 531 a of the electric motor 531 is fixed to the fixed end (case of driving apparatus for vehicle 513 ) 520 .
- the rotor 531 a rotates relative to the stator 531 b .
- the second electric motor 531 in FIG. 7 is disposed at the position of the electric motor 511 in FIG. 1 .
- the first electric motor 511 is disposed on the upstream side of the second electric motor 531 in such a manner as to connect with the first output shaft 515 on the downstream side of a torsional vibration damper 521 .
- an electric motor is required to use a range of small load and low efficiency when necessary driving force is small during driving of a vehicle.
- either the first electric motor 511 or the second electric motor 531 is used as an electric motor for driving, while the other of the first and second electric motors 511 and 531 is used as a power generator, i.e., an electric motor for load.
- the electric motor for driving is driven in a range of larger load and higher efficiency, while power exceeding driving force necessary for vehicle driving is generated by the other electric motor, and can be stored as electrical energy.
- the electrical energy stored herein can be used for subsequent vehicle driving.
- driving force for driving a vehicle is large in an opposite case, an electric motor is required to use a large load and low efficiency range.
- driving force is shared by the first electric motor 511 and the second electric motor 531 to lower each load of the electric motors and achieve driving in a high efficiency range.
- a different clutch 540 may be added between the torsional vibration damper 521 and the second sun gear 505 to allow separation of the engine 510 .
- the damper 521 is a damper provided for transmitting a torque of the engine 510 , and absorbing and isolating torsional vibration.
- An input side member 540 a of the different clutch 540 is connected to the downstream side of the torsional vibration damper 521 , while an output side member 540 b disposed adjacent to the input side member 540 a and facing the input side member 540 a is connected to an output shaft 541 of the different clutch 540 .
- the output shaft 541 is connected to the second sun gear 505 .
- torque of the engine 510 is transmitted to the output shaft 541 during closing between the input side member 540 a and the output side member 540 b .
- torque of the engine 510 is not transmitted to the output shaft 541 during separation between the input side member 540 a and the output side member 540 b.
- losses produced by corotation of the engine 510 can be eliminated when the vehicle is driven only by the electric motor 511 , or when kinetic energy of the vehicle is regenerated into electrical energy by the electric motor 511 . Accordingly, efficiency during driving and a regeneration quantity can improve.
- FIG. 10 illustrates a modified example which positions the friction clutch 502 between the pinion carrier 509 and the ring gear 508 . More specifically, the pinion carrier 509 and the driving ring 342 are connected to each other. The annular disks 341 for the friction clutch 502 are connected to an outer surface of a ring member 340 a . The ring member 340 a in this condition is connected to the ring gear 508 and the second output shaft 517 .
- FIG. 11 illustrates another modified example which positions the friction clutch 502 between the first sun gear 504 and the second sun gear 505 .
- the first sun gear 504 is connected via the rotation shaft 516 to a rotation ring 342 c which integrally rotates with the rotor 511 a of the electric motor 511 .
- the annular disks 341 for the friction clutch 502 are connected to an outer surface of the first output shaft 515 .
- the first output shaft 515 in this condition is connected to the second sun gear 505 .
- effects produced by the friction clutch 502 can be basically obtained as common effects.
- drag torque of the friction clutch 502 during closing of the friction brake 503 disposed between the pinion carrier 509 and the fixed end 520 i.e., during relative rotations of disks 341 and plates 343 with friction clutch 502 opened.
- a relative rotation speed difference is produced between the disks 341 and the plates 343 of the friction clutch 502 by an amount of a length of a downward arrow put for the first sun gear 504 in FIG. 3 .
- a relative rotation speed difference is produced between the disks 341 and the plates 343 of the friction clutch 502 by an amount of a length of a downward arrow put for the ring gear 508 in FIG. 3 .
- a relative rotation speed difference is produced between the disks 341 and the plates 343 of the friction clutch 502 by an amount of the sum of a length of an upward arrow put for the second sun gear 505 and the length of the downward arrow put for the first sun gear 504 in FIG. 3 .
- the respective levels of the relative rotation speed difference have a relationship of: configuration example (2) in FIG. 10 ⁇ configuration example (1) in FIG. 1 ⁇ configuration example (3) in FIG. 11 .
- a state close to a no-torque transmission state is basically produced in the opened state of the friction clutch 502 .
- a viscous resistance component in a shearing direction remains, and causes drag torque, i.e., power losses.
- the order of excellency of the respective configuration examples is considered as the configuration example (2) in FIG. 10 , the configuration example (1) in FIG. 1 , and the configuration example (3) in FIG. 11 in the descending order.
- a driving apparatus for vehicle and a vehicle according to the present invention prevent discomfort felt by a user as a result of speed change shock or a discontinuous change of acceleration, and are therefore useful when applied to various types of vehicle including a compact automobile.
Abstract
Description
- The present invention relates to a driving apparatus for vehicle and a vehicle.
-
Patent Literature 1 discloses a discontinuous change of a speed reduction ratio produced by using a combination of a continuously variable transmission and a two-speed sub-transmission at the time of switching between two stages of high and low speeds. - PTL 1: Japanese Patent No. 4660583
- However, according to the above conventional art which produces a discontinuous change of a speed reduction ratio by using a combination of a continuously variable transmission and a two-speed sub-transmission at the time of switching between high and low speeds, there has been arising an issue of discomfort felt by a user as a result of speed change shock, or a discontinuous change of acceleration, at the time of absorption of energy corresponding to a relative rotation speed difference produced by the discontinuous change of the speed reduction ratio.
- Accordingly, an object of the present invention is to solve the aforementioned issue by providing a driving apparatus for vehicle and a vehicle each preventing discomfort felt by a user as a result of speed change shock, or a discontinuous change of acceleration.
- In accomplishing these and other objects, according to an aspect of the present invention, there is provided a driving apparatus for vehicle, the apparatus comprising:
- a Ravigneaux planetary gear;
- a friction clutch; and
- a friction brake,
- wherein
- input paths of two systems and an output path of one system are provided for the Ravigneaux planetary gear, and
- continuously variable adjustment of output of the one system is achieved by adjusting each input from the two systems connected to the Ravigneaux planetary gear in an opened state of each of the friction clutch and the friction brake.
- In accomplishing these and other objects, according to a different aspect of the present invention, there is provided a vehicle comprising:
- a driving apparatus for vehicle that includes a Ravigneaux planetary gear, a friction clutch, and a friction brake, wherein input paths of two systems and an output path of one system are provided for the Ravigneaux planetary gear; and
- a controller provided on the vehicle to perform continuously variable control of output of the one system by controlling a rotation direction, a rotation speed, and torque of each input from the two systems connected to the Ravigneaux planetary gear in an opened state of each of the friction clutch and the friction brake.
- According to the aspect of the present invention, continuously variable adjustment of output of one system is achievable by adjusting each input of two systems. Accordingly, discomfort felt by a user as a result of speed change shock or a discontinuous change of acceleration is avoidable.
- These and other objects and features of the present invention will become apparent in the light of following description relating to preferred embodiments describing the accompanying drawings. In the drawings:
-
FIG. 1 is a schematic configuration view of a driving apparatus for vehicle according to a first embodiment of the present invention; -
FIG. 2 is an alignment chart of an operation state (variable speed, reverse rotation) of the driving apparatus for vehicle according to the first embodiment; -
FIG. 3 is an alignment chart of an operation state (fixed reduction ratio, reverse rotation) of the driving apparatus for vehicle according to the first embodiment; -
FIG. 4 is an alignment chart of an operation state (variable speed, normal rotation) of the driving apparatus for vehicle according to the first embodiment; -
FIG. 5 is an alignment chart of an operation state (fixed reduction ratio, normal rotation) of the driving apparatus for vehicle according to the first embodiment; -
FIG. 6 is a schematic configuration view of a driving apparatus for vehicle according to a modified example of the first embodiment of the present invention; -
FIG. 7 is a schematic configuration view of a driving apparatus for vehicle according to a different modified example of the first embodiment of the present invention; -
FIG. 8 is a schematic configuration view of a driving apparatus for vehicle according to a further different modified example of the first embodiment of the present invention; -
FIG. 9 is a schematic configuration view of a vehicle including the driving apparatus for vehicle according to the first embodiment of the present invention; -
FIG. 10 is a schematic configuration view of a driving apparatus for vehicle according to a still further different modified example of the first embodiment of the present invention; and -
FIG. 11 is a schematic configuration view of a driving apparatus for vehicle according to a still further different modified example of the first embodiment of the present invention. - Embodiments according to the present invention are hereinafter described in detail with reference to the drawings.
- As illustrated in
FIG. 1 , a driving apparatus forvehicle 513 according to a first embodiment of the present invention includes a Ravigneauxplanetary gear 501, afriction clutch 502, afriction brake 503, and acontrol mechanism 316. Input paths of two systems and an output path of one system are provided for the Ravigneauxplanetary gear 501 in this configuration. Continuously variable adjustment (control) of output of the one system is achievable by adjusting (controlling) a rotation direction, a rotation speed, and torque of each input of the two systems connected to the Ravigneauxplanetary gear 501 in an opened state of each of thefriction clutch 502 and thefriction brake 503. A vehicle 591 (seeFIG. 9 ) equipped with the driving apparatus forvehicle 513 according to the first embodiment includes a vehicle-side controller (e.g., engine control unit (ECU)) 590 described below to perform the foregoing control. - According to the first embodiment, a continuously variable sub-transmission is adopted instead of the two-speed sub-transmission to solve the conventional issue. This point is hereinafter detailed.
- The Ravigneaux
planetary gear 501 includes afirst sun gear 504, asecond sun gear 505, afirst pinion gear 506, asecond pinion gear 507, aring gear 508, and apinion carrier 509. - Relative rotations of the
second pinion gear 507 and thefirst pinion gear 506 are regulated by theidentical pinion carrier 509. - The
first sun gear 504 engages with thefirst pinion gear 506 via thesecond pinion gear 507. - The
second sun gear 505 engages with thefirst pinion gear 506. Thefirst pinion gear 506 is a gear elongated in the axial direction, and engages with thesecond sun gear 505 on the downstream side of an engagement portion between thefirst pinion gear 506 and thesecond pinion gear 507. - The
first pinion gear 506 and thering gear 508 engage with each other. Thering gear 508 is disposed outside thefirst pinion gear 506. - A first input path of the input paths of the two systems is connected to the
second sun gear 505, while a second input path is connected to thefirst sun gear 504. The output path of the one system is connected to thering gear 508. - In an example, the first input path of the input passes of the two systems in
FIG. 1 is defined by connection between thesecond sun gear 505 and afirst output shaft 515 of anengine 510 provided as an example of an internal combustion engine. The second input path thereof is defined by connection between arotation shaft 516 integrally rotating with arotor 511 a of anelectric motor 511, and thefirst sun gear 504. The upstream side of asecond output shaft 517 provided as the output path of the one system is connected to thering gear 508, while the downstream side of thesecond output shaft 517 is connected to atransmission 512. - A
stator 511 b for therotor 511 a of theelectric motor 511 is fixed to a fixed end (case of driving apparatus for vehicle 513) 520. Therotor 511 a rotates relative to thestator 511 b. - The
friction clutch 502 and thefriction brake 503 are also connected to therotation shaft 516 integrally rotating with therotor 511 a of theelectric motor 511. Accordingly, driving is achievable by closing of thefriction clutch 502 or thefriction brake 503 only with theengine 510 even when electric input from theelectric motor 511 becomes zero as a result of no supply of power from a battery. - The
friction clutch 502 and thefriction brake 503 are configured to be controlled (closed or opened) by closing control under thecontrol mechanism 316. Thecontrol mechanism 316 herein is a hydraulic piston or an electric actuator, for example, which independently closes or opens thefriction clutch 502 and/or thefriction brake 503. For example, thefriction clutch 502 transmits torque by an axial press againstdisks 341 and drivenplates 343 alternately overlapped with each other. In this case, a pressing action is achievable by a direct press with a hydraulic piston or by a press with an electric actuator via a bearing. Thefriction brake 503 stops rotation by an axial press againstdisks 344 and drivenplates 345 alternately overlapped on each other. In this case, a pressing action is achievable by a direct press with a hydraulic piston or by a press with an electric actuator via a bearing. - More specifically, the
friction clutch 502 regulates relative rotations of therotation shaft 516 and thepinion carrier 509 of the Ravigneauxplanetary gear 501, while thefriction brake 503 regulates relative rotations of thepinion carrier 509 of the Ravigneauxplanetary gear 501 and the fixed end (case of driving apparatus for vehicle 513) 520. - The
pinion carrier 509 is connected to adriving ring 342 described below. - More specifically, the
friction clutch 502 and thefriction brake 503 have following configurations as illustrated inFIG. 1 . - The
annular disks 341 for thefriction clutch 502 are connected to an outer surface of aninput side member 340 which is concentrically connected to therotation shaft 516 of theelectric motor 511 and integrally rotates with therotation shaft 516. The drivingring 342, whose rotation axis center is disposed concentrically with therotation shaft 516, includes on the inner surface side thereof the annular drivenplates 343 for thefriction clutch 502 facing thedisks 341. The drivingring 342 is restricted in the axial direction of therotation shaft 516. Theannular disks 344 for thefriction brake 503 are connected to the outer surface side of the drivingring 342. The annular drivenplates 345 for thefriction brake 503 are connected to the inner circumferential surface of the fixed end (case of driving apparatus for vehicle 513) 520 at positions facing theannular disks 344. Note that the drivenplates 345 are restricted in the rotation direction with respect to thefixed end 520, but are movable in the axial direction of therotation shaft 516. In this manner, theannular disks 341 for thefriction clutch 502 and the annular drivenplates 343 for thefriction clutch 502 are alternately disposed with a clearance left between each other. In addition, theannular disks 344 for thefriction brake 503 and the annular drivenplates 345 for thefriction brake 503 are alternately disposed with a clearance left between each other. Accordingly, thedisks 341 and the drivenplates 343 disposed adjacent to each other for thefriction clutch 502 are allowed to contact with each other with pressure or separate from each other to achieve relative rotation regulation by axial forward or backward movement using a hydraulic piston or an electric actuator, for example, under the closing control by thecontrol mechanism 316. Simultaneously, thedisks 344 and the annular drivenplates 345 disposed adjacent to each other for thefriction brake 503 are allowed to contact with each other with pressure or separate from each other to achieve relative rotation regulation. Note that thedisks 344 and the drivenplates 345 for thefriction brake 503 are allowed to achieve forward and backward movement in the axial direction, while the drivingring 342 is restricted in the axial direction. - The
friction clutch 502 is configured to regulate relative rotations of any two elements selected from thefirst sun gear 504, thesecond sun gear 505, thepinion carrier 509, and thering gear 508. Thefriction brake 503 is configured to regulate relative rotations of thepinion carrier 509 and a fixed end (case of driving apparatus for vehicle 513) 520. - The expression “to regulate” herein refers to any action of forward or backward movement of components in the axial direction by driving of the
control mechanism 316 to shift one of the components in the axial direction for contact with each other and thereby achieving connection between the components, to shift one of the components in the axial direction for separation from each other and thereby achieving disconnection between the components, or to shift one of the components in the axial direction for approach to each other and thereby achieving slip between the components with contact therebetween (half-clutch). - An operation of the driving apparatus for
vehicle 513 having this configuration is now described. -
FIG. 2 is an alignment chart of an operation state (variable speed, reverse rotation) of the driving apparatus forvehicle 513.FIG. 3 is an alignment chart of an operation state (fixed reduction ratio, reverse rotation) of the driving apparatus forvehicle 513.FIG. 4 is an alignment chart of an operation state (variable speed, normal rotation) of the driving apparatus forvehicle 513.FIG. 5 is an alignment chart of an operation state (fixed reduction ratio, normal rotation) of the driving apparatus forvehicle 513. - Each of
FIGS. 2 to 5 herein is an alignment chart showing a mechanical relationship between rotation speeds and torques of respective rotation elements in the driving apparatus forvehicle 513. Four vertical lines in a horizontal-axis X direction in each of the alignment charts inFIGS. 2 to 5 represent a gear ratio relationships of rotation elements, i.e., thesecond sun gear 505, thepinion carrier 509, thering gear 508, and thefirst sun gear 504 of the Ravigneauxplanetary gear 501 in this order from the left in the chart, respectively. Each of the four vertical lines indicates two-dimensional coordinates expressing a relative rotation speed in the vertical-axis Y direction. One dotted oblique line indicates rotation speeds, i.e., respective rotation speeds of theelectric motor 511 and theengine 510 provided as an example of an internal combustion engine connected to the output shaft. -
FIG. 2 illustrates a continuously variable transmission mode of the driving apparatus forvehicle 513. In this mode, theengine 510 and theelectric motor 511 have a relationship of reversed rotation directions. Accordingly, the second sun gear 505 (input) and the ring gear 508 (output) have a relationship of reversed rotation directions. In addition, a value of output from thering gear 508 is adjustable by any speed reduction ratio obtained by adjusting the rotation speed of theelectric motor 511 connected to thefirst sun gear 504 via therotation shaft 516 and the rotation speed of theengine 510 connected to thesecond sun gear 505 via thefirst output shaft 515 in a free state of thepinion carrier 509 without closing of thefriction clutch 502 and thefriction brake 503 by thecontrol mechanism 316. The rotation direction, the rotation speed, and the torque output from thering gear 508 are determined in accordance with the rotation directions, the rotation speeds, and the torque of theengine 510 and the electric motor 511 (as for relationship between rotation speeds and torques, see dotted line indicating linear relationship on alignment chart). The respective rotation directions, the rotation speeds, and the torques of theengine 510 and theelectric motor 511 herein are not determined simply by the single driving apparatus forvehicle 513. Instead, the operation states of theengine 510 and theelectric motor 511 are determined and controlled based on comprehensive determination made by the controller (engine control unit (ECU) or the like) 590 at the side of the vehicle equipped with the driving apparatus forvehicle 513 based on a request from a user with reference to respective degrees of efficiency of theengine 510 and theelectric motor 511, a state of a battery, or other conditions. -
FIG. 3 shows a fixed speed reduction ratio mode of the driving apparatus forvehicle 513. In this mode, the second sun gear 505 (input) and the ring gear 508 (output) have a relationship of reversed rotation directions. In addition, the speed reduction ratio is fixed when thepinion carrier 509 is fixed by closing of thefriction brake 503 under thecontrol mechanism 316. Accordingly, a rotation speed of theelectric motor 511 connected to thefirst sun gear 504 and a value of output from thering gear 508 are determined when the rotation speed of theengine 510 connected to thesecond sun gear 505 is determined. -
FIG. 4 shows a continuously variable transmission mode of the driving apparatus forvehicle 513, where the second sun gear 505 (input) and the ring gear 508 (output) have a relationship of rotations in the same direction. In addition, the rotation direction of output from thering gear 508 is equalized when the rotation direction of theelectric motor 511 connected to thefirst sun gear 504 is equalized with the rotation direction of theengine 510 connected to thesecond sun gear 505 by equalization of the rotation directions of theengine 510 and theelectric motor 511 in a free state of thepinion carrier 509 without closing of thefriction clutch 502 and thefriction brake 503 by thecontrol mechanism 316. Moreover, a value of output from thering gear 508 is adjustable by any speed reduction ratio obtained by adjusting the rotation speed of theelectric motor 511 connected to thefirst sun gear 504 and the rotation speed of theengine 510 connected to thesecond sun gear 505. Note herein that input and output rotate in the same direction when theengine 510 and theelectric motor 511 rotate in the same rotation direction. The normal rotation and reverse rotation, and adjustment of the rotation speed of theelectric motor 511 are achievable by using the controller (e.g., inverter) 590. -
FIG. 5 shows a fixed speed reduction ratio mode of the driving apparatus forvehicle 513, where the second sun gear 505 (input) and the ring gear 508 (output) have a relationship of rotations in the same direction. In addition, the speed reduction ratio is fixed to 1 by connection between thepinion carrier 509 and thefirst sun gear 504 via thefriction clutch 502 connected to thepinion carrier 509 by driving of thecontrol mechanism 316. In this case, a rotation speed of theelectric motor 511 connected to thefirst sun gear 504 and a value of output from thering gear 508 are determined when the rotation speed of theengine 510 connected to thesecond sun gear 505 is determined. - When the
transmission 512 is a CVT, thetransmission 512 may be configured by a pair ofpulleys 311 b (only one ofpulleys 311 b is shown, and the other pulley is not shown) capable of adjusting a distance between opposed sheave surfaces 311 a, and a band-shapedmember 311 c such as a belt or a chain laid between the pair ofpulleys 311 b. - According to the first embodiment as described above, the issue of speed change shock or a feeling of discontinuity of acceleration can be solved by making at least continuous (smooth) adjustment of input of the two systems. In other words, there occurs an issue of speed change shock or a feeling of discontinuity of acceleration at the time of rapid regulation of relative rotations by using elements allowing a slight slip but only producing substantially two states of on and off (i.e., discontinuous elements), such as a friction clutch and a friction brake. In this case, the user may be shocked, for example, at the time of an instantaneous stop (brake) of a driving electric motor, for example.
- More specifically, in comparison with the two-speed sub-transmission which switches between high and low speeds in Patent Literature 3, the first embodiment adopting the continuously variable sub-transmission can eliminate speed change shock caused by a speed change of the sub-transmission, or discomfort felt by a user as a result of a discontinuous change of acceleration. Moreover, the driving apparatus for
vehicle 513 functions as a continuously variable sub-transmission when combined with the existingtransmission 512. Accordingly, a transmission gear ratio range (ratio coverage) of the existingtransmission 512 expands, wherefore traveling performance and fuel consumption of the vehicle can improve. Moreover, the driving apparatus forvehicle 513 functioning as a continuously variable sub-transmission achieves smooth operation. Furthermore, addition of theelectric motor 511 can improve fuel consumption of the vehicle. - In a modified example of the first embodiment, as illustrated in
FIG. 6 , the input paths of the two systems may be constituted by a first input path defined by connection between thesecond sun gear 505 and theelectric motor 511, and a second input path defined by connection between thefirst sun gear 504 and theengine 510 provided as an example of an internal combustion engine to make connection between thefriction brake 503 and thering gear 508, and between theoutput 517 and thepinion carrier 509. Note that thecontrol mechanism 316 is capable of shifting the disks and the driven plates forward and backward in the axial direction to perform closing control of thefriction clutch 502 and thefriction brake 503. According to this modified example, effects similar to the effects of the first embodiment can be obtained. - In a different modified example illustrated in
FIG. 7 , the input paths of the two systems may be constituted by a first input path defined by connection between thesecond sun gear 505 and the firstelectric motor 511 provided as a first electric motor, and a second input path defined by connection between thefirst sun gear 504 and a secondelectric motor 531. Astator 531 b for therotor 531 a of theelectric motor 531 is fixed to the fixed end (case of driving apparatus for vehicle 513) 520. Therotor 531 a rotates relative to thestator 531 b. Note that the secondelectric motor 531 inFIG. 7 is disposed at the position of theelectric motor 511 inFIG. 1 . The firstelectric motor 511 is disposed on the upstream side of the secondelectric motor 531 in such a manner as to connect with thefirst output shaft 515 on the downstream side of atorsional vibration damper 521. - According to this different modified example, following effects can be obtained. Generally, an electric motor is required to use a range of small load and low efficiency when necessary driving force is small during driving of a vehicle. In this case, either the first
electric motor 511 or the secondelectric motor 531 is used as an electric motor for driving, while the other of the first and secondelectric motors electric motor 511 and the secondelectric motor 531 to lower each load of the electric motors and achieve driving in a high efficiency range. - In a further different modified example, as illustrated in
FIG. 8 , adifferent clutch 540 may be added between thetorsional vibration damper 521 and thesecond sun gear 505 to allow separation of theengine 510. Thedamper 521 is a damper provided for transmitting a torque of theengine 510, and absorbing and isolating torsional vibration. Aninput side member 540 a of thedifferent clutch 540 is connected to the downstream side of thetorsional vibration damper 521, while anoutput side member 540 b disposed adjacent to theinput side member 540 a and facing theinput side member 540 a is connected to anoutput shaft 541 of thedifferent clutch 540. Theoutput shaft 541 is connected to thesecond sun gear 505. Accordingly, torque of theengine 510 is transmitted to theoutput shaft 541 during closing between theinput side member 540 a and theoutput side member 540 b. However, torque of theengine 510 is not transmitted to theoutput shaft 541 during separation between theinput side member 540 a and theoutput side member 540 b. - According to this different modified example, losses produced by corotation of the engine 510 (friction and pumping losses) can be eliminated when the vehicle is driven only by the
electric motor 511, or when kinetic energy of the vehicle is regenerated into electrical energy by theelectric motor 511. Accordingly, efficiency during driving and a regeneration quantity can improve. - Furthermore, following two combinations may be adopted as modified examples of the combination of any two elements selected from the
first sun gear 504, thesecond sun gear 505, thepinion carrier 509, and thering gear 508 in the first embodiment as a combination of relative rotations regulated by thefriction clutch 502, as well as the combination of thefirst sun gear 504 and thepinion carrier 509 as described above. -
FIG. 10 illustrates a modified example which positions thefriction clutch 502 between thepinion carrier 509 and thering gear 508. More specifically, thepinion carrier 509 and the drivingring 342 are connected to each other. Theannular disks 341 for thefriction clutch 502 are connected to an outer surface of a ring member 340 a. The ring member 340 a in this condition is connected to thering gear 508 and thesecond output shaft 517. -
FIG. 11 illustrates another modified example which positions thefriction clutch 502 between thefirst sun gear 504 and thesecond sun gear 505. More specifically, thefirst sun gear 504 is connected via therotation shaft 516 to arotation ring 342 c which integrally rotates with therotor 511 a of theelectric motor 511. Moreover, theannular disks 341 for thefriction clutch 502 are connected to an outer surface of thefirst output shaft 515. Thefirst output shaft 515 in this condition is connected to thesecond sun gear 505. - According to the foregoing three configuration examples in total, i.e., the embodiment in
FIG. 1 , the modified example inFIG. 10 , and the modified example inFIG. 11 , effects produced by thefriction clutch 502 can be basically obtained as common effects. However, in view of drag torque of thefriction clutch 502 during closing of thefriction brake 503 disposed between thepinion carrier 509 and the fixed end 520 (i.e., during relative rotations ofdisks 341 andplates 343 with friction clutch 502 opened), following differences are produced. Specific description is made below. - (1) According to the configuration example in
FIG. 1 , a relative rotation speed difference is produced between thedisks 341 and theplates 343 of thefriction clutch 502 by an amount of a length of a downward arrow put for thefirst sun gear 504 inFIG. 3 . - (2) According to the configuration example in
FIG. 10 , a relative rotation speed difference is produced between thedisks 341 and theplates 343 of thefriction clutch 502 by an amount of a length of a downward arrow put for thering gear 508 inFIG. 3 . - (3) According to the configuration example in
FIG. 11 , a relative rotation speed difference is produced between thedisks 341 and theplates 343 of thefriction clutch 502 by an amount of the sum of a length of an upward arrow put for thesecond sun gear 505 and the length of the downward arrow put for thefirst sun gear 504 inFIG. 3 . - Summarizing above, the respective levels of the relative rotation speed difference have a relationship of: configuration example (2) in
FIG. 10 <configuration example (1) inFIG. 1 <configuration example (3) inFIG. 11 . Regarding problems caused by a relative rotation speed difference, in the opened state of thefriction clutch 502, a state close to a no-torque transmission state is basically produced. However, in case of a wet clutch or the like which has lubricant between disks and plates even in an opened state, a viscous resistance component in a shearing direction remains, and causes drag torque, i.e., power losses. - Accordingly, in view of drag torque, the order of excellency of the respective configuration examples is considered as the configuration example (2) in
FIG. 10 , the configuration example (1) inFIG. 1 , and the configuration example (3) inFIG. 11 in the descending order. - By properly combining the arbitrary embodiment(s) or modified example(s) of the aforementioned various embodiments and modified example(s), the effects possessed by the embodiment(s) or modified example(s) can be produced. Moreover, combinations of the embodiments, combinations of the working examples, and combinations of the embodiment(s) and the working example(s) may be made. Furthermore, combinations of the features included in the different embodiments or working examples may be made.
- Although the present invention has been fully described in connection with the embodiments thereof with reference to the accompanying drawings, it is to be noted that various changes and modifications are apparent to those skilled in the art. Such changes and modifications are to be understood as included within the scope of the present invention as defined by the appended claims unless they depart therefrom.
- A driving apparatus for vehicle and a vehicle according to the present invention prevent discomfort felt by a user as a result of speed change shock or a discontinuous change of acceleration, and are therefore useful when applied to various types of vehicle including a compact automobile.
-
-
- 311 a. sheave surface
- 311 b. pulley
- 311 c. band-shaped member
- 316. control mechanism
- 340. input side member
- 340 a. ring member
- 341. disk
- 342, 342 b. driving ring
- 342 c. rotation ring
- 343. driven plate
- 344. disk
- 345. driven plate
- 501. Ravigneaux planetary gear
- 502. friction clutch
- 503. friction brake
- 504. first sun gear
- 505. second sun gear
- 506. first pinion gear
- 507. second pinion gear
- 508. ring gear
- 509. pinion carrier
- 510. engine
- 511. electric motor
- 511 a. rotor
- 511 b. stator
- 512. transmission
- 513. driving apparatus for vehicle
- 515. first output shaft
- 516. rotation shaft
- 517. second output shaft
- 520. fixed end (case of driving apparatus for vehicle)
- 521. torsional vibration damper
- 531. second electric motor
- 531 a. rotor
- 531 b. stator
- 540. different clutch
- 540 a. input side member
- 540 b. output side member
- 541. output shaft
- 590. controller
- 591. vehicle
Claims (18)
Applications Claiming Priority (5)
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JP2015-206491 | 2015-10-20 | ||
JP2015206491 | 2015-10-20 | ||
JP2016-183440 | 2016-09-20 | ||
JP2016183440A JP6945287B2 (en) | 2015-10-20 | 2016-09-20 | Vehicle drive and vehicle |
PCT/JP2016/080395 WO2017069041A1 (en) | 2015-10-20 | 2016-10-13 | Vehicle drive device, and vehicle |
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US20180304896A1 true US20180304896A1 (en) | 2018-10-25 |
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US15/769,232 Active 2037-05-06 US10724616B2 (en) | 2015-10-20 | 2016-10-13 | Power transmission apparatus for vehicle and power transmission system for vehicle |
US15/769,176 Abandoned US20180304896A1 (en) | 2015-10-20 | 2016-10-13 | Driving apparatus for vehicle and vehicle |
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US15/769,232 Active 2037-05-06 US10724616B2 (en) | 2015-10-20 | 2016-10-13 | Power transmission apparatus for vehicle and power transmission system for vehicle |
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JP (3) | JP6759027B2 (en) |
CN (3) | CN108136887A (en) |
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Also Published As
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CN108141105B (en) | 2020-08-25 |
US10724616B2 (en) | 2020-07-28 |
US20180304733A1 (en) | 2018-10-25 |
JP2017077884A (en) | 2017-04-27 |
JP2017078508A (en) | 2017-04-27 |
DE112016004789T5 (en) | 2018-07-05 |
CN108136887A (en) | 2018-06-08 |
US20180313439A1 (en) | 2018-11-01 |
JP6945287B2 (en) | 2021-10-06 |
US10788110B2 (en) | 2020-09-29 |
JP6759027B2 (en) | 2020-09-23 |
DE112016004798T5 (en) | 2018-07-19 |
CN108138931B (en) | 2021-11-19 |
JP2017078509A (en) | 2017-04-27 |
DE112016004784T5 (en) | 2018-07-05 |
CN108138931A (en) | 2018-06-08 |
CN108141105A (en) | 2018-06-08 |
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