WO2006132020A1 - ハイブリッド駆動装置 - Google Patents
ハイブリッド駆動装置 Download PDFInfo
- Publication number
- WO2006132020A1 WO2006132020A1 PCT/JP2006/305694 JP2006305694W WO2006132020A1 WO 2006132020 A1 WO2006132020 A1 WO 2006132020A1 JP 2006305694 W JP2006305694 W JP 2006305694W WO 2006132020 A1 WO2006132020 A1 WO 2006132020A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- planetary gear
- electric motor
- output shaft
- gear unit
- output
- Prior art date
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Classifications
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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
- 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
- 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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- 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
- B60K6/42—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
- B60K6/44—Series-parallel type
- B60K6/445—Differential gearing distribution type
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
- B60L15/00—Methods, circuits, or devices for controlling the traction-motor speed of electrically-propelled vehicles
- B60L15/20—Methods, circuits, or devices for controlling the traction-motor speed of electrically-propelled vehicles for control of the vehicle or its driving motor to achieve a desired performance, e.g. speed, torque, programmed variation of speed
- B60L15/2009—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 for braking
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
- B60L50/00—Electric propulsion with power supplied within the vehicle
- B60L50/10—Electric propulsion with power supplied within the vehicle using propulsion power supplied by engine-driven generators, e.g. generators driven by combustion engines
- B60L50/16—Electric propulsion with power supplied within the vehicle using propulsion power supplied by engine-driven generators, e.g. generators driven by combustion engines with provision for separate direct mechanical propulsion
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
- B60L50/00—Electric propulsion with power supplied within the vehicle
- B60L50/50—Electric propulsion with power supplied within the vehicle using propulsion power supplied by batteries or fuel cells
- B60L50/60—Electric propulsion with power supplied within the vehicle using propulsion power supplied by batteries or fuel cells using power supplied by batteries
- B60L50/61—Electric propulsion with power supplied within the vehicle using propulsion power supplied by batteries or fuel cells using power supplied by batteries by batteries charged by engine-driven generators, e.g. series hybrid electric vehicles
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
- B60L7/00—Electrodynamic brake systems for vehicles in general
- B60L7/10—Dynamic electric regenerative braking
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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
- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/04—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units
- B60W10/08—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units including control of electric propulsion units, e.g. motors or generators
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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
- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/10—Conjoint control of vehicle sub-units of different type or different function including control of change-speed gearings
- B60W10/11—Stepped gearings
- B60W10/115—Stepped gearings with planetary 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
- 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
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
- B60L2240/00—Control parameters of input or output; Target parameters
- B60L2240/40—Drive Train control parameters
- B60L2240/48—Drive Train control parameters related to transmissions
- B60L2240/486—Operating parameters
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
- B60L2240/00—Control parameters of input or output; Target parameters
- B60L2240/40—Drive Train control parameters
- B60L2240/50—Drive Train control parameters related to clutches
- B60L2240/507—Operating parameters
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
- B60L2270/00—Problem solutions or means not otherwise provided for
- B60L2270/10—Emission reduction
- B60L2270/14—Emission reduction of noise
- B60L2270/145—Structure borne vibrations
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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
- B60W20/00—Control systems specially adapted for hybrid vehicles
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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
- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
- F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
- F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
- F16H2037/0866—Power split variators with distributing differentials, with the output of the CVT connected or connectable to the output shaft
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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
- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
- F16H37/10—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing at both ends of intermediate shafts
- F16H2037/102—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing at both ends of intermediate shafts the input or output shaft of the transmission is connected or connectable to two or more differentials
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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
- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
- F16H37/10—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing at both ends of intermediate shafts
- F16H2037/104—Power split variators with one end of the CVT connected or connectable to two or more differentials
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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
- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
- F16H37/10—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing at both ends of intermediate shafts
- F16H2037/105—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing at both ends of intermediate shafts characterised by number of modes or ranges, e.g. for compound gearing
- F16H2037/107—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing at both ends of intermediate shafts characterised by number of modes or ranges, e.g. for compound gearing with switching means to provide three variator modes or ranges
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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
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three 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
- F16H2200/202—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set
- F16H2200/2023—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set using a Ravigneaux set with 4 connections
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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
- 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
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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
- Y02T10/70—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
- 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
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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
- Y02T10/72—Electric energy management in electromobility
Definitions
- the present invention relates to a hybrid drive device, and more specifically, an input shaft that receives a drive force of engine power, an output shaft that outputs a drive output to first and second electric motors, a planetary gear unit, and wheels, It is related with the hybrid drive device provided with.
- the apparatus disclosed in this document includes first and second motors (motors / generators) 2 and 3 and a power distribution mechanism including a planetary gear mechanism. And a transmission 41 comprising two planetary gear mechanisms.
- the hybrid drive device described in Patent Document 1 realizes multiple shift speeds by changing the combination of engagement of brakes B1 and B2, one-way clutch Fl, and clutch C1, which are friction engagement elements. To do.
- a stepped transmission mechanism is employed on the lower transmission side of a so-called three-element structure consisting of the first and second electric motors 2, 3 and a single planetary gear mechanism. Therefore, in this configuration, although the motor size can be reduced, a step-shift is performed on the lower side, so that a shock is accompanied at the time of the shift.
- motor is a generic term for “motor”, “motor 'generator” or “generator”, and is indicated by the symbol “MG” unless otherwise specified.
- the planetary gear mechanism can be obtained by combining a plurality of planetary gear mechanisms or a plurality of planetary gear mechanisms, and has functions such as distribution of driving force and deceleration.
- Each device is called a planetary gear device.
- a planetary gear unit alone or a combination of a plurality of planetary gear units and including a rotating element for input, a rotating element for output, and a rotating element for shifting is called a planetary gear unit.
- Patent Document 2 proposes a structural force that eliminates the shock during shifting described above.
- the hybrid drive device proposed in this document is also configured to include an input shaft connected to the engine, first and second electric motors, and a planetary gear unit.
- This device is configured to include a drive transmission mechanism shown in FIG. 1 of the Patent Document 2 (FIG. 8 of the present application is a transcription of this figure as it is).
- This device has, as its operation mode, a first mode on the low speed side and a second mode on the high speed side.
- This apparatus includes an input shaft 12 that receives a driving force from the engine 14 and an output shaft 64 that outputs a driving output to wheels.
- the first and second electric motors 56 and 72 are operatively connected to the energy storage means 76, and exchange electric power with the energy storage means 76.
- Control means 74 is provided to regulate the exchange of power between the energy storage means 76 and the first and second motors 56,72. The control means 74 further adjusts the mutual power exchange between the first motor 56 and the second motor 72.
- the mutual power exchange for the first and second electric motors 56, 72 in the control means 74 is mainly performed by maintaining the rotational speed of the engine 14 at a predetermined rotational speed in the first electric motor 56, and This motor 72 works to assist the driving force that is insufficient with the engine 14 alone.
- this hybrid drive device includes three planetary gear mechanisms 24, 26, 28 and two friction engagement elements 62, 70.
- FIG. 9 of the present application shows the relationship between the vehicle speed and the speed of the engine and each electric motor shown in FIG. 5 of Patent Document 2.
- the lower side of the figure shows the switching state between the first mode and the second mode, and the operating state of each electric motor (generator (denoted as “power generation” in the figure)). Another of what worked as a).
- FIG. 10 of the present application shows the speed (denoted as input speed), the motor torque, and the motor output of the hybrid drive device.
- FIG. 9 The correspondence relationship between FIG. 9 and FIG. 10 is that the upper speed in FIG. 10 corresponds to FIG. 9, and the vehicle speed range shown in FIG. 10 is wider than that in FIG.
- this hybrid drive device is configured to switch between the first mode adopted on the low speed side and the second mode adopted on the high speed side by switching the friction engagement elements. Switching is performed.
- the drive transmission state in this second mode further exceeds the vehicle speed range shown in FIG. However, even if the vehicle speed increases further to the higher speed side, it is maintained as it is.
- the drive transmission state in the first mode is a drive transmission state called "3-element structure", and the drive transmission state in the second mode is a structure called "4-element structure”.
- each rotating element composing the planetary gear unit is indicated by ⁇ , and the connected state of each rotating element is indicated by an arm (horizontal bar and vertical bar).
- the rotating element connected to the engine is (E)
- the rotating element connected to the output is (OUT)
- the rotating element connected to the first electric motor MG1 is (MG1)
- the rotating element connected to the motor MG2 is indicated by (MG2).
- connection refers to a direct connection type in which the rotating element and the one connected to the rotating element have the same rotational speed, and a connection in which the rotating speed of the rotating element and the one connected to the rotating element is a constant ratio It shall include both forms.
- the driving force from the engine E is input to a specific rotation element (first rotation element) of the planetary gear device Pa.
- the rotating element (second rotating element) connected to the first electric motor MG1 mainly functions as a counter-reception, and the remaining rotating element (third rotating element) outputs OUT.
- the second electric motor MG2 is connected to the remaining rotating element (third rotating element). That is, in this planetary gear unit, in the speed diagram, the second and third rotating elements connected to the first electric motor MG1 and the second electric motor MG2 across the first rotating element that receives the engine drive. And the driving force of the third rotating element to which the second electric motor MG2 is connected is output OUT.
- the carrier functions as an idler
- the planetary gear mechanisms 24 and 26 function as a planetary gear unit that defines the three-element structure in the first mode.
- the electric motor 56 serves as the first electric motor MG1
- the electric motor 72 serves as the second electric motor MG2.
- the planetary gear mechanism 28 serves only as a speed reducer.
- this structure has two planetary gear units Pa and Pb.
- the driving force of the engine E is input to a specific rotating element (input rotating element) of one planetary gear device Pa.
- the other two rotating elements of the planetary gear device Pa become rotating elements connected to the output OUT and the second electric motor MG2.
- the rotation element connected to the output OU T is the output rotation element.
- the drive transmission state of this four-element structure consists of an input rotating element connected to the input shaft, an output rotating element connected to the output shaft, and a rotating element connected to the second electric motor.
- this planetary gear unit has four rotating elements as rotating elements arranged on the velocity diagram, and these When the rotational state of two of the rotating elements is determined, the rotating state of the other rotating elements is determined, resulting in a two-degree-of-freedom planetary gear unit.
- Each rotary element is connected to the input shaft from engine E, the output shaft to the wheels, and two motors MG1 and MG2. /
- the planetary gear mechanisms 24, 26, and 28 function as a single body in the second mode, and the electric motor 56 As the first electric motor MG1, the electric motor 72 works as the second electric motor MG2.
- Patent Document 2 realizes drive transmission with a three-element structure in the first mode on the low speed side, and a four-element structure in the second mode on the higher speed side.
- this figure shows the hybrid drive device speed (upper stage), motor torque (middle stage), and motor output (in the invention described in Patent Document 2).
- (Lower) Each figure is shown in a box, which indicates the line division in each figure.
- “3Lo” indicates the “drive transmission in the three-element structure on the low speed side” described above
- “4Hi” indicates the “drive transmission in the four-element structure on the high speed side” described above. ing. Therefore, “3Lo” corresponds to the first mode described so far, and “4Hi” corresponds to the second mode.
- Ne, Nmgl, Nmg2, and Nout in the upper diagram on the right side are the speeds of the input shaft I, the first motor MG1, the second motor MG2, and the output shaft O in the order listed. Speed).
- Tmgl and Tmg2 indicate the torques of the first electric motor MG1 and the second electric motor MG2 in the order of description.
- Pmgl and Pmg2 in the lower diagram indicate outputs of the first electric motor MG1 and the second electric motor MG2 in the order of description. This output corresponds to the fact that this is a positive state, the motor is acting as a motor, and the negative state is acting as a generator.
- FIG. 9 corresponding to FIG. 5 of Patent Document 2
- the switching from the first mode to the second mode is performed as shown in FIG. It is performed at the vehicle speed at the vertical line position shown in Fig. 1.
- the vertical line indicates that the switching force from the first mode to the second mode is performed.
- the first mode on the low speed side and the second mode on the high speed side are provided as modes, and in the second mode, the drive transmission state of the four-element structure is Maintained. Since this drive transmission state is maintained even in a higher speed region, in the higher vehicle speed region (region closer to the right end in the figure in FIG. 9), the second electric motor works as a motor while This motor works as a generator, and its output is relatively large.
- Patent Document 1 JP-A-2005-61498
- Patent Document 2 Japanese Patent No. 3220115
- a rotating element connected to the engine is inserted in the speed diagram and connected to the first electric motor MG1 and the second electric motor MG2 on both sides thereof.
- a rotating element is positioned.
- the rotating element OUT that bears the output and the rotating element to which the second electric motor MG2 is connected are the same rotating element. For this reason, the inertial force remaining in the state where the regenerative brake is applied works on the output OUT side, but this can be directly received by the second motor MG2.
- the first and second electric motors MG1, MG2 are located at both ends of the four-element structure as a whole in the speed diagram. . Inside, a rotating element that receives the output of the engine and a rotating element connected to the output side are arranged.
- the engine is inserted in the velocity diagram.
- the first electric motor MG1 and the second electric motor MG2 are located on both sides.
- the first and second motors MG1 and MG2 are located at both ends of the four-element structure as a whole in the velocity diagram, and the inner side thereof.
- a rotating element that receives the output of engine E and a rotating element that is connected to the output OUT side are positioned.
- a lever that uses the input position of the engine drive as a fulcrum is assumed. That's fine.
- the second motor MG2 and output OUT are at high speeds, but their fulcrum forces are the same in their operating positions in the three-element structure.
- the first electric motor MG1 only needs to generate a torque corresponding to the moment with the input position of the engine drive as a fulcrum.
- the positions of the output OUT and the second electric motor MG2 are different from each other and the position of the second electric motor MG2 is distant from the fulcrum force at which the engine drive is input. Therefore, the first electric motor MG1 needs to generate a torque in the reverse direction larger than that of the three-element structure.
- FIG. 3 and 10 the lower diagram is a diagram showing the motor output.
- the horizontal axis represents the vehicle speed and the vertical axis represents the motor output. Therefore, the high-speed area is an area close to the right end in the figure.
- Fig. 3 shows the output when the driving transmission state of the three-element structure according to the present application is adopted in this region
- Fig. 10 shows the output when the driving transmission state of the four-element structure is adopted in this region. Yes. Comparing the results shown in Fig. 3 and Fig. 10, the change rate (increase rate of the output difference between the two motors) with the increase in travel speed of the first and second motor outputs is larger in Fig. 10, and the four-element structure It turns out that it is disadvantageous.
- the present invention has been made in view of the above problems, and an object of the present invention is to provide a noble drive with two electric motors and a planetary gear unit between an input shaft and an output shaft.
- the device it is possible to realize a continuously variable transmission without engaging a stepped shift in a shift involving disengagement of a plurality of friction engagement elements, preventing a reduction in energy recovery efficiency during regeneration, and a high vehicle speed.
- the object is to obtain a hybrid drive device that does not cause a decrease in transmission efficiency in the drive force region (negative hybrid region).
- An input shaft that receives driving force from the engine, an output shaft that outputs a driving output to the wheels, a first and second electric motor, a planetary gear unit, and a first gear between the input shaft and the output shaft.
- a first friction engagement element that forms a drive transmission state; a second friction engagement element that forms a second drive transmission state between the input shaft and the output shaft; the input shaft and the output And a third friction engagement element that forms a third drive transmission state between the shaft and the shaft, the characteristic configuration of the hybrid drive device is that the first drive transmission state is the planetary gear unit.
- the input shaft is connected to the first rotating element of the planet, the first electric motor is connected to the second rotating element of the planetary gear unit, and the output is supplied to the third rotating element of the planetary gear unit.
- a shaft and the second electric motor are connected, and the second drive transmission
- the state is a state in which the input shaft, the output shaft, the first electric motor, and the second electric motor are independently connected to the four rotating elements of the planetary gear unit.
- the input shaft is connected to the first rotating element of the planetary gear unit
- the first electric motor is connected to the second rotating element of the planetary gear unit
- a reduction ratio smaller than the reduction ratio in the first drive transmission state is formed.
- the reduction ratio means [input rotational speed Z output rotational speed] in the hybrid drive device, and specifically, [rotational speed Z of input shaft I in an embodiment described later. Rotation speed of output shaft O].
- This hybrid drive device realizes the first to third drive transmission states as the drive transmission state in accordance with the engagement and disengagement of the friction engagement elements.
- the input shaft is connected to the first rotation element of the planetary gear unit.
- the first electric motor is connected to the second rotating element of the planetary gear unit, and the output shaft and the second electric motor are connected to the third rotating element of the planetary gear unit. That is, the drive transmission state of the three-element structure described above is realized and reduced. The speed ratio is different.
- the input shaft, the output shaft, the first motor, and the second motor are connected. That is, the drive transmission state of the four-element structure described above is realized.
- this second drive transmission state is disadvantageous for the three-element structure
- this second drive transmission state is affected by the reduction ratio range of the first and third drive transmission states. It is possible to set the range of the specific reduction ratio. Therefore, as a result, it is possible to keep the energy conversion efficiency within an allowable range during regeneration.
- the planetary gear unit and a limited number of frictional engagement elements receive the engine driving force and distribute the driving force to the first and second motors. While acting as a generator or motor, energy recovery efficiency can be prevented from decreasing during regeneration, and there is no significant reduction in transmission efficiency in the high vehicle speed 'low driving force region (negative hybrid region). A hybrid drive device could be obtained.
- the engagement and the disengagement of the two frictional engagement elements among the first to third frictional engagement elements are operated in conjunction with each other. It is preferable to do.
- the two friction engagement elements one friction engagement element is engaged and the other force S is disengaged. Therefore, the engagement between the least frictional engagement elements Different drive transmission states can be realized by the disengagement operation, and the change of the drive transmission state can be performed stably. As a result, a highly reliable hybrid drive device can be obtained.
- two friction engagement elements among the first to third friction engagement elements are provided on the condition that the rotational speeds of the two members engaged by the friction engagement elements are the same. It is preferable that the engagement state is switched so that the drive transmission state is switched.
- the first friction engagement element is a brake that stops rotation of the rotation element of the planetary gear device that functions as a speed reducer in the engaged state, and in the first drive transmission state, Preferably, only the first friction engagement element is engaged, and the rotation of the third rotation element of the planetary gear unit is decelerated by the reduction gear and transmitted to the output shaft.
- the first electric motor acts as a reaction force receiver for the driving force of the engine force, and the output shaft from the rotating element (third rotating element) connected to the rotor of the second electric motor. It becomes the structure which transmits a drive rotation to. Therefore, in the transmission, a relatively large reduction ratio can be realized by using the first friction engagement element to reduce the speed using the planetary gear device that functions as a reduction gear.
- the second friction engagement element is a clutch that directly connects one rotation element of the planetary gear unit and the output shaft in the engagement state, and is in the second drive transmission state.
- the second friction engagement element is engaged, and the output shaft is directly connected to the one rotation element among the four rotation elements of the planetary gear unit.
- the output shaft is directly connected to one of the four rotating elements (output rotating element) of the planetary gear unit.
- the drive rotation that can be obtained in the drive transmission state can be directly transmitted to the output shaft. Therefore, it has the simplest structure and one drive transmission state (second Can be realized.
- the third friction engagement element is a clutch that directly connects two rotating elements of one planetary gear mechanism in the engaged state, and in the third drive transmission state, the third friction engagement element is the clutch. It is preferable that the rotation of the third rotating element of the planetary gear unit is transmitted to the output shaft as it is by engaging only the frictional engagement element and fixing the planetary gear mechanism. In the drive transmission state, the third rotation element of the planetary gear unit is directly connected to the output shaft by engagement of the clutch, so that the drive rotation that can be obtained in the third drive transmission state is directly applied to the output shaft. Can be transmitted to. Therefore, with the simplest structure, it is possible to realize one drive transmission state (third drive transmission state) that is essential for V in the present application.
- first and second electric motors and the switching mechanism including the first to third friction engagement elements are provided on the same axis, and the first to second output motors are arranged from the engine side toward the output shaft side.
- the first motor, the second motor, and the structure are preferably arranged in this order.
- the hybrid drive unit can be made smaller on the output shaft side connected to the wheels, making it easier to adopt in a car with a conventional configuration.
- the planetary gear unit includes three planetary gear mechanisms, and in the third drive transmission state, one planetary gear mechanism is fixed by engagement of a third friction engagement element, It is preferable that the third rotating element of the planetary gear unit and the output shaft rotate at the same speed.
- one planetary gear mechanism realizes the same speed rotation state (direct connection state) between the third rotating element and the output shaft, and the remaining planetary gear mechanism (there is one remaining! May be a combination of the two), which distributes the driving force of the engine power between the first and second motors and determines the driving rotation that can be obtained with the third rotating element.
- the number of planetary gear combinations is small.
- the required number of drive transmission states can be realized.
- the second drive transmission state is connected to the input shaft as the planetary gear unit.
- Input rotating element connected to the output shaft, and rotating element force connected to the second electric motor.
- a hybrid drive device including an input shaft that receives a driving force of an engine force, an output shaft that outputs a driving output to a wheel, first and second electric motors, and a planetary gear unit.
- the input shaft is connected to the first rotating element of the planetary gear unit, wherein the second rotation elements of the planetary gear unit first motor is connected, the third of the Yu star gear unit
- the output shaft and the second electric motor are connected to the rotating elements of the first mode driven by a three-element structure, and the four rotating elements of the planetary gear unit are independent of the input shaft and the output, respectively.
- Three driving modes in the driven third mode The mode is to switch in the order of the first mode, the second mode, and the third mode as the reduction ratio decreases.
- the hybrid drive device having this configuration has a third mode on the higher speed side (lower reduction ratio side) than the first mode and the second mode of the conventional hybrid drive device.
- this third mode a three-element drive drive state is adopted.
- the drive speed is obtained with a three-element structure that reduces the first mode
- the drive output is obtained with the four-element structure in the second mode
- a three-element structure is directly connected to the high-speed side.
- a drive output can be obtained.
- the driving force of engine power as the first electric motor, the second electric motor, and the planetary gear unit is distributed between the first and second electric motors.
- a planetary gear device that works as a split device, and a planetary gear device that works as a speed reducer for the drive output of the third rotating element in the drive transmission state of the second motor and the three-element structure are arranged coaxially.
- a configuration may be adopted in which the first electric motor, the split device, the second electric motor, and the reduction gear are arranged in this order from the engine side to the output shaft side.
- the engine side force is also equipped with large equipment in order, and as a whole, the output drive side connected to the wheel and the hybrid drive device can be made small, and it is easy to adopt it in a car with a conventional configuration. Become.
- the apparatus includes three friction engagement elements and two planetary gear units as the planetary gear unit, and distributes the driving force of the engine force between the first electric motor and the second electric motor. It is preferable that an output mechanism for selectively outputting the output after distribution to the output shaft is provided at a position where the engine force within the drive device body is also farthest away.
- the hybrid drive device as a whole can be reduced in size on the output shaft side, and can be easily adopted in a vehicle having a conventional configuration.
- FIG. 1 is a skeleton diagram showing a drive transmission system of the hybrid drive device M according to the present application.
- the hybrid drive device M receives the drive force of the engine E provided on the left side in the figure on the input shaft I and outputs it from the right output shaft O after shifting.
- the hybrid drive device M includes two electric motors (first and second electric motors MG1, MG2), and as a planetary gear unit, a planetary gear device that distributes the driving force of the engine, And a reduction gear having three friction engagement elements (first and second clutches CI and C2 and brake B1), and these are arranged coaxially.
- First and second electric motors The first and second electric motors MG1 and MG2 are configured to include a stator st provided in the casing C and a rotor rt that is rotatable relative to the stator st, and are electrically connected to the power storage device B, respectively.
- the electric power storage device B or the other electric motor MG acting as a generator is supplied with electric power and operates.
- the electric storage device B can store electric power or supply electric power to the other electric motor MG that functions as a motor.
- the hybrid drive device M is provided with a control device CPU that controls the operation of the drive device M, and the control device CPU controls the speed of the first and second electric motors MG1, MG2. Do.
- the control device CPU is configured to receive accelerator pedal and brake pedal operation information, engine rotation speed information, and input shaft I and output shaft O rotation speed information.
- the control unit CPU determines whether to accelerate or decelerate according to a predetermined sequence of the driver's operating force from these input information, and monitors the state of the engine E along with this determination. Determine the output rotational speed of the hybrid drive M necessary to give the desired acceleration or deceleration.
- an intermediate shaft Ml and a connection shaft S1 supported rotatably with respect to the intermediate shaft Ml are configured.
- a damper D is inserted between the input shaft I and the intermediate shaft Ml.
- the driving device M is provided with three planetary gear mechanisms. These planetary gear mechanisms are called first, second, and third planetary gear mechanisms PI, P2, and P3 in order from the input shaft I side. . As shown in the figure, the first and third planetary gear mechanisms PI and P3 are of a single pion type, and the second planetary gear mechanism P2 is of a double pion type. [0053]
- the intermediate shaft Ml will be described. The intermediate shaft Ml is configured to rotate integrally with the carrier shaft ca of the first and third planetary gear mechanisms PI, P3. Therefore, the input shaft I is connected to the carrier shaft ca of the first and third planetary gear mechanisms PI, P3.
- the ring gear of the first planetary gear mechanism P1 the rotor rt of the second motor MG2, the sun gear s of the second planetary gear mechanism P2, and the sun gear of the third planetary gear mechanism P3 It is configured to rotate integrally with s.
- the rotor rt of the first electric motor MG1 adopts a structure that rotates integrally with the sun gear s of the first planetary gear mechanism P1!
- the drive device M includes three friction engagement elements (first and second clutches CI and C2, and a brake B1).
- These three friction engagement elements CI, C2, and B1 are determined to be engaged / disengaged according to an operation command from the control device CPU.
- the first clutch C1 determines engagement / disengagement between the ring gear!: Constituting the third planetary gear mechanism P3 and the output shaft O.
- the ring gear! Constituting the third planetary gear mechanism P 3 and the output shaft O rotate together, but in the engaged state, the first planetary gear mechanism P1 and the third planetary gear mechanism P1
- the planetary gear mechanism P3 has a four-element structure, and the rotation of the ring gear r of the third planetary gear mechanism P3 is transmitted to the output shaft O.
- the third planetary gear mechanism P3 does not affect the rotation of the output shaft O.
- the brake B1 and the second clutch C2 determine engagement / disengagement of the casing C or the connection shaft S1, which is a ground, and the carrier shaft ca of the second planetary gear mechanism P2.
- the hybrid drive device M In the hybrid drive device M according to the present application, three modes of a first mode, a second mode, and a third mode are set.
- the first mode is the first drive transmission state
- the second mode is the second drive transmission state
- the third mode is the third drive transmission state.
- the first mode corresponds to the low speed range, and is indicated as “Lo” in FIGS. 2 and 3 (corresponding to FIG. 10 relating to the background art).
- the second mode corresponds to the medium speed range and is shown as “Mid” in FIGS.
- the third mode corresponds to the high speed range and is shown as “Hi” in FIGS.
- the medium speed region in the structure of the present application corresponds to the high speed region of Patent Document 2. Therefore, the present application can be regarded as a configuration in which a further high-speed region is newly provided with respect to the conventional structure described in Patent Document 2.
- the transmission state in each mode is as follows.
- the rotor rt force of the first electric motor MG1 and the sun gear s are integrally rotated, so that the first electric motor MG1 functions as a reaction force receiver for the engine driving force.
- the second electric motor MG2 works for output assist.
- this transmission state corresponds to the drive transmission state of the three-element structure described above, and the rotational speed that can be extracted from the first planetary gear mechanism P1 is further reduced by the second planetary gear mechanism P2 to the output shaft O. I will tell you. Therefore, Fig. 2 shows the first mode (Lo).
- the friction engagement element (brake B1) force that realizes the first drive transmission state corresponds to the first friction engagement element.
- This velocity diagram is a diagram representing the relationship between the rotational speeds of the rotating elements of the planetary gear unit on a straight line.
- the vertical lines in this speed diagram are the rotating element that rotates together with the first electric motor MG1 (described as MG1 in the figure) and the rotating element that may be fixed to the ground via the brake B1 (from the left side in the figure).
- Rotation speed of output shaft 0 (denoted as OUT on the diagram), intermediate shaft Ml (denoted as ENG in the diagram) and connecting shaft S1 (denoted as MG2 in the diagram) It is a vertical axis indicated by.
- this velocity diagram shows the relative relationship of the gear ratio between the rotating elements in the horizontal axis direction.
- the speed of connecting shaft S1 is determined as the speed obtained in MG2 by the speed line connecting (MG1, ENG, MG2). Further, regarding the second planetary gear mechanism P2, the speed of the output shaft O is determined as the speed obtained at OUT by the speed line connecting (MG2, OUT, g). Therefore, MG1, ENG, and MG2 at vehicle speed vl are as shown in the figure.
- FIG. 3 is a diagram showing the relationship among the input speed, the motor torque, and the motor output in the hybrid drive device M according to the present application.
- the force that shows two thin vertical lines on the right side of the vertical axis shown at the left end is the switching speed between the first mode and the second mode in this application, and the second mode and the third mode. Corresponding to the switching speed with the switch.
- the description regarding the first mode is “3Lo”
- the description regarding the second mode is “4Mid”
- the description regarding the third mode is “3Hi”.
- the description of the intermediate shaft Ml, the first motor MG1, the second motor MG2, and the output shaft O is the same as that shown in FIG.
- the input shaft rotation to which the engine E force driving force is transmitted is kept constant, and the rotation of the second electric motor MG2 increases the speed. Accordingly, the rotation of the first electric motor MG1 decreases.
- the second electric motor MG2 mainly serves as a motor
- the first electric motor MG1 mainly serves as a generator. In this first mode, the output of each motor falls within a limited range in its absolute value, which is half the IJ.
- the first clutch C1 is maintained in the engaged state, and the brake B1 is maintained in the disengaged state. Therefore, the transmission from the input shaft I to the output shaft O is performed by the first planetary gear mechanism P1 and the third Determined by planetary gear mechanism P3. In other words, it is transmitted to the intermediate shaft Ml via the damper D
- the engine rotation is driven by a drive distribution determined by the gear ratio of the four rotating elements of the first planetary gear mechanism Pl and the third planetary gear mechanism P3. It is transmitted to the ring gear r of P3 and transmitted to the output shaft O.
- the second electric motor MG2 mainly functions as a reaction force receiver.
- this transmission state corresponds to the drive transmission state of the four-element structure described above, and the output that can be taken out via the first planetary gear mechanism P1 and the third planetary gear mechanism P3 is transmitted to the output shaft O as it is. Will be. Therefore, the second mode (Mid) is described in FIG. 2 .Friction engagement element (clutch C1) force that realizes the second drive transmission state with respect to the friction engagement element Second friction engagement Corresponds to the element.
- the engine E force and the driving force are transmitted.
- the input shaft rotation is kept constant, and the rotation of the second electric motor MG2 increases as the speed increases.
- the rotation of the first electric motor MG1 increases.
- the second electric motor MG2 shifts from a function as a motor to a function as a generator
- the first electric motor MG1 shifts from a function as a generator to a function as a motor.
- the output of each motor is within the limited range in the absolute value even in the second mode.
- the first clutch Cl and the brake B1 are disengaged, and the second clutch C2 is maintained in the engaged state.
- the connecting shaft S1 and the output shaft O are at the same speed.
- the shock can be eliminated by engaging and disengaging the friction engagement elements in a state where the same speed condition is satisfied.
- the second clutch C2 is engaged and the other frictional engagement elements CI, B1 are kept disengaged, so the transmission from the input shaft I to the output shaft O is the first planetary gear. Determined by mechanism Pl and second planetary gear mechanism P2.
- the sun gear s and the carrier shaft ca of the second planetary gear mechanism P2 rotate in the same direction, and the connection shaft S1 and the output shaft O are directly connected. It becomes a state.
- the engine driving force transmitted to the intermediate shaft Ml via the damper D undergoes a shift determined by the first planetary gear mechanism P1, is transmitted to the ring gear r of the first planetary gear mechanism P1, and is directly output to the output shaft O. It is transmitted to.
- the rotor rt force of the first electric motor MG1 and the sun gear s are rotated together with the first electric motor MG1, so that the first electric motor MG1 works as a reaction force receiver of the engine driving force. .
- this transmission state corresponds to the drive transmission state of the three-element structure described above, and the output that can be taken out via the first planetary gear mechanism P1 is transmitted to the output shaft O as it is. . Therefore, FIG. 2 shows the third mode (Hi).
- the friction engagement element (clutch C2) that realizes the third drive transmission state corresponds to the third friction engagement element.
- the first planetary gear mechanism P1 is obtained on the connecting shaft S1 by the speed line connecting (MG1, ENG, MG2) indicated by v4, v5, v6. (MG2, ENG, OUT) indicated by v4, v5, and v6.
- the speed line determines the speed of the output shaft o.
- the motor output of each electric motor is within the limited range even in the third mode, even in the absolute value.
- the first planetary gear mechanism P1 functions as a split device that distributes engine drive between the first and second electric motors MG1, MG2.
- the second planetary gear mechanism P2 corresponds to a planetary gear device that acts as a speed reducer with the brake B1 engaged.
- the brake B1, the first clutch Cl, and the second clutch C2 form the disengagement referred to in this application.
- the ring gear r of the second planetary gear mechanism P2 is provided with respect to the output shaft O so as to be integrally rotatable.
- the first clutch C1 is between the ring gear r of the third planetary gear mechanism P3 and the output shaft O
- the second clutch C2 is between the carrier shaft ca of the second planetary gear mechanism P2 and the sun gear s.
- the output to the output shaft O is selected by the engagement selection between the first and second clutches Cl and C2.
- the second and third planetary gear mechanisms P2, P3 and the first and second clutches C1, C2 serve as output mechanisms for selective output.
- Figure 4 shows the propulsive force that can be achieved. This figure shows the vehicle speed on the horizontal axis and the propulsive force on the vertical axis.
- the areas covered by the first mode, second mode, and third mode are shown.
- the hybrid drive device M shown in the present application it is possible to perform good speed change with sufficient margin while operating the engine at its most efficient rotational speed.
- the hybrid drive device includes two electric motors.
- three planetary gear mechanisms PI, P2, P3 and three friction engagement elements CI, C2, B1 are provided between the input shaft I and the output shaft O.
- the first mode As the operation mode (drive transmission state), the first mode (first drive transmission state) that further reduces and outputs the rotation speed of the three-element structure for the low speed range, and the rotation obtained by the four-element structure for the medium speed range It is possible to realize the second mode (second drive transmission state) that outputs the speed as it is and the third mode (third drive transmission state) that outputs the rotation speed obtained by the three-element structure for the high speed range as it is. Yes.
- Each of the three different embodiments shown below maintains the above-described technical structure, and, as described above, two clutches (the first clutch C1 and the second clutch) are used as friction engagement elements. C2) and one brake B1.
- the switching of the engagement and the disengagement is the same switching mode as described in Table 1, and the first force can also realize the third mode.
- the corresponding velocity diagram is also the same.
- the names of the planetary gear mechanisms are called first, second, and third planetary gear mechanisms PI, P2, and P3 in the order in which they are arranged from the input shaft I side to the output shaft O side.
- the example shown in FIG. 5 is an example in which the input shaft I is provided on the left side and the output shaft O is provided on the right side in the figure, as shown in FIG.
- the rotation of the input shaft I is configured to be taken into the first intermediate shaft Ml via the damper D, and this first intermediate shaft Ml is connected to the ring gear r of the first planetary gear mechanism P1.
- the structure which rotates integrally is employ
- the sun gear s of the first planetary gear mechanism P1 is configured to rotate integrally with the ring gear r of the second planetary gear mechanism P2, and is directly connected to the rotor rt of the first electric motor MG1.
- the carrier shaft ca of the first and second planetary gear mechanisms Pl, P2 is configured to rotate integrally with the second intermediate shaft M2, and this second intermediate shaft M2 is located on the lower side. In this way, the output shaft O can be engaged and disengaged via the first clutch C1.
- the sun gear s of the second planetary gear mechanism P2 is configured to rotate integrally with the connection shaft S1, and this connection shaft S1 is configured to rotate integrally with the rotor rt of the second electric motor MG2.
- a second clutch C2 is provided for the connecting shaft S1, and the connecting shaft S1 is configured to be rotatable integrally with the ring gear r of the third planetary gear mechanism P3.
- P3 is configured so that its ring gear r can be engaged with the ground via the brake B1, and the carrier shaft ca is integrated with the output shaft O, and its sun gear s rotates together with the connecting shaft S1. The configuration is adopted!
- the first mode and the second mode described above with respect to the prior art can be realized in the released state of the second clutch C2.
- the third mode the first clutch and the brakes CI and B1 are released, and the second clutch C2 is engaged to connect the connection shaft S1 and the output shaft O to the third planet. It can be directly connected via the gear mechanism P3.
- the first and second planetary gear mechanisms PI and P2 are integrated can be realized.
- the first and second planetary gear mechanisms PI, P2 correspond to planetary gear devices that act as split devices, and the third planetary gear mechanism with the brake B1 engaged.
- P3 corresponds to a planetary gear unit that acts as a reduction gear.
- the brake Bl, the first clutch Cl, and the second clutch C2 constitute the disengagement referred to in this application.
- the carrier shaft ca of the third planetary gear mechanism P3 is provided so as to be integrally rotatable with respect to the output shaft O.
- the first clutch C1 is engaged between the second intermediate shaft M2 and the output shaft O
- the second clutch C2 is engaged between the ring gear r of the third planetary gear mechanism P3 and the sun gear s. It is configured to be disengageable.
- the output to the output shaft O is selected by selecting the engagement between the first and second clutches Cl and C2. Therefore, the third planetary gear mechanism P3 and the first and second clutches CI and C2 serve as output mechanisms for selective output.
- the example shown in FIG. 6 is an example having an input shaft I on the left side and an output shaft O on the right side, as shown in FIG.
- a configuration is adopted in which the first planetary gear mechanism P1 and the second planetary gear mechanism P2 constitute a so-called rabbi type planetary gear device Pr. That is, the second planetary gear mechanism P2 is of a double pion type, and the carrier shaft of the pion located on the inner diameter side thereof is the first planetary gear mechanism P1 and the second planetary gear mechanism P2.
- the carrier axis is referred to as a common carrier axis (in the following description, this carrier axis is referred to as a common carrier axis cac).
- the second planetary gear mechanism P2 is of a double pion type, but the carrier shafts ca of both pions of this planetary gear mechanism P2 rotate at the same speed.
- the rotation of the input shaft I is configured to be taken into the first intermediate shaft Ml via the damper D, and this first intermediate shaft Ml Is configured so as to rotate integrally with a common carrier shaft ca c disposed across the first planetary gear mechanism P1 and the second planetary gear mechanism P2. This rotation is transmitted to the second planetary gear mechanism P2 and also to the carrier shaft cai located on the outer diameter side of the double beon.
- the rotor rt of the first electric motor MG1 is connected to the second planetary gear mechanism via the first connection shaft S1. It is configured to rotate integrally with the P2 sun gear s.
- the rotor rt of the second electric motor MG2 is configured to be rotatable integrally with the sun gear s of the first planetary gear mechanism P1, and this rotation is performed on the lower transmission side via the connecting shaft S2.
- a configuration is adopted in which the sun gear s of the planetary gear mechanism P3 is rotated and the ring gear r of the third planetary gear mechanism P3 is rotated by the engagement of the second clutch C2.
- the sun gear s of the third planetary gear mechanism P3 is transmitted with the rotation of the second connecting shaft S2, and the carrier shaft ca rotates integrally with the output shaft O.
- the ring gear r of the third planetary gear mechanism P3 is driven by the sun gear s according to the engagement / disengagement state of the brake B1 and the second clutch C2, and the third planetary gear mechanism P3 It is configured to be able to transmit to the output shaft O via the carrier shaft ca.
- the ring gear r is fixed, the rotation of the second connecting shaft S2 is decelerated, and the output shaft O It is transmitted.
- the planetary gear transmission state is realized by the sun gear s of the second planetary gear mechanism P2, the pion provided on the common carrier shaft cac, and the sun gear s of the first planetary gear mechanism P1.
- the third planetary gear mechanism P3 is fixed. The rotational force of the connecting shaft S2 is transmitted to the output shaft O as it is.
- the output (rotation of the second connecting shaft S2) obtained by the three-element speed reducing structure constituted by the first planetary gear mechanism P1 and the second planetary gear mechanism P2 Can be decelerated by the third planetary gear mechanism P3 and transmitted to the output shaft O as the rotation of the carrier shaft ca of the planetary gear mechanism P3.
- the first and second planetary gear mechanisms Pl and P2 correspond to planetary gear devices that act as split devices, and the brake B1 is engaged.
- the third planetary gear mechanism P3 corresponds to a planetary gear device that functions as a reduction gear.
- the first and second planetary gear mechanisms Pl and P2 serving as the split devices and the three planetary gear mechanisms P3 serving as the speed reducers constitute the output mechanism referred to in the present application.
- the brake B1, the first clutch Cl, and the second clutch C2 form the disengagement referred to in this application.
- the example shown in FIG. 7 is an example in which the input shaft I is provided on the right side and the output shaft O is provided on the central left side, contrary to the case shown in FIG.
- the rotation of the input shaft I is configured to be taken into the first intermediate shaft Ml via the damper D.
- the first intermediate shaft Ml is connected to the ring gear r of the first planetary gear mechanism P1 and the second
- the planetary gear mechanism P2 has a structure that rotates together with the carrier shaft ca of the P2.
- the sun gear s of the first planetary gear mechanism P1 is connected to the rotor rt of the first electric motor MG1 .
- the second planetary gear mechanism P2 its ring gear r force is provided on the connecting shaft SI that rotates integrally with the carrier shaft ca of the first planetary gear mechanism PI, and the carrier shaft ca is integrated with the first intermediate shaft Ml. Rotate.
- the sun gear s of the second planetary gear mechanism P2 is provided on the second intermediate shaft M2 that rotates integrally with the rotor rt of the second electric motor MG2 on the lower transmission side.
- the second intermediate shaft M2 is provided with the sun gear s of the third planetary gear mechanism P3 and is configured to be rotatable integrally with the carrier shaft ca of the third planetary gear mechanism P3 by the second clutch C2. It has been.
- the third planetary gear mechanism P3 is configured such that the ring gear r rotates integrally with the output shaft O.
- the carrier shaft ca of the third planetary gear mechanism P3 can rotate integrally with the second intermediate shaft M2 via the second clutch C2, and can be fixed to the ground via the brake B1.
- a three-element structure is transmitted to the second intermediate shaft M2 through the first planetary gear mechanism P1 and the second planetary gear mechanism P2, and this output is transmitted to the third planetary gear mechanism. Decelerated in mechanism P3 and transmitted to output shaft O.
- the first and second planetary gear mechanisms Pl, P2 correspond to planetary gear devices that act as split devices, and the brake B1 is engaged.
- the third planetary gear mechanism P2 corresponds to a planetary gear device that functions as a reduction gear.
- the brake B1, the first clutch Cl, and the second clutch C2 form the disengagement referred to in this application.
- the ring gear r of the third planetary gear mechanism P3 is provided so as to be integrally rotatable with respect to the output shaft O.
- the first clutch C1 is engaged between the connection shaft S1 and the output shaft O
- the second clutch C2 is engaged between the second intermediate shaft M2 and the carrier shaft ca of the third planetary gear mechanism P3. It is configured to be disengageable.
- the output to the output shaft O is selected by the engagement selection between the first and second clutches C 1 and C 2. Therefore, the third planetary gear mechanism P3 and the first and second clutches CI and C2 serve as output mechanisms for selective output.
- a hybrid drive device that includes two electric motors between the input shaft and the output shaft and also includes a planetary gear unit, it is effective at a speed change that involves engagement / disengagement of a plurality of friction engagement elements. It is a configuration that can realize a continuously variable transmission without performing a step shifting, preventing a decrease in energy recovery efficiency during regeneration, and causing a decrease in transmission efficiency in a high vehicle speed / low driving force region (negative hybrid region). A hybrid drive that never I was able to get it.
- FIG. 1 is a diagram showing a drive transmission system of a hybrid drive device according to the present application.
- FIG. 3 A diagram showing the relationship between the speed, torque and output of the hybrid drive device according to the present application.
- FIG. 4 A diagram showing the propulsive force obtained by the hybrid drive device according to the present application in each mode.
- FIG. 6 is a diagram showing a drive transmission system of another embodiment of the hybrid drive device according to the present invention.
- FIG. 6 is a diagram showing a drive transmission system of another embodiment of the hybrid drive device according to the present application.
- FIG. 7 is another embodiment of the hybrid drive device according to the present application.
- FIG.8 Diagram of drive transmission system of conventional hybrid drive system
- FIG. 9 is a diagram showing motor and engine speeds in a conventional hybrid drive device.
- FIG. 10 is a diagram showing the relationship between speed, torque and output of a conventional hybrid drive device.
Abstract
Description
Claims
Priority Applications (1)
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DE112006001124T DE112006001124T5 (de) | 2005-06-07 | 2006-03-22 | Hybridantriebseinheit |
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JP2005-166945 | 2005-06-07 | ||
JP2005166945A JP2006341647A (ja) | 2005-06-07 | 2005-06-07 | ハイブリッド駆動装置 |
JP2005-166946 | 2005-06-07 | ||
JP2005166946A JP2006341648A (ja) | 2005-06-07 | 2005-06-07 | ハイブリッド駆動装置 |
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WO2006132020A1 true WO2006132020A1 (ja) | 2006-12-14 |
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PCT/JP2006/305694 WO2006132020A1 (ja) | 2005-06-07 | 2006-03-22 | ハイブリッド駆動装置 |
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US (1) | US20060276288A1 (ja) |
DE (1) | DE112006001124T5 (ja) |
WO (1) | WO2006132020A1 (ja) |
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JP2005112019A (ja) * | 2003-10-03 | 2005-04-28 | Toyota Motor Corp | ハイブリッド車の駆動装置 |
JP2005132143A (ja) * | 2003-10-28 | 2005-05-26 | Nissan Motor Co Ltd | ハイブリッド変速機のエンジン始動制御装置 |
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- 2006-03-22 DE DE112006001124T patent/DE112006001124T5/de not_active Withdrawn
- 2006-03-22 WO PCT/JP2006/305694 patent/WO2006132020A1/ja active Application Filing
- 2006-06-01 US US11/444,319 patent/US20060276288A1/en not_active Abandoned
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JP2005016570A (ja) * | 2003-06-24 | 2005-01-20 | Nissan Motor Co Ltd | ハイブリッド車のモード遷移制御装置 |
JP2005061498A (ja) * | 2003-08-11 | 2005-03-10 | Toyota Motor Corp | ハイブリッド車の駆動装置 |
JP2005067319A (ja) * | 2003-08-21 | 2005-03-17 | Toyota Motor Corp | ハイブリッド車の駆動装置 |
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Cited By (2)
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JP2009248825A (ja) * | 2008-04-08 | 2009-10-29 | Aisin Aw Co Ltd | ハイブリッド駆動装置 |
JP2014105860A (ja) * | 2012-11-26 | 2014-06-09 | Hyundai Motor Company Co Ltd | ハイブリッド自動車の動力伝達装置 |
Also Published As
Publication number | Publication date |
---|---|
US20060276288A1 (en) | 2006-12-07 |
DE112006001124T5 (de) | 2008-05-08 |
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