WO2007138777A1 - 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
- WO2007138777A1 WO2007138777A1 PCT/JP2007/055344 JP2007055344W WO2007138777A1 WO 2007138777 A1 WO2007138777 A1 WO 2007138777A1 JP 2007055344 W JP2007055344 W JP 2007055344W WO 2007138777 A1 WO2007138777 A1 WO 2007138777A1
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- WIPO (PCT)
- Prior art keywords
- planetary gear
- gear
- rotating element
- clutch
- mode
- Prior art date
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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
- B60L58/00—Methods or circuit arrangements for monitoring or controlling batteries or fuel cells, specially adapted for electric vehicles
- B60L58/10—Methods or circuit arrangements for monitoring or controlling batteries or fuel cells, specially adapted for electric vehicles for monitoring or controlling batteries
- B60L58/12—Methods or circuit arrangements for monitoring or controlling batteries or fuel cells, specially adapted for electric vehicles for monitoring or controlling batteries responding to state of charge [SoC]
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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
- 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
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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
- B60K6/22—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
- 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
- B60K6/50—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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- 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
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- B—PERFORMING OPERATIONS; TRANSPORTING
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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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- 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
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- 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
- B60W10/02—Conjoint control of vehicle sub-units of different type or different function including control of driveline clutches
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- B—PERFORMING OPERATIONS; TRANSPORTING
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- 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
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- B—PERFORMING OPERATIONS; TRANSPORTING
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- 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
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- 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
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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
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- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
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- 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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- 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
- B60L2260/00—Operating Modes
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- B60L2260/26—Transition between different drive modes
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- 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
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- B60W20/00—Control systems specially adapted for hybrid vehicles
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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
- 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
- F16H2037/088—Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft
- F16H2037/0886—Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft with switching means, e.g. to change ranges
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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
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- 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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- F16H—GEARING
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- 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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- F16H—GEARING
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- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2043—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with five engaging means
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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
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- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
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- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
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- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2048—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with seven engaging means
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
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- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/62—Hybrid vehicles
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
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- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/64—Electric machine technologies in electromobility
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
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- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/70—Energy storage systems for electromobility, e.g. batteries
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- 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
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- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/72—Electric energy management in electromobility
Definitions
- the present invention includes an input shaft connected to an engine, an output shaft connected to wheels, a rotating electrical machine, a first planetary gear device, and a second planetary gear device, and is an electric torque converter.
- the present invention relates to a hybrid drive device having a functioning state.
- Patent Document 1 describes a configuration as shown in FIG.
- This hybrid drive device includes an input shaft I connected to the engine, an output shaft O connected to the wheels, a first rotating electric machine Ml, a second rotating electric machine M2, and a double pinion type planetary gear unit PG.
- a power distribution mechanism SP is provided, and an automatic transmission AT is connected in series via the transmission member T between the power distribution mechanism SP and the output shaft O.
- the planetary gear device PG has a sun gear ss, a carrier cas supporting a plurality of pairs of pin-on gears which are in mesh with each other, and a ring gear rs which is in mesh with the sun gear ss through the pin-on gears as a rotating element.
- the carrier cas is connected to the input shaft I and an engine (not shown), the sun gear ss is connected to the first rotating electric machine Ml, and the ring gear rs is connected to the transmission member T and the second rotating electric machine M2.
- a switching brake BO is provided between the sun gear ss and the case Ds
- a switching clutch CO is provided between the sun gear ss and the carrier cas.
- the rotational speed is in the order of the carrier cas, the ring gear rs, and the sun gear ss. Therefore, when the first rotary electric machine Ml connected to the sun gear ss functions as a reaction force receiver for rotational torque of the input shaft 1 (engine), the rotation of the input shaft I (engine) connected to the carrier cas is decelerated. Is transmitted to the ring gear. Then, the rotation of the ring gear rs is transmitted to the automatic transmission AT via the transmission member T, and is output from the output shaft O.
- the relationship of ⁇ is established. Therefore, for example, when the gear ratio ⁇ is about 0.5, the torque equivalent to the engine torque is shared by the first rotating electric machine Ml, and a torque of about twice the engine torque is output from the carrier cas.
- the planetary gear device PG functions as an electric torque converter that starts the vehicle while amplifying and outputting the rotational torque of the engine by the torque of the first rotating electrical machine Ml.
- Patent Document 1 JP-A-2005-206136 (FIGS. 37-38, FIG. 17) Disclosure of the Invention
- the rotational torque force generated by the first rotating electric machine Ml is a reaction force with respect to the rotational torque of the input shaft I (engine) on the gear PG. Therefore, according to the upper limit of the rotational torque generated by the first rotary electric machine Ml and the gear ratio ⁇ of the planetary gear device PG, the rotational torque that can be transmitted from the planetary gear device PG to the transmission member ⁇ side, ie, the output shaft ⁇ side
- the upper limit is fixed.
- the upper limit of the rotational torque transmittable to the output shaft side is increased by reducing the gear ratio of the planetary gear device PG, the amplification factor of the engine torque as an electric torque converter is reduced.
- the present invention has been made in view of the above problems, and an object thereof is a hybrid drive device having a state of functioning as an electric torque converter, which has a relatively small output torque force S. It is an object of the present invention to provide a passive drive device capable of transmitting large rotational torque to the output shaft side even when used.
- a characteristic configuration of a hybrid drive device including an output shaft connected to the rotary electric machine, a first planetary gear device, and a second planetary gear device is the first planetary gear device. Transmits the second planetary gear set to the second planetary gear set by decelerating the absolute value of the rotational speed of the rotary electric machine, and the second planetary gear set transmits the rotation transmitted from the first planetary gear set and the input shaft. The point is that the rotation is synthesized and the absolute value of the rotational speed of the input shaft is decelerated and transmitted to the output shaft.
- connection includes a structure that directly transmits rotation, and also includes a structure that indirectly transmits rotation via one or more members.
- order of rotation speed is either “high-speed side facing low-speed side” or “low-speed side facing“ high-speed side ”. Depending on the state of rotation, it can be either, but in any case the order of rotation elements does not change.
- planet gear device a device obtained by the planetary gear mechanism alone or by combining a plurality of planetary gear mechanisms.
- rotary electric machine is used as a concept including the!, Deviation of an electric motor, a generator (generator), and a motor generator that functions as both a motor and a generator as required.
- the absolute value of the rotational speed of the rotating electrical machine is reduced by the first planetary gear device, It is transmitted to the two planetary gear system.
- the rotational torque of the input shaft (engine) is amplified using the rotational torque transmitted from the first planetary gear device as a reaction force, and is transmitted to the output shaft. Therefore, even when a rotating electrical machine having a relatively small output torque is used, a torque obtained by amplifying the rotating torque of the rotating electricity can be used as a reaction force by the first idle gear device. Therefore, it becomes possible to transmit a large rotational torque to the output shaft side, which can not reduce the amplification factor of the engine torque as the electric torque converter.
- the rotating element to which the rotation of the input shaft in the second planetary gear device is transmitted is provided with a first clutch that selectively transmits the rotation of the rotating electric machine, and the engagement of the first clutch In parallel mode in which the input shaft and the rotating electrical machine are It is preferable to
- the input shaft and the rotary electric machine are directly connected by engaging the first clutch, and the input shaft is manufactured using the same rotary electric machine that operates in the electric torque converter mode. It is possible to realize a parallel mode in which traveling is performed while the rotational torque of the (engine) is assisted by the rotational torque of the rotary electric machine.
- the rotational speed of the input side rotational member of the first clutch and the rotational speed of the output side rotational member of the first clutch are the same. It is preferable that the synchronous switching which performs engagement of 2 is comprised possible. By virtue of such construction, it is possible to greatly reduce the impact due to the engagement of the first clutch at the time of mode switching from the electric torque converter mode to the parallel mode.
- the parallel mode is configured to have a plurality of shift speeds.
- the absolute value of the rotational speed of the input shaft is accelerated and transmitted to the output shaft, and the absolute value of the rotational speed of the rotating electrical machine is decelerated to the output shaft. It is preferable to further include a transmission for increasing speed.
- a first clutch for selectively transmitting the rotation of the rotating electrical machine to the rotating element to which the rotation of the input shaft in the second planetary gear device is transmitted, and the rotation of the input shaft
- a second clutch selectively transmitting the rotation element of the planetary gear unit, wherein the input shaft is engaged with the first clutch engaged and the second clutch disengaged.
- the electric traveling mode is configured to be separated from the output shaft and to transmit the rotation of the rotating electrical machine to the output shaft.
- the first planetary gear set and the second planetary gear set have a plurality of shift speeds in the electric travel mode.
- the vehicle can travel in the electric travel mode over a wide speed range.
- the present invention includes an input shaft connected to an engine, an output shaft connected to wheels, a rotating electric machine, a first planetary gear device, and a second planetary gear device.
- Another characteristic configuration of the drive device is that the first planetary gear device and the second planetary gear device respectively have three rotations of at least a first rotation element, a second rotation element, and a third rotation element in order of rotational speed.
- the rotating electric machine is connected to the first rotating element, the second rotating element is fixed to the non-rotating member, and in that state, the absolute value of the rotating speed of the third rotating element
- the gear ratio is set such that the speed of the second planetary gear unit is reduced with respect to the absolute value of the rotational speed of the first rotating element, and the second planetary gear device has the input shaft connected to the first
- the output shaft is connected to the element, and the third rotating element is In that the third rotating element of the planetary gear device is connected.
- the hybrid drive device functions as an electric torque converter for amplifying the rotational torque of the engine and outputting the rotational torque of the engine while gradually increasing the reaction torque by gradually increasing the rotational torque of the rotating electrical machine.
- the rotational torque of the input shaft (engine) is amplified by using the rotational torque amplified by reducing the absolute value of the rotational speed of the rotary electric machine by the first planetary gear device as a reaction force. Can be transmitted to Therefore, the output torque is relatively small Even when a rotary electric machine is used, it is possible to transmit a large rotational torque to the output shaft without reducing the amplification factor of the engine torque as an electric torque converter.
- a first clutch for selectively connecting the first rotating element of the first planetary gear set and the first rotating element of the second planetary gear set.
- the hybrid drive system uses the same rotating electrical machine that works as the electric torque converter to assist the rotational torque of the input shaft (engine) with the rotational torque of the rotating electrical machine. It can be made to function as a parallel type hybrid drive device which runs while traveling.
- the input of the first clutch is selected. Synchronous switching is possible in which the first clutch is engaged with the rotational speeds of the side rotation member and the output side rotation member being the same. Therefore, at the time of the state switching, the impact due to the engagement of the first clutch can be extremely reduced.
- a second clutch be provided to selectively connect the first rotating element of the second planetary gear set and the input shaft.
- this hybrid drive device uses the same rotary electric machine that functions as the electric torque converter, and travels by using only the rotational torque of the rotary electric machine while the engine is stopped. Can function as a driving device for the
- a third clutch selectively connecting the second rotation element of the first planetary gear set to the input shaft, and the non-rotation member of the second rotation element of the first planetary gear set
- the first brake selectively performing fixation, and the third rotating element of the first planetary gear set and the third rotating element of the second planetary gear set connected to each other are selectively selected as non-rotating members. It is preferable to include one or more of the second brakes to be fixed. According to this structure, when this hybrid drive system is made to function as a parallel type hybrid drive system or a drive system for electric travel, it can be configured to have a plurality of shift speeds.
- the second planetary gear set includes an intermediate rotary element between the second rotary element and the third rotary element in order of rotational speed, and the intermediate rotary element of the second planetary gear set It is preferable to provide a third brake for selectively fixing the wheel to the non-rotational member.
- this hybrid drive system when this hybrid drive system is made to function as a parallel type hybrid drive system or a drive system for electric travel, it can be configured to have more gear stages.
- the second planetary gear set includes an intermediate rotating element between the second rotating element and the third rotating element in the order of rotational speed, and the intermediate rotating element of the second planetary gear set It is preferable to have a fourth clutch that selectively connects the two and the input shaft.
- the hybrid drive system when the hybrid drive system functions as a parallel type hybrid drive system, it can be configured to have a reverse gear.
- the present invention includes an input shaft connected to an engine, an output shaft connected to a wheel, a rotating electrical machine, a first planetary gear device, and a second planetary gear device.
- the first planetary gear set and the second planetary gear set each have at least a first rotational element, a second rotational element, and a third rotational element in order of rotational speed.
- the first planetary gear device has the first rotating element connected to the rotating electrical machine, the third rotating element is fixed to the non-rotating member, and the second planetary gear device comprises the first rotating element
- the input shaft is connected to the second rotation element
- the output shaft is connected to the second rotation element
- the second rotation element of the first planetary gear set is connected to the third rotation element.
- the rotational torque of the rotating electrical machine transmitted to the second planetary gear device via the first planetary gear device is used as a reaction force
- the second planetary gear device is used.
- the reaction force and the rotation of the input shaft can be synthesized, and the absolute value of the rotational speed of the input shaft can be decelerated and transmitted to the output shaft. Therefore, the hybrid drive device functions as an electric torque converter for amplifying the rotational torque of the engine and outputting the rotational torque of the engine while gradually increasing the reaction torque by gradually increasing the rotational torque of the rotating electrical machine.
- the rotational torque of the input shaft (engine) is amplified by using the rotational torque amplified by reducing the absolute value of the rotational speed of the rotary electric machine by the first planetary gear device as a reaction force. Can be transmitted to Therefore, even when using a rotating electrical machine having a relatively small output torque, it is possible to transmit a large rotational torque to the output shaft without reducing the amplification factor of the engine torque as an electric torque converter. It becomes.
- a first clutch for selectively connecting the first rotating element of the first planetary gear set and the first rotating element of the second planetary gear set.
- the input shaft and the rotary electric machine can be directly coupled by engaging the first clutch. Therefore, the hybrid drive system uses the same rotating electrical machine that works as the electric torque converter to assist the rotational torque of the input shaft (engine) with the rotational torque of the rotating electrical machine. It can be made to function as a parallel type hybrid drive device which runs while traveling.
- the input of the first clutch is selected. Synchronous switching is possible in which the first clutch is engaged with the rotational speeds of the side rotation member and the output side rotation member being the same. Therefore, at the time of the state switching, the impact due to the engagement of the first clutch can be extremely reduced.
- a second clutch be provided to selectively connect the first rotating element of the second planetary gear device and the input shaft.
- this hybrid drive Functions as a drive device for electric travel, which travels only by the rotational torque of the rotating electric machine while the engine is stopped using the same rotary electric machine that works as the electric torque converter functions. It can be done.
- a first brake that selectively fixes the third rotating element of the first planetary gear set to the non-rotating member, a second rotating element of the first planetary gear set connected to each other, and It is preferable to include at least one second brake for selectively fixing the third rotating element of the second planetary gear set to the non-rotating member.
- the hybrid drive device when the hybrid drive device is made to function as a parallel type hybrid drive device or a drive device for electric travel, it can be configured to have a plurality of shift speeds.
- this hybrid drive device can also function as a drive device for engine travel that travels only by the rotational torque of the input shaft (engine) without using the rotational torque of the rotating electrical machine.
- the hybrid drive device when the hybrid drive device is engaged with the second brake to switch to a state where it functions as a drive device for engine travel by acting as an electric torque converter, the input side rotation of the second brake is performed. It is configured to be able to perform synchronous switching in which the second brake is engaged while the rotational speeds of the member and the output side rotation member are the same. Therefore, at the time of the said state change, the impact by engagement of said 2nd brake can be made very small.
- a third clutch selectively connecting the second rotary element of the first planetary gear set and the third rotary element of the second planetary gear set connected to each other and the input shaft.
- the second planetary gear set includes an intermediate rotary element between the second rotary element and the third rotary element in the order of rotational speed, and the intermediate rotary element and the input of the second planetary gear set It is preferable to be configured to include a third clutch that selectively connects with the shaft.
- the hybrid drive system when the hybrid drive system functions as a parallel type hybrid drive system, it can be configured to have more gear stages.
- the second planetary gear set includes an intermediate rotating element between the second rotating element and the third rotating element in the order of rotational speed, and the intermediate rotating of the second planetary gear set
- a third brake is provided to selectively secure the element to the non-rotating member.
- the hybrid drive device when the hybrid drive device is made to function as a parallel type hybrid drive device or a drive device for electric travel, it can be configured to have more gear stages.
- this hybrid drive device can also function as a drive device for engine travel that travels only by the rotational torque of the input shaft (engine) without using the rotational torque of the rotating electrical machine.
- the hybrid drive device is switched to a state in which the third brake is engaged to function as a driving force for engine travel by engaging the third brake, the input side rotation of the third brake is performed. It is configured to be able to perform synchronous switching in which the third brake is engaged while the rotational speeds of the member and the output side rotation member are the same. Therefore, at the time of the state switching, the impact due to the engagement of the third brake can be made extremely small.
- FIG. 1 is a skeleton diagram showing a configuration of a hybrid drive device H according to the present embodiment.
- FIG. 2 is a schematic view showing a system configuration of the hybrid vehicle drive device H according to the present embodiment.
- the double solid line shows the transmission path of the driving force
- the double broken line shows the transmission path of the electric power
- the hollow arrows show the flow of the hydraulic fluid.
- solid arrows indicate transmission paths of various information.
- the drive unit H has an input shaft I connected to the engine E, an output shaft O connected to the wheels W, a motor 'generator MG, and a first planetary gear.
- a device P1 and a second planetary gear device P2 are provided. These components are accommodated in a drive case Ds (hereinafter simply referred to as "case Ds") as a non-rotational member fixed to the vehicle body.
- the motor generator MG corresponds to the “rotating electric machine” in the present invention.
- the input shaft I is connected to the engine E.
- engine E Various known engines such as gasoline engines and diesel engines can be used.
- the input shaft I is integrally connected to an output rotation shaft such as a crankshaft of the engine E. It is also preferable that the input shaft I be connected to the output rotation shaft of the engine E via a damper or a clutch.
- the output shaft O is integrally configured with the external gear Og in the present embodiment.
- the output shaft O is connected so as to be able to transmit the rotational driving force to the wheel W via a gear train (not shown) engaged with the external gear Og, the differential device 17 shown in FIG.
- the motor 'generator MG has a stator St fixed to the case Ds, and a rotor Ro rotatably supported radially inward of the stator St.
- the rotor Ro of the motor generator MG is connected to rotate integrally with the carrier cal of the first planetary gear set P1.
- the motor 'generator MG is electrically connected to a battery 11 as a storage device via an inverter 12.
- the motor's generator MG is capable of performing both the function as a motor generating power by receiving supply of electric power and the function as a generator generating power by receiving supply of power. There is.
- motor 'generator MG performs power generation by the rotation of output shaft O by the rotation of input shaft I by engine E and the inertia force during deceleration of the vehicle being transmitted to carrier cal and driven to rotate. , Charge the battery.
- the motor 'generator MG functions as a drive motor that supplements the drive force for traveling the vehicle.
- the first planetary gear unit P1 is configured of a double gear-on type planetary gear mechanism coaxially arranged with the input shaft I. That is, the first planetary gear unit P1 has, as rotating elements, a carrier cal for supporting a plurality of gear sets, and a sun gear s1 and a ring gear rl, which are engaged with the gear sets.
- the carrier cal is connected to rotate integrally with the motor generator MG.
- the ring gear rl is selectively fixed to the case Ds via the first brake B1, and selectively connected to the input shaft I via the third clutch C3.
- the sun gear si is connected to rotate integrally with the sun gear s2 of the second planetary gear device P2.
- the gear ratio of the first planetary gear unit P1 is determined as follows: With the ring gear r1 fixed to the case Ds by the first brake B1, the sun gear s 1 turns The absolute value of the rotational speed is set to be reduced relative to the absolute value of the rotational speed of the carrier cal.
- the carrier cal, the ring gear rl, and the sun gear si are respectively the “first rotating element (1)” and the “second rotating element (2)” of the first planetary gear device P1 in the present invention. , And "the third rotation element (3)".
- the second planetary gear device P2 is configured by a single gear type planetary gear mechanism coaxially arranged with the input shaft I. That is, the second planetary gear device P2 has, as rotating elements, a carrier ca2 for supporting a plurality of pinion gears, and a sun gear s2 and a ring gear r2 which respectively mesh with the pinion gears.
- the ring gear r2 is selectively connected to the carrier cal of the first planetary gear unit P1 via the first clutch C1, and selectively connected to the input shaft I via the second clutch C2. That is, in the ring gear r2, the rotation of the input shaft I is selectively transmitted by the second clutch C2, and the rotation of the motor generator MG is selectively transmitted by the first clutch C1.
- the carrier ca2 is connected to rotate integrally with the output shaft O.
- the sun gear s2 is connected to rotate integrally with the sun gear si of the first planetary gear device P1.
- the sun gears si and s2 are selectively fixed to the case Ds via the second brake B2.
- the ring gear r2, the carrier ca2, and the sun gear s2 force are respectively the "first rotating element (1)”, the “second rotating element (2)", and the second planetary gear device P2 in the present invention. It corresponds to the "third rotation element (3)".
- the driven drive device H includes, as friction engagement elements, the first clutch C1, the second clutch C2, and the third clutch C3, and the first brake B1 and the second brake B2.
- these friction engagement elements it is possible to use a multiple disc clutch or multiple disc brake operated by hydraulic pressure.
- the hydraulic pressure supplied to these friction engagement elements is controlled by the hydraulic control device 13 operated by the control command of the control device ECU force.
- the supply of hydraulic fluid to the hydraulic control device 13 is performed by the mechanical oil pump 14 while the engine E is in operation, and is supplied by the electric oil pump 15 while the engine E is stopped.
- the mechanical oil pump 14 is driven by the rotational driving force of the input shaft I.
- the electric oil pump 15 is driven by the electric power (supply path is not shown) from the battery 11 supplied via the electric oil pump inverter 16.
- the frictional engagement elements Cl, C2, C3, Bl and B2 are not shown as being included in the first planetary gear unit PI and the second planetary gear unit P2.
- FIG. 3 is a schematic diagram showing the connection state of each component of the hybrid drive device H in a more simplified manner.
- the respective rotating elements of the first planetary gear unit P1 and the second planetary gear unit P2 are arranged laterally in the order of rotational speed and connected by broken lines, and are connected to these respective rotating elements. Components are connected by solid lines.
- the first planetary gear unit P1 has a carrier cal, a ring gear rl, and a sun gear si in the order of rotational speed.
- the second planetary gear device P2 has a ring gear r2, a carrier ca2 and a sun gear s2 in the order of rotational speed.
- the sun gear s 1 of the first planetary gear unit P1 and the sun gear s2 of the second planetary gear unit P2 are connected so as to rotate integrally.
- the carrier cal of the first planetary gear device P1 is connected to rotate integrally with the motor 'generator MG, and is connected to the ring gear r2 of the second planetary gear device P2 via the first clutch C1. It is possible to connect selectively.
- the ring gear rl of the first planetary gear unit P1 can be selectively fixed to the case Ds via the first brake B1, and selectively connected to the input shaft I via the third clutch C3. It is made possible.
- the ring gear r2 of the second planetary gear device P2 is selectively connectable to the carrier of the first planetary gear device P1 via the first clutch C1, and the input shaft via the second clutch C2 It is possible to selectively connect to I.
- the carrier ca2 of the second planetary gear set is connected to rotate integrally with the output shaft O.
- the sun gear si of the first planetary gear unit P1 and the sun gear s2 of the second planetary gear unit P2 connected to each other can be selectively fixed to the case Ds via the second brake B2.
- the control unit ECU uses the information acquired by the sensors Sel to Se6 provided in each part of the vehicle, and via the engine E, motor 'generator MG and hydraulic control unit 13 It controls the operation of the friction engagement elements of the first planetary gear set P1 and the second planetary gear set P2, the electric oil pump 15, and the like.
- these sensors in this example, an engine rotational speed sensor Sel, a motor 'generator' rotational speed sensor Se2, a battery state detection sensor Se3, a vehicle speed sensor Se4, an accelerator operation detection sensor Se5, and a brake Operation detection sensor Se6 is provided.
- the engine rotational speed sensor Se 1 is a sensor for detecting the rotational speed of the output rotary shaft of the engine E.
- the motor 'generator rotational speed sensor Se2 is a sensor for detecting the rotational speed of the rotor Ro of the motor' generator MG.
- the battery state detection sensor Se3 is a sensor for detecting a state such as the charge amount of the battery 11.
- the vehicle speed sensor Se4 is a sensor for detecting the rotational speed of the output shaft O in order to detect the vehicle speed.
- An accelerator operation detection sensor Se5 is a sensor for detecting an operation amount of the accelerator pedal 18.
- the brake operation detection sensor Se6 is a sensor for detecting the amount of operation of the brake pedal 19 linked to a wheel brake (not shown).
- control unit ECU includes an engine control unit 31, a motor 'generator control unit 32, a battery state detection unit 33, a motor' generator rotation detection unit 34, and a vehicle speed detection unit 35.
- Switching control means 36 mode 'gear position selecting means 37, electric oil pump control means 38, engine rotation detecting means 39, required driving force detecting means 40, and engine stop condition judging means 41.
- Each of these means in the control unit ECU is implemented by hardware and / or software (program) or both, with an arithmetic processing unit such as a CPU as the core member, and performing various processing on input data. It is organized.
- the engine control means 31 performs operation control such as operation start / stop of the engine E, rotational speed control, output torque control and the like.
- the motor 'generator control means 32 performs operation control such as rotational speed control and rotational torque control of the motor' generator MG via the inverter 12.
- the battery state detection means 33 detects a state such as the charge amount of the battery 11 based on the output of the battery state detection sensor Se3.
- the motor 'generator rotation detecting means 34 detects the rotational speed of the motor / generator MG based on the output of the motor / generator rotational speed sensor Se2.
- the vehicle speed detection means 35 detects the vehicle speed based on the output from the vehicle speed sensor Se4.
- the switching control means 36 controls the operation of the hydraulic control device 13 in accordance with the operation mode and the gear position selected by the mode / gear position selection means 37, whereby each friction engagement element Cl, C2 of the hybrid drive device H , C3, Bl, B2 engagement or disengagement, and performs control to switch the operation mode and gear of the hybrid drive unit H.
- Mode 'gear selection means 37 selects the operation mode and gear in accordance with a control map as shown in FIG.
- FIG. 6 is a diagram showing an example of a control map defining the relationship between the speed (vehicle speed) of the vehicle and the required driving force, and the coverage of each gear in the electric torque converter mode and the parallel mode.
- the horizontal axis is the vehicle speed
- the vertical axis is the required driving force.
- the mode 'gear position selection means 37 selects an appropriate operation mode and gear position according to the control map according to the vehicle speed and the required driving force. Specifically, the mode 'gear selection means 37 acquires information on the vehicle speed from the vehicle speed detection means 35. Also, the mode 'gear stage selection means 37 acquires information on the required driving force from the required driving force detection means 40. Then, according to the control map shown in FIG. 6, the mode 'gear position selection means 37 selects the operation mode and the gear position defined in accordance with the acquired vehicle speed and the required driving force.
- the mode 'gear selection means 37 selects the electric torque converter mode during start acceleration of the vehicle or when the vehicle speed is very low. In the other states, the mode 'gear selection means 37 selects each gear in the parallel mode or the electric travel mode in accordance with the vehicle speed, the required driving force, and the like. The electric travel mode is selected when it is determined by the engine stop condition determination unit 41 that the engine stop condition is satisfied.
- the electric oil pump control means 38 controls the operation of the electric oil pump 15 via the electric oil pump inverter 16.
- the engine rotation detection means 39 detects the rotation speed of the output rotation shaft of the engine E based on the output from the engine rotation speed sensor Sel.
- the required driving force detection means 40 calculates and acquires the required driving force by the driver based on the outputs from the accelerator operation detection sensor Se5 and the brake operation detection sensor Se6.
- the engine stop condition determining means 41 determines whether or not the engine stop condition is satisfied.
- the engine stop condition is, for example, a combination of various conditions such as the vehicle speed, the required driving force, the charge amount of the battery 11, the cooling water temperature, the lubricating oil temperature, the exhaust catalyst temperature, and the elapsed time from engine start. It is stipulated that stopping engine E represents an appropriate condition.
- FIG. 4 shows one or more operation modes and one or more operation modes. It is an operation table which shows the operating state of each friction engagement element CI in a gear, C2, C3, Bl, B2. In this figure, “o” indicates that each frictional engagement element is in the engaged state. On the other hand, “no mark” indicates that each frictional engagement element is in the disengaged state.
- FIG. 5 is a diagram showing the relationship between switchable operation modes and shift speeds. Note that the white arrows in this figure indicate the relationship in which synchronous switching is possible.
- FIG. 6 is a view showing an example of a control map used to select the operation mode and the gear in the mode 'gear selection means 37 as described above.
- FIG. 7 and 8 show velocity diagrams of the first planetary gear unit P1 and the second planetary gear unit P2, and FIG. 7 is a velocity diagram in the electric torque converter mode. 8 shows the velocity diagram in parallel mode. Note that “1st” and “2nd” in Figure 8 are the same as the velocity diagram in the electric travel mode.
- the vertical axis corresponds to the rotational speed of each rotation element. That is, "0" corresponding to the vertical axis indicates that the rotational speed is zero, the upper side is positive, and the lower side is negative.
- the plurality of vertical lines arranged in parallel correspond to the respective rotation elements of the first planetary gear set P1 and the second planetary gear set P2.
- each vertical line corresponds to the carrier cal of the first planetary gear unit PI, ring gear rl and sun gear s 1 respectively
- “r 2”, “Ca2” and “s2” correspond to the ring gear r2, carrier ca2 and sun gear s2 of the second planetary gear unit P2, respectively.
- the distance between the vertical lines corresponding to the respective rotating elements corresponds to the gear ratio of the first planetary gear device P1 and the second planetary gear device P2.
- a straight line L1 indicates the operating state of the first planetary gear device P1
- a straight line L2 indicates the operating state of the second planetary gear device P2.
- each straight line indicates the operating state of the first planetary gear unit P1 and the second planetary gear unit P2 at each shift speed.
- ⁇ is the rotational speed of motor 'generator MG
- ⁇ is the rotational speed of input shaft 1 (engine E)
- ⁇ is the rotational speed of output shaft O
- X indicates the brakes respectively.
- the hybrid drive device H uses an electric torque converter mode, a parallel mode, and an electric travel mode using one motor generator MG. It is configured to be able to switch between the three operation modes. Further, the hybrid drive device H has four gear stages in the parallel mode and has two gear stages in the electric travel mode.
- the operation mode and the switching of the shift speed in each operation mode are controlled by the hydraulic control device 13 according to a control command from the switching control means 36 of the control device ECU to control the friction engagement elements Cl, C2,. It is done by engaging or disengaging C3, Bl, B2.
- the switching control means 36 gives a control command to the hydraulic control device 13 according to the operation mode and the selection result of the shift position performed by the mode shift position selection device 37 according to the control map shown in FIG. Output
- the control unit ECU also controls the rotational speed and rotational torque of the motor generator MG, and controls the rotational speed and rotational torque of the engine E, and the like.
- the operating state of the hybrid drive device H in each operation mode will be described in detail.
- the electric torque converter mode is a mode that can start the vehicle while amplifying and outputting the rotational torque of the input shaft I (engine E) using the rotational torque of the motor 'generator MG.
- this electric torque converter mode as shown in FIG. 4, the second clutch C2 and the first brake B1 are engaged. Thereby, the ring gear rl of the first planetary gear unit P1 is fixed to the case Ds, and the ring gear of the second planetary gear unit P2 is connected to rotate integrally with the input shaft I.
- the rotational speed of the ring gear rl which is intermediate in the order of the rotational speed, becomes zero. Therefore, the sun gear si reversely rotates with respect to the rotation of the carrier cal connected so as to rotate integrally with the motor 'generator MG.
- the motor 'generator MG rotates in the positive direction (rotational speed is positive) in the same manner as the input shaft 1 (engine E), the sun gear si rotates in the negative direction (rotational speed is negative).
- the absolute value of the speed is set to be reduced relative to the absolute value of the rotational speed of the carrier cal. That is, In the present embodiment, since the first planetary gear unit PI is a double be-on type, the relationship of the gear ratio ⁇ 1 is as shown in the lower part of FIG.
- the gear ratio ⁇ 1 larger than 0.5.
- this gear length it is more preferable to set this gear length to 1 ⁇ , and to set ⁇ ⁇ . 55 to 0.65 or so.
- the sun gear si of the first planetary gear unit P1 and the sun gear s2 of the second planetary gear unit P2 are connected to rotate integrally with each other. Therefore, the first planetary gear unit P1 decelerates the absolute value of the rotational speed of the motor generator MG and transmits it to the sun gear s2 of the second planetary gear unit P2.
- the rotational torque of the motor / generator MG amplified according to the gear ratio by the first planetary gear unit P1 is transmitted to the sun gear s2 of the second planetary gear unit P2.
- the rotational torque of the carrier cal (motor 'generator MG): the rotational torque of the ring gear rl: the rotational torque of the sun gear si ⁇ 1- ⁇ 1): 1: ⁇ 1
- the gear ratio ⁇ 1 of the first planetary gear unit P1 is approximately 0.6
- the rotational torque of approximately 1.5 times the rotational torque of the motor 'generator MG is the second planetary gear via the sun gear s1. It is transmitted to the sun gear s2 of the device ⁇ 2.
- the carrier ca2 which is intermediate in the order of rotational speed, rotates integrally with the output shaft O, and the ring gear r2 becomes one side in the order of rotational speed. Rotates integrally with the input shaft I. Then, the rotation of the motor 'generator MG decelerated by the first planetary gear device P1 as described above is transmitted to the sun gear s2, which is the other side in the order of rotational speed. Therefore, the second planetary gear device P2 synthesizes the rotation of the motor 'generator MG after deceleration and the rotation of the input shaft 1 (engine E) and transmits it to the output shaft O.
- the torque of the motor / generator MG transmitted to the sun gear s2 via the first planetary gear unit P1 and the rotation of the input shaft 1 (engine E) transmitted to the ring gear r2 These rotational torques are synthesized and transmitted to the output shaft O by being a reaction force of torque.
- the sun gear s2 that rotates integrally with the sun gear si of the first planetary gear unit P1 has a negative rotation
- the ring gear r2 that rotates with the engine E and the input shaft I has a positive rotation.
- the absolute value of the rotational speed of the carrier ca2 in the middle of is decelerated relative to the absolute value of the rotational speed of the ring gear r2.
- the second planetary gear Position P 2 decelerates the absolute value of the rotational speed of input shaft I and transmits it to output shaft O. Thereby, the rotational torque of the input shaft I is amplified and transmitted to the output shaft O.
- the second planetary gear unit P2 is a single gear type, as shown in the lower part of FIG.
- the gear ratio ⁇ 2 can be appropriately set in consideration of the characteristics of the engine and the motor 'generator MG, the vehicle weight, and the like.
- the hybrid drive device ⁇ functions as an electric torque converter by operating as follows. That is, when the vehicle is started, the motor gear generator MG rotating forward is caused to generate electric power to gradually increase the rotation torque in the negative direction, whereby the sun gear s2 of the second planetary gear unit 2 rotating negatively is generated. The rotational torque in the positive direction is gradually increased to increase the reaction force, and the rotational speed of this sun gear s2 is increased (the absolute value of the rotational speed in the negative direction is decreased). From this, it is possible to gradually increase the rotational speed of the carrier ca2 of the second planetary gear set P2 connected to the output shaft O to smoothly start the vehicle. At this time, an output torque of approximately (1 + ⁇ 2) times the engine torque can be transmitted to the output shaft O.
- the rotational torque of the motor 'gear generator MG amplified by the first planetary gear device P1 is a reaction force, so the output torque is relatively small, and the motor / gear generator MG is used. However, sufficient reaction torque can be obtained. Note that the upward or downward arrows shown beside each rotary element in FIG. 7 indicate the direction of the rotational torque of each rotary element at the time of such start.
- the input side of the first clutch C1 is If the rotational speeds of the rotating member and the output side rotating member are the same, Synchronous switching to engage the latch CI is configured to be possible.
- the ring gear r2 of the second planetary gear device P2 which rotates integrally with the input shaft 1 (engine E) with the second clutch C2 engaged, and a motor
- the carrier cal of the first planetary gear device P1 that rotates integrally with the generator MG corresponds to the input-side rotating member and the output-side rotating member of the first clutch C1.
- the rotational torque in the negative direction of the motor 'generator MG is further increased gradually from the state shown in FIG. 7 to decrease the rotational speed, whereby the first forward speed in the speed diagram of FIG. As indicated by a straight line representing the state of the stages, it is possible to make the rotational speed of the motor 'generator MG coincident with the rotational speed of the input shaft I.
- the rotational speed of the ring gear r2 of the second planetary gear unit P2 and the rotational speed of the carrier cal of the first planetary gear unit P1 serving as the input side rotational member and the output side rotational member of the first clutch C1 Therefore, the first clutch C1 can be engaged without generating an impact or the like.
- the parallel mode is a mode capable of traveling by transmitting both of the rotational torque of the input shaft 1 (engine E) and the rotational torque of the motor's generator MG to the output shaft O.
- the parallel mode in addition to a plurality of gear stages configured in a state in which input shaft I and motor generator MG are directly connected, the absolute value of the rotational speed of input shaft I Is transmitted to the output shaft O, and an accelerated gear is provided to decelerate the absolute value of the rotational speed of the motor 'generator MG and transmit it to the output shaft O! /.
- this hybrid drive unit H has an input shaft I and a motor
- the third forward gear as a direct coupling stage that transmits the rotational speed to the output shaft O at the same speed, and the absolute value of the rotational speed of the input shaft I are transmitted to the output shaft O at an accelerated speed.
- It has the fourth forward speed as a step-up gear to reduce the absolute value of the rotational speed and transmit it to the output shaft O.
- the first forward speed can be switched between the electric torque converter mode and the second forward speed and the third forward speed in the parallel mode. That is, the first forward speed is realized by engaging the first clutch C1 from the electric torque converter mode. As described above, this switching from the electric torque comparator mode to the first forward gear can be performed by synchronous switching.
- the first forward speed is realized by disengaging the second forward speed second brake B2 and engaging the first brake B1.
- the first forward speed is realized by disengaging the third clutch C3 from the third forward speed and engaging the first brake B1.
- the nominal mode can be switched to and from the electric drive mode. Then, by releasing the engagement of the first forward gear force second clutch C2 in the parallel mode, the first forward gear in the electric travel mode is realized.
- the ring gear r2 of the second planetary gear unit P2 is engaged by engaging the first clutch C1 and the second clutch C2.
- the input shaft I (engine E) and the motor 'generator MG are directly connected to each other, and they rotate together.
- the absolute value of the rotational speed of the ring gear r2 of the second planetary gear set P2 is reduced and transmitted to the carrier ca2 of the second planetary gear set P2, Output from output axis O.
- the speed change ratio of the first forward speed is set to be largest.
- the first clutch Cl, the second clutch C2, and the second brake B2 are engaged.
- this second forward gear is in parallel mode.
- the first forward gear, the third forward gear, and the fourth forward gear can be switched. That is, the second forward speed is realized by disengaging the first brake B1 and engaging the second brake B2. Further, the second forward speed is realized by disengaging the third clutch C3 from the third forward speed and engaging the second brake B2. Further, the second forward speed is realized by disengaging the third clutch C3 in the fourth forward speed gear and engaging the second clutch C2. In addition, it is possible to switch between the electrical mode and the electric mode.
- the second forward gear in parallel mode is also disengaged from the second clutch C2, whereby the second forward gear in the electric travel mode is realized.
- the first clutch C1 and the second clutch C2 are engaged as in the first forward speed, so that The input shaft 1 (engine E) and the motor 'generator MG are directly coupled to the ring gear r2 of the two-planet gear unit P2, and they are in a state of being integrally rotated.
- the second brake B2 is engaged, the absolute value of the rotational speed of the ring gear r2 of the second planetary gear device P2 is reduced and transmitted to the carrier ca2 of the second planetary gear device P2, Output from output axis O.
- the gear ratio of the second forward gear is set to be smaller than the gear ratio of the first forward gear.
- the third forward gear can be switched among the first forward gear, the second forward gear and the fourth forward gear in the parallel mode. That is, the third forward speed is realized by disengaging the first brake B1 and engaging the third clutch C3. Further, the third forward speed is realized by disengaging the second brake second power B2 and engaging the third clutch C3. Further, the third forward speed is realized by disengaging the second brake B2 and engaging the second clutch C2. Note that although the Nolare mode can be switched between the electric travel mode, in this example, it is not possible to switch to the electric travel mode directly from the third forward gear in this parallel mode.
- the drive device H is configured such that the gear ratio of the transmission ratio force can not be realized when the input shaft 1 (engine E) is separated. Therefore, when switching from the third forward gear in the parallel mode to the electric travel mode, the second forward gear in the parallel mode or the fourth forward gear is selected. After switching, control is performed to switch to the electric travel mode. This control process will be described in detail using a flowchart in "16. Special Control Process" later.
- the first clutch C1 and the second clutch C2 are engaged as in the first forward speed, so that The input shaft 1 (engine E) and the motor 'generator MG are directly coupled to the ring gear r2 of the two-planet gear unit P2, and they are in a state of being integrally rotated. Furthermore, when the third clutch C3 is engaged, the first planetary gear unit P1 and the second planetary gear unit P2 are directly connected so that the whole is integrally rotated, and the input shaft I and the motor 'generator MG The rotational speed is transmitted to the output shaft O with the same speed and output. Therefore, the gear ratio of this third forward gear is 1.
- the fourth forward gear can be switched between the second forward gear in the nolarel mode and the third forward gear. That is, the fourth forward speed is realized by disengaging the second clutch C2 and engaging the third clutch C3. Further, the fourth forward speed is realized by disengaging the third forward power second clutch C2 and engaging the second brake B2.
- the Nolarel mode can be switched to and from the electric travel mode. Then, by releasing the engagement of the fourth forward gear third clutch C3 in the parallel mode, the second forward gear in the electric travel mode is realized.
- the first clutch C1 is engaged, whereby the motor 'generator MG is engaged with the ring gear r2 of the second planetary gear device P2. It is connected directly and will be in a state of rotating together.
- the third clutch C3 and the second brake B2 are engaged, the absolute value of the rotational speed of the input shaft 1 (engine E) is accelerated via the sun gear si of the first planetary gear unit P1. Then, it is transmitted to the carrier cal of the first planetary gear unit P1, and is transmitted to the ring gear r2 of the second planetary gear unit P2 via the first clutch C1 with the rotation of the motor 'generator MG.
- the absolute value of the rotational speed of the ring gear r2 of the second planetary gear set P2 is decelerated, transmitted to the carrier ca2 of the second planetary gear set P2, and the output shaft O force is output.
- the first planetary gear set P1 and the second planetary gear set P1 are arranged such that the absolute value of the rotational speed of the input shaft I is increased and transmitted to the carrier ca2 of the second planetary gear set P2.
- the gear ratio of gear unit P2 is set. Therefore, the gear ratio of this fourth forward gear is less than one.
- the input shaft 1 (engine E) is also separated from the output shaft O, and the rotation of the motor generator MG can be transmitted to the output shaft O for traveling.
- the hybrid drive device H decelerates the absolute value of the rotational speed of the motor 'generator MG and transmits it to the output shaft O in the plurality of shift speeds.
- the input shaft I is disengaged from the ring gear r2 of the second planetary gear device P2 by disengaging the second clutch C2.
- it is the same as the first forward gear and the second forward gear in the parallel mode.
- the first forward speed in the electric travel mode is realized by disengaging the second clutch C2 also in the first forward speed in the parallel mode.
- the second forward gear is disengaged from the second forward gear second clutch C2 in the nolarel mode, or disengaged from the fourth forward gear fourth clutch C3 in the parallel mode. It is realized by Further, by engaging one of the first brake B1 and the second brake B2, it is possible to switch between the first forward gear and the second forward gear in the electric travel mode.
- FIG. 9 is a flowchart showing this control process.
- this control process generally, when switching to the forward third gear in parallel mode, the electric travel mode is maintained in the parallel mode according to the predetermined conditions, and in this case, another gear, here, second gear or fourth gear. It is a control process to switch to the electric travel mode after switching to the stage. This control processing is performed by making a determination based on information from each part of the control device ECU power and outputting a command signal to each part of the hybrid drive device H such as the hydraulic control device 13 and the like. The details will be described below.
- the control unit ECU is configured such that the current state of the hybrid drive unit H is in the parallel mode. It is judged whether it is the forward third gear (step # 01). If the current state is the third forward gear in the Nolarel mode, (Step # 01: No), the process ends because there is no need to perform this control process. Then, if the current state is the third forward gear in the parallel mode (step # 01: Yes), then the control unit ECU determines whether the engine stop condition is satisfied by the engine stop condition judging means 41 or not. Decide (step # 02). When the engine stop condition is satisfied (step # 02: Yes), the control unit ECU then determines whether or not the vehicle speed detected by the vehicle speed detection unit 35 is equal to or greater than a predetermined value. (Step # 03).
- the predetermined value serving as the determination reference may be, for example, a vehicle speed intermediate between the vehicle speed normally handled by the second forward gear in parallel mode and the vehicle speed normally handled by the fourth forward gear.
- step # 03: Yes the control unit ECU operates the hydraulic control unit 13 by the switching control means 36 to set the hybrid drive unit H in the non-releasing mode. Forward Shift up to 4th gear (Step # 04). After that, the control unit ECU operates the hydraulic control unit 13 by the switching control means 36 to release the engagement of the third clutch C3 (step # 05). Thus, the hybrid drive device H is switched to the second forward gear in the electric travel mode.
- step # 03: No when the vehicle speed is less than the predetermined value, the control device ECU operates the hydraulic control device 13 by the switching control means 36 to move the obstacle drive device H forward in parallel mode 2 Shift down to fast gear (step # 06).
- control unit ECU operates the hydraulic control unit 13 by the switching control means 36 to release the engagement of the second clutch C2 (step # 07).
- the hybrid drive unit H is switched to the second forward gear in the electric travel mode.
- control unit ECU causes the engine control means 31 to stop the engine E (step # 08). The process ends here.
- step # 09 the control unit ECU determines whether the required driving force is less than zero, that is, whether there is a deceleration request (step # 09).
- the determination as to whether or not the required driving force is less than zero may be made by the required driving force detection means 40, for example, in a state where the accelerator pedal of the vehicle is not operated and / or a state in which the brake pedal is operated. It can be done based on follows If the required driving force is equal to or greater than zero (step # 09: No), no deceleration is necessary, and it is sufficient to drive at the forward third gear in the parallel mode, so the process ends. Do.
- step # 09: Yes the controller ECU determines that the charge amount of the battery 11 is equal to or more than the predetermined value by the battery condition detection means 33. Determine if it is a force (step # 10).
- the battery charge amount serving as the determination reference is set to, for example, the charge amount when the battery 11 hardly needs to be charged, that is, set near the upper limit value of the charge amount in the usage range of the battery 11. It is suitable.
- the control unit ECU stops the engine E by the engine control means 31 while maintaining the third forward gear in parallel mode. Stop (Step # 08).
- step # 10 the process proceeds to step # 03, and upshift or downshift is performed according to the vehicle speed.
- step # 08 The output shaft O power is also disconnected, and the engine E is stopped (step # 08).
- the hybrid drive unit H according to the present embodiment has a configuration similar to that of the hybrid drive unit H according to the first embodiment, but has a configuration in which the parallel mode and the electric travel mode are further multi-tiered. It has 7 gear stages including reverse gear in mode and 3 gear stages in electric drive mode.
- the hybrid drive device H according to the present embodiment will be described focusing on differences from the first embodiment.
- the hybrid according to the present embodiment The system configuration of the driving device H is the same as that shown in FIG. 2, so that the explanation thereof is omitted. Further, the other configurations are the same as those of the first embodiment in the points which are not particularly described.
- FIG. 10 is a skeleton diagram showing a configuration of a hybrid drive device H according to the present embodiment.
- this hybrid drive device H also has an input shaft I connected to the engine E and an output shaft O connected to the wheels W (see FIG. 2), as in the first embodiment.
- these structures are stored in case Ds as a non-rotating member fixed to a vehicle body.
- the drive device H according to this embodiment is the same as the first embodiment in the configuration of the first planetary gear unit P1, the second planetary gear unit P2 has four rotating elements. It has a configuration, which is different from the first embodiment. In addition, the number of frictional engagement elements is also larger than that in the first embodiment.
- the second planetary gear set P2 is formed of a Ravley type planetary gear set disposed coaxially with the input shaft I.
- the second planetary gear unit P2 is a long pinion gear that engages with both the first sun gear s2 and the second sun gear s3, the ring gear r2, and both the first sun gear s2 and the ring gear r2.
- It has a common carrier ca2 that supports a short gear and a short gear engaged with the second sun gear s3 as a rotation element.
- the ring gear r2 is connected to rotate integrally with the output shaft O.
- the first sun gear s2 is connected to rotate integrally with the sun gear si of the first planetary gear device P1.
- sun gears si and s2 are selectively fixed to the case Ds via the second brake B2.
- the second sun gear s3 is selectively connected to the carrier cal of the first planetary gear device P1 via the first clutch C1, and selectively connected to the input shaft I via the second clutch C2. . That is, in the second sun gear s3, the rotation of the input shaft I is selectively transmitted by the second clutch C2, and the rotation of the motor generator MG is selectively transmitted by the first clutch C1.
- the carrier ca2 is selectively fixed to the case Ds via the third brake B3 and selectively to the input shaft I via the fourth clutch C4.
- the second sun gear s3, the ring gear r2, and the first sun gear s2 are respectively the “first rotating element (1)” and the “second rotating element (2)” of the second planetary gear device P2 in the present invention. And the third rotating element (3). Further, the carrier ca2 corresponds to the "intermediate rotating element (m)" of the second planetary gear device P2 in the present invention.
- the fourth clutch C 4 and the third brake B 3 are, like the friction engagement elements according to the first embodiment, a multi-plate type operated by the hydraulic pressure supplied via the hydraulic control device 13.
- a clutch or multi-disc brake can be used.
- FIG. 11 is an operation table showing the operating states of the respective friction engagement elements Cl, C2, C3, C4, Bl, B2, B3 in one or more gear stages provided with a plurality of operation modes and each operation mode.
- FIGS. 12 and 13 correspond to FIGS. 7 and 8 regarding the first embodiment, respectively. That is, these figures show velocity diagrams of the first planetary gear unit P1 and the second planetary gear unit P2, FIG. 12 is a velocity diagram in the electric torque converter mode, and FIG. 13 is a parallel mode. Shows a velocity diagram for Note that “1st”, “2nd”, and “3rd” in FIG.
- each of the plurality of vertical lines arranged in parallel corresponds to the respective rotating elements of the first planetary gear set P1 and the second planetary gear set P2. doing. That is, “cal”, “rl” and “sl” described on the upper side of each vertical line correspond to the carrier cal, ring gear rl and sun gear si of the first planetary gear unit P1, respectively, “s3” and “r2”.
- the “ca2” and “s2” correspond to the second sun gear s3, the ring gear r2, the carrier ca2 and the first sun gear s2 of the second planetary gear unit P2, respectively.
- a straight line L1 indicates the operating state of the first planetary gear device P1
- a straight line L2 indicates the operating state of the second planetary gear device P2.
- each straight line indicates the operating state of the first planetary gear device P1 and the second planetary gear device P2 at each shift speed.
- “1st,” “2nd,” and “3rd” indicate the first forward gear, the second forward gear, and the third forward gear in the parallel mode and the electric travel mode, respectively. Each is shown. Also, “4th,”"5th,” “6th,” and “REV” are the fourth forward gear in parallel mode, the fifth forward gear, and the front. The sixth gear and the reverse gear are shown respectively.
- the hybrid drive device H includes an "electric torque converter mode", a "parallel mode”, and an "electric travel” using one motor generator / generator MG. It is the same as the first embodiment in that the three operation modes of “mode” are configured to be switchable. On the other hand, the hybrid drive system H has more gear stages than the first embodiment, and specifically, in the parallel mode, has seven gear stages including reverse gear, The electric travel mode has three gear stages.
- the operating state of the hybrid drive device H in each operating mode will be described in detail.
- the second clutch C2 and the first brake B1 are engaged.
- the ring gear rl of the first planetary gear device P1 is fixed to the case Ds, and the second sun gear s3 of the second planetary gear device P2 is connected to rotate integrally with the input shaft I.
- ring gear r 2 which is the second in order of rotational speed, rotates integrally with output shaft O, and the first in rotational speed order.
- the second sun gear s3 that rotates with the input shaft I rotates integrally.
- the rotation of the motor 'generator MG decelerated by the first planetary gear device P1 is transmitted to the fourth first sun gear s2 in the order of rotational speed.
- the third carrier ca2 in the order of rotational speed is in a freely rotatable state.
- “order of rotational speed” is basically the order from high speed side to low speed side, and in reverse mode in parallel mode, the order is from low speed side to high speed side.
- the second planetary gear unit P2 The rotation of generator generator MG and the rotation of input shaft 1 (engine E) are synthesized and transmitted to output shaft O. That is, in the second planetary gear device P2, the rotational torque force of the motor 'generator MG transmitted to the first sun gear s2 via the first planetary gear device P1 is transmitted to the second sun gear s3. These rotational torques are synthesized and transmitted to the output shaft O by being a reaction force of the rotational torque of.
- the second sun gear unit P2 decelerates the absolute value of the rotational speed of the input shaft I and transmits it to the output shaft O. Thereby, the rotational torque of the input shaft I is amplified and transmitted to the output shaft O.
- the hybrid drive device H functions as an electric torque converter by operating in the same manner as in the first embodiment.
- the hybrid drive device H operates in the same manner as in the first embodiment to allow the input side of the first clutch C1 to switch the mode from the electric torque converter mode to the first forward gear in the parallel mode. Synchronous switching is possible, in which the first clutch C1 is engaged in the state where the rotational speeds of the rotary member and the output side rotary member are the same.
- hybrid drive device H in the parallel mode, is configured as the first gear, the second gear, and the second gear as the reduction gear that is configured by connecting input shaft I and motor 'generator MG directly.
- the third gear stage is also configured by connecting the input shaft I and the motor generator / generator MG directly, and the fourth forward gear as a direct coupling stage that transmits the rotational speed of the input shaft I to the output shaft O at the same speed. It accelerates the absolute value of the rotational speed of the input shaft I and transmits it to the output shaft O, and decelerates the absolute value of the rotational speed of the motor generator MG and transmits it to the output shaft O It has five forward speeds, and six forward speeds, and a reverse speed.
- the operating state of the hybrid drive system H in each gear will be described.
- the first clutch Cl, the second clutch C2, and the first brake B1 are engaged in the first forward speed.
- the second planetary gear is engaged by engaging the first clutch C1 and the second clutch C2.
- the input shaft I (engine E) and the motor 'generator MG are directly coupled to the second sun gear s3 of the vehicle device P2, and they are in an integrally rotated state.
- the absolute value of the rotational speed of the second sun gear s3 of the second planetary gear set P2 is reduced and transmitted to the ring gear r2 of the second planetary gear set P2, Output from output axis O.
- the gear ratio of the first forward gear is set to be the largest among the plurality of gear stages in the non-zero mode.
- the gear ratio of this fourth forward gear is 1.
- the hybrid drive system H according to the present embodiment also has a configuration that can not realize the shift ratio of the transmission ratio force with the input shaft 1 (engine E) separated as in the first embodiment.
- the fourth forward gear in parallel mode can not be directly switched to electric travel mode. Therefore, as in the control process described in “1-6. Special control process” according to the first embodiment, when switching from the fourth forward speed in the parallel mode to the electric travel mode, the forward mode in the parallel mode After switching to 3rd gear or 5 forward gears, control to switch to electric travel mode is performed.
- the motor 'generator MG is engaged with the second sun gear s3 of the second planetary gear device P2 by engaging the first clutch C1. It will be in a state where it is directly connected and rotates integrally.
- the third clutch C3 and the second brake B2 are engaged, the absolute value of the rotational speed of the input shaft I (engine E) is increased and transmitted to the carrier cal of the first planetary gear device P1. The torque is transmitted to the second sun gear s3 of the second planetary gear unit P2 via the first clutch C1 with the rotation of the motor generator MG.
- the absolute value of the rotational speed of the second sun gear s3 of the second planetary gear set P2 is decelerated and transmitted to the ring gear r2 of the second planetary gear set P2, and the output shaft O force is output.
- the gear ratio of the first planetary gear unit P1 and the second planetary gear unit P2 is set so that the absolute value of the rotational speed of the input shaft I is accelerated and transmitted to the ring gear r2 of the second planetary gear unit P2. Is set. Therefore, the gear ratio of the fifth forward gear is less than one.
- the first clutch Cl As shown in FIG. 11, in the sixth forward speed, the first clutch Cl, the third clutch C3, and the third brake B3 are engaged. Then, as shown in FIGS. 10 and 13, in the sixth forward speed, the first clutch C1 is engaged, whereby the motor 'generator MG is engaged with the second sun gear s3 of the second planetary gear device P2. It will be in a state where it is directly connected and rotates integrally.
- the gear ratio of the first planetary gear unit P1 and the second planetary gear unit P2 is set so that the absolute value of the rotational speed of the input shaft I is increased and transmitted to the ring gear r2 of the second planetary gear unit P2. Is set. Also, the gear ratio of the sixth forward gear is set to be smaller than the gear ratio of the fifth forward gear !.
- the drive device H decelerates the absolute value of the rotational speed of the motor's generator MG and transmits it to the output shaft O as the first forward gear as the reduction gear. , 2nd gear forward, and 3rd gear forward.
- the input shaft I is moved to the second planetary gear unit by disengaging the second clutch C2. It is the same as the first forward gear, the second forward gear and the third forward gear in the parallel mode except that the second sun gear s3 force of P2 is separated.
- FIGS. 14 to 16 show an example in which the first planetary gear set P1 has three rotating elements, and the second planetary gear set P2 has four rotating elements, as shown in FIG.
- FIG. 19 shows an example in which the first planetary gear device P1 has four rotating elements and the second planetary gear device P2 has three rotating elements.
- the following points are common. That is, in the first planetary gear unit P1, the motor 'generator MG is connected to the first rotating element (1), the second rotating element (2) is fixed to the case Ds by the brake, and in that state the third rotating element
- the gear ratio is set such that the absolute value of the rotational speed of 3) is decelerated with respect to the absolute value of the rotational speed of the first rotating element (1).
- the input shaft I is connected to the first rotating element (1)
- the output shaft O is connected to the second rotating element (2)
- the first rotating element (3) is connected to the first
- the third rotating element (3) of the planetary gear set P1 is connected!
- the arrangement of the vertical lines corresponding to the respective rotating elements in these velocity diagrams is determined by the setting of the gear ratios of the first planetary gear unit P1 and the second planetary gear unit P2.
- various configurations capable of realizing the number of rotating elements required in each example can be applied. .
- the arrangement of the vertical lines corresponding to each rotating element is the first planetary gear unit P1 and the second planetary gear unit P1 from the high speed side of the rotational speed to the low speed side (right side to left side in the drawing).
- a longitudinal line corresponding to the first rotating element (1) of the planetary gear set P2, a vertical line corresponding to the second rotating element (2) of the second planetary gear set P2, an intermediate rotating element of the second planetary gear set P2 a vertical line corresponding to m), a vertical line corresponding to the second rotating element (2) of the first planetary gear unit P1, a third rotating element (3) of the first planetary gear unit P1 and the second planetary gear unit P2 The order of the vertical lines corresponding to
- the arrangement of vertical lines corresponding to each rotation element is from the high speed side to the low speed side (right side to left side in the figure) of the rotational speed.
- the order of the vertical lines corresponds to the third rotation element (3) of. Therefore, in the example shown in FIG.
- the “al”, “bl”, and “cl”, which are described above the vertical lines of the velocity diagram shown in FIG. 15 and are arranged in the order of the rotational speed, are respectively the first planetary gear unit PI
- “A2”, “B2”, “C2” and “D2” arranged at the lower part of these in the order of rotational speed are respectively the first rotation element (1) and the second rotation of the second planetary gear device P2. It corresponds to the element (2), the intermediate rotating element (m), and the third rotating element (3).
- the arrangement of the vertical lines corresponding to each of the rotating elements is the first planetary gear unit P1 and the second planetary gear unit P1 from the high speed side to the low speed side (right side to left side in the drawing) of the rotational speed.
- the vertical lines correspond to the first planetary gear unit PI and the third rotating element (3) of the second planetary gear unit P2. That is, in the example shown in FIG. 15, the position of the vertical line corresponding to the second rotating element (2) of the first planetary gear device P1 and the position of the vertical line corresponding to the intermediate rotating element (m) of the second planetary gear device P2. It differs from the example shown in Figure 12 in that
- the arrangement of the vertical lines corresponding to each of the rotary elements is the first planetary gear unit P1 and the first planetary gear unit P1 in the direction from the high speed side of the rotational speed to the low speed side (right A vertical line corresponding to the first rotating element (1) of the two-planet gear system P2, a vertical line corresponding to the second rotating element (2) of the second planetary gear system P2, a second rotation point of the first planetary gear system P1 A vertical line corresponding to the element (2), a vertical line corresponding to the third rotation element (3) of the first planetary gear unit P1 and the second planetary gear unit P2, a fourth rotating element of the second planetary gear unit P2 It corresponds to the order of vertical lines corresponding to 4). That is, in the example shown in FIG. 16, the second planetary gear unit P2 is replaced by the intermediate rotating element (m), and the fourth rotating element (4) following the third rotating element (3) in the order of rotational speed It differs from the example shown in Fig. 12 in that it has the
- the first planetary gear device P1 has an intermediate rotating element (m), which corresponds to the vertical line and the second corresponding to the second rotating element (2) of the first planetary gear device P1. It differs from the example shown in FIG. 12 in that it is disposed between the vertical line corresponding to the first rotation device P1 and the third rotation element (3) of the second rotation device P2.
- the first planetary gear device P1 has an intermediate rotating element (m), which is the first rotating element of the first planetary gear device P1 and the second planetary gear device P2.
- This example differs from the example shown in FIG. 12 in that it is disposed between the vertical line corresponding to (1) and the vertical line corresponding to the second rotation element (2) of the second planetary gear device P2.
- the hybrid drive device H is a carrier cal, which is the "second rotating element (2)" of the first planetary gear device P1, and a “third rotating element (3)” of the second planetary gear device P2.
- Carrier ca2 is connected to be integrally rotated, and ring gear rl, which is the "third rotating element (3)” of first planetary gear unit P1, is selectively fixed to case Ds by first brake B1. ing.
- the configuration of the first embodiment that is, the “third rotating element (3) (sun gear si)” of the first planetary gear device P1 and the “third rotating element (second gear) of the second planetary gear device P2.
- the first planetary gear device P1 is configured by a single gear type planetary gear mechanism
- the second planetary gear device P2 is a double gear type planetary gear.
- the first embodiment is also different from the first embodiment in that it is configured by a mechanism. With such a configuration change, the motor 'generator MG can be disposed on the engine E side, and the first planetary gear device P1 and the second planetary gear device P2 can be disposed adjacent to each other. Is also different from the first embodiment.
- the hybrid drive device H according to the present embodiment will be described focusing on differences from the first embodiment.
- the system configuration of the hybrid drive device H according to the present embodiment is the same as that shown in FIG. 2, and thus the explanation thereof is omitted.
- the other configurations are the same as those of the first embodiment in the points that are not particularly described. 3- 1.
- FIG. 20 is a skeleton diagram showing a configuration of a hybrid drive device H according to the present embodiment.
- this hybrid drive device H also has an input shaft I connected to the engine E and an output shaft O connected to the wheels W (see FIG. 2), as in the first embodiment.
- these structures are stored in case Ds as a non-rotating member fixed to a vehicle body.
- the configurations of the first planetary gear device P1 and the second planetary gear device P2 are different from those of the first embodiment.
- the first planetary gear unit P1 is constituted by a single gear type planetary gear mechanism coaxially arranged with the input shaft I. That is, the first planetary gear unit P1 has, as rotating elements, a carrier cal for supporting a plurality of pinion gears, and a sun gear s1 and a ring gear rl which respectively mesh with the pinion gears.
- the sun gear si is connected to rotate integrally with the motor generator MG.
- the carrier cal is connected to rotate integrally with the carrier ca2 of the second planetary gear device P2.
- the carriers cal and ca2 are selectively fixed to the case Ds via the second brake B2, and selectively connected to the input shaft I via the third clutch C3.
- the ring gear rl is selectively fixed to the case Ds via the first brake B1.
- the sun gear si, the carrier cal, and the ring gear rl are respectively the “first rotating element (1)” and the “second rotating element (2)” of the first planetary gear device P1 in the present invention.
- the third rotation element (3) is the “third rotation element (3)”.
- the second planetary gear device P2 is configured of a double-on-type planetary gear mechanism coaxially arranged with the input shaft I. That is, the second planetary gear unit P2 has, as rotating elements, a carrier ca2 for supporting a plurality of sets of pinion gears, and a sun gear s2 and a ring gear r2 that respectively mesh with the pinion gears.
- the sun gear s2 is selectively connected to the sun gear si of the first planetary gear unit P1 via the first clutch C1, and is selectively connected to the input shaft I via the second clutch C2. That is, in this sun gear s2, the rotation of the input shaft I is selectively transmitted by the second clutch C2, and the motor 'J. The rotation of the motor MG is selectively transmitted.
- the ring gear r2 is connected to rotate integrally with the output shaft O.
- the carrier ca2 is connected to rotate integrally with the carrier ca1 of the first planetary gear device P1.
- these carriers cal and ca2 are selectively fixed to the case Ds via the second brake B2, and selectively connected to the input shaft I via the third clutch C3.
- the sun gear s2, the ring gear r2, and the carrier ca2 are respectively the "first rotating element (1)" and the "second rotating element (2)" of the second planetary gear device P2 in the present invention.
- the third rotation element (3) are respectively the "first rotating element (1)" and the "second rotating element (2)" of the second planetary gear device P2 in the present invention.
- FIG. 21 is a schematic diagram showing the connection state of each component of the hybrid drive device H in a more simplified manner.
- the respective rotating elements of the first planetary gear unit P1 and the second planetary gear unit P2 are arranged laterally in the order of rotational speed and connected by broken lines, and are connected to these respective rotating elements. Components are connected by solid lines.
- the first planetary gear unit P1 has a sun gear si, a carrier cal and a ring gear rl in the order of rotational speed.
- the second planetary gear device P2 has a sun gear s2, a ring gear r2 and a carrier ca2 in the order of rotational speed.
- the carrier ca1 of the first planetary gear device P1 and the carrier ca2 of the second planetary gear device P2 are connected so as to rotate integrally.
- the sun gear si of the first planetary gear unit P1 is connected to rotate integrally with the motor 'generator MG, and is connected to the sun gear s2 of the second planetary gear unit P2 via the first clutch C1. It is possible to connect selectively.
- the carrier cal of the first planetary gear device P1 and the carrier ca2 of the second planetary gear device P2 are selectively connectable to the input shaft I via the third clutch C3. And can be selectively fixed to the case Ds via the second brake B2.
- the ring gear r1 of the first planetary gear unit P1 can be selectively fixed to the case Ds via the first brake B1.
- the sun gear s2 of the second planetary gear device P2 is selectively connectable to the sun gear si of the first planetary gear device P1 via the first clutch C1, and an input shaft via the second clutch C2. It is possible to selectively connect to I.
- the ring gear r2 of the second planetary gear unit P2 is connected to rotate integrally with the output shaft O !.
- this hybrid drive unit H arranges the motor 'generator MG closer to the engine E side than the first planetary gear unit P1, as shown in FIG.
- the first planetary gear unit PI and the second planetary gear unit P2 are disposed adjacent to each other.
- the motor 'generator MG which generally has a larger diameter than the gear trains of the first planetary gear set P1 and the second planetary gear set P2, etc., is used as the torque of the conventional automatic transmission on the engine E side. It becomes possible to arrange in the position corresponding to a converter. Therefore, it becomes possible to set it as the hybrid drive unit H highly compatible with the conventional automatic transmission.
- the gear trains of the first planetary gear unit P1 and the second planetary gear unit P2 can be divided into units separated from the motor generator MG, the assemblability of the hybrid drive unit H is improved. be able to.
- FIG. 22 is an operation table showing the operating states of the respective friction engagement elements Cl, C2, C3, Bl, B2 in a plurality of operating modes and one or more gear stages provided for each operating mode.
- “o” indicates that each frictional engagement element is in the engaged state.
- “not marked” indicates that each frictional engagement element is in the disengaged state.
- FIG. 23 is a view showing the relationship between switchable operation modes and shift speeds. Note that the white arrows in this figure indicate the relationship in which synchronous switching is possible.
- FIG. 22 is an operation table showing the operating states of the respective friction engagement elements Cl, C2, C3, Bl, B2 in a plurality of operating modes and one or more gear stages provided for each operating mode.
- “o” indicates that each frictional engagement element is in the engaged state.
- “not marked” indicates that each frictional engagement element is in the disengaged state.
- FIG. 23 is a view showing the relationship between switchable operation modes and shift speeds. Note that the white arrows in this figure indicate the relationship in which
- FIG. 24 is a diagram showing an example of a control map defining the relationship between the speed (vehicle speed) of the vehicle and the required driving force, and the holding ranges of the respective shift stages in the electric torque converter mode and the parallel mode. Also in this figure, the horizontal axis is the vehicle speed, and the vertical axis is the required driving force based on the driver's accelerator operation or the like.
- FIG. 25 shows velocity diagrams of the first planetary gear unit P1 and the second planetary gear unit P2, and FIG. 25 shows the velocity in the electric torque converter mode.
- FIG. 26 shows a velocity diagram in the parallel mode
- FIG. 27 shows a velocity diagram in the engine running mode. Note that "1st” and “2nd” in Fig. 26 are the same as the speed diagram in the electric travel mode.
- the vertical axis corresponds to the rotational speed of each rotating element. That is, "0" corresponding to the vertical axis indicates that the rotational speed is zero, the upper side is positive, and the lower side is negative.
- each of a plurality of vertical lines arranged in parallel corresponds to the respective rotating elements of the first planetary gear device P1 and the second planetary gear device P2.
- Ru That is, “sl”, “cal” and “rl” described on the upper side of each vertical line correspond to the sun gear si, carrier cal and ring gear rl of the first planetary gear unit P1, respectively, “s2” and “r2”.
- the “ca2” corresponds to the sun gear s2, the ring gear r2 and the carrier ca2 of the second planetary gear unit P2, respectively.
- the distance between the vertical lines corresponding to each of the rotating elements corresponds to the gear ratio of the first planetary gear set P1 and the second planetary gear set P2.
- the straight line L1 indicates the operating state of the first planetary gear device P1
- the straight line L2 indicates the operating state of the second planetary gear device P2.
- each straight line indicates the operating state of the first planetary gear unit P1 and the second planetary gear unit P2 at each shift speed.
- ⁇ is the rotational speed of motor 'generator MG
- ⁇ is the rotational speed of input shaft 1 (engine E)
- ⁇ is the rotational speed of output shaft O
- X indicates brakes respectively.
- “1st” indicates the first forward speed of the parallel mode, the electric travel mode, and the engine travel mode.
- “2nd” indicates the second forward gear in parallel mode and electric travel mode.
- “3rd” and “4th” indicate the forward 3rd gear and parallel 4th gear in parallel mode respectively.
- the hybrid drive device H has three operation modes of “electric torque converter mode”, “parallel mode”, and “electric travel mode”, and Furthermore, it has an “engine travel mode” that can be driven only by the driving force of the engine E without using the motor 'generator MG, and a total of four operation modes can be switched. Further, the hybrid drive system H has four gear stages in the parallel mode and has two gear stages in the electric travel mode. Then, the operation mode and switching of the shift speed in each operation mode are controlled by the hydraulic control device 13 according to the control command from the switching control means 36 of the control device ECU to control the respective friction engagement elements C1, C2, C3. , Bl, B2 by engaging or disengaging.
- the switching control means 36 outputs a control command to the hydraulic control device 13 in accordance with the operation mode and the selection result of the shift speed performed by the mode 'shift speed selection means 37 in accordance with the control map shown in FIG.
- the control device ECU also controls the rotational speed and rotational torque of the motor 'generator MG, and controls the rotational speed and rotational torque of the engine E, and the like.
- the mode 'gear selection means 37 operates according to the control map shown in FIG. 24 according to the vehicle speed detection means 35 and the required driving force detection means 40 and the operation mode defined according to the required vehicle speed and the required driving force. Select a gear.
- the mode 'gear selection means 37 selects the electric torque converter mode during start acceleration of the vehicle or when the vehicle speed is very low. In the other states, the mode 'gear selection means 37 selects each gear in the parallel mode or the electric travel mode in accordance with the vehicle speed, the required driving force, and the like. The electric travel mode is selected when the engine stop condition determination means 41 determines that the engine stop condition is satisfied. Further, the engine travel mode is selected when conditions such as a small amount of battery charge are satisfied during start acceleration in the electric torque converter mode.
- the operation state of the hybrid drive device H in each operation mode will be described in detail.
- the second clutch C2 and the first brake B1 are engaged.
- the ring gear rl of the first planetary gear unit P1 is fixed to the case Ds, and the sun gear s2 of the second planetary gear unit P2 is connected to rotate integrally with the input shaft I.
- the first planetary gear unit P1 sets the rotational speed of the ring gear rl on the other side to the sun gear si on the other side in order of the rotational speed to zero. Become. Therefore, the absolute value of the rotational speed of the sun gear s 1 connected to rotate integrally with the motor 'generator MG is decelerated and transmitted to the carrier ca 1 which is intermediate in the order of the rotational speed.
- the carrier cal since the motor 'generator MG rotates in the negative direction (rotational speed is negative) as opposed to the input shaft 1 (engine E), the carrier cal also rotates in the negative direction.
- the carrier cal of the first planetary gear device P1 and the carrier ca2 of the second planetary gear device P2 are connected so as to rotate integrally. Therefore, the first planetary gear unit P1 decelerates the absolute value of the rotational speed of the motor gear MG and transmits it to the carrier ca2 of the second planetary gear unit P2. As a result, the rotational torque of the motor generator / generator MG amplified according to the gear ratio by the first planetary gear device P1 is transmitted to the carrier ca2 of the second planetary gear device P2.
- the first planetary gear unit P1 is a single gear type. Then, as shown in the lower part of FIG.
- the gear ratio ⁇ 1 can be appropriately set in consideration of the characteristics of the motor 'generator MG, the weight of the vehicle, and the like.
- the ring gear r2 which is intermediate in the order of rotational speed, rotates integrally with the output shaft, and the sun gear s 2 which is one side in the order of rotational speed. Rotates integrally with the input shaft I. Then, the rotation of the motor 'generator MG decelerated by the first planetary gear device P1 as described above is transmitted to the carrier ca2, which is the other side in the order of rotational speed. Therefore, the second planetary gear device P2 synthesizes the rotation of the motor 'generator MG after deceleration and the rotation of the input shaft 1 (engine E) and transmits it to the output shaft O.
- These rotational torques are synthesized and transmitted to the output shaft O by being a reaction force of.
- the carrier ca2 integrally rotating with the carrier cal of the first planetary gear device P1 has a negative rotation
- the sun gear s2 integrally rotating with the engine E and the input shaft I has a positive rotation.
- the absolute value of the rotational speed of the ring gear r2 in the middle is decelerated with respect to the absolute value of the rotational speed of the sun gear s2.
- the second planetary gear unit P 2 decelerates the absolute value of the rotational speed of the input shaft I and transmits it to the output shaft O. Thereby, the rotational torque of the input shaft I is amplified and transmitted to the output shaft O.
- the second planetary gear set P2 is a double be-on type, as shown in the lower part of FIG.
- gear ratio ⁇ 2 is about 0.5
- the rotational torque of input shaft 1 (engine E) is shared by the carrier ca2 (rotational torque of amplified motor 'generator MG) sharing about half of the rotational torque of the rotational gear s2 (input shaft I).
- the rotational torque about twice that of is transmitted to the output shaft O.
- the gear ratio 2 can be set appropriately in consideration of the characteristics of the engine E and the motor / generator MG, the vehicle weight, and the like.
- the hybrid drive device H functions as an electric torque converter by operating as follows. That is, at the time of start of the vehicle, the motor ca generator MG rotating in the negative direction generates electric power to gradually increase the rotational torque in the positive direction, whereby the carrier ca2 of the second planetary gear device P2 rotating in the negative direction. The rotational torque in the positive direction is gradually increased to increase the reaction force, and the rotational speed of the carrier ca2 is increased (the absolute value of the rotational speed in the negative direction is decreased). From this, the rotation speed of the ring gear r2 of the second planetary gear device P2 connected to the output shaft O can be gradually increased to smoothly start the vehicle. At this time, an output torque of approximately ( ⁇ ⁇ ⁇ ⁇ 2) times the engine torque can be transmitted to the output shaft O.
- the rotational torque of the motor 'gear generator MG amplified by the first planetary gear device P1 is a reaction force, so the output torque is relatively small, and the motor / gear generator MG is used. However, sufficient reaction torque can be obtained. Note that the upward or downward arrows shown beside each of the rotary elements in FIG. 25 indicate the direction of the rotational torque of each of the rotary elements at the time of such start.
- the input drive rotating member of the first clutch C1 Synchronous switching is possible in which the first clutch C1 is engaged while the rotational speed of the output side rotation member is the same.
- the second brake is used with the rotational speed of the rotation-side member of the second brake 2 being zero, even when the mode is switched to the first forward speed in the engine travel mode. Engage the hook 2 Synchronized switching is possible. Specifically, as shown in FIG.
- a sun gear s2 of the second planetary gear device 2 that rotates integrally with the input shaft I (the engine ⁇ ) in the engaged state of the second clutch C2;
- the first planetary gear device P1 rotates integrally with the motor generator MG, and the sun gear si of the first clutch C1 is connected to the input-side rotating member and the output-side rotating member of the first clutch C1. It corresponds to Further, carriers cal and ca2 of the first planetary gear device P1 and the second planetary gear device P2 which are integrally rotated correspond to the rotation side members of the second brake B2.
- the motor 'generator MG is further pushed back without engaging the second brake B2 to increase the rotational torque in the forward direction.
- the rotational speed of the motor generator MG and the rotational speed of the input shaft I coincide with each other as shown by the straight line representing the state of the second forward gear in the speed diagram in FIG. can do.
- the rotational speed of the sun gear s2 of the second planetary gear unit P2 and the rotational speed of the sun gear si of the first planetary gear unit P1 serving as the input side rotational member and the output side rotational member of the first clutch C1 Therefore, the first clutch C1 can be engaged without generating an impact or the like.
- synchronous switching can be performed to shift to the parallel mode in a state where the rotational torque in the positive direction is generated by the motor 'generator MG. That is, according to this configuration, the direction of the rotational torque of the motor 'generator MG does not change when the electric torque converter mode force is also switched to the parallel mode. Therefore, the gear by the change in the meshing direction of the gears of the first planetary gear unit P1 Sounds can be prevented, and silent and smooth synchronous switching can be performed.
- both the synchronous switching by engaging these second brakes B2 and the synchronous switching by engaging the first clutch C1 are the motor 'generator MG when running in the electric torque converter mode. This is realized in the process of increasing the rotational speed of the output shaft O by increasing the rotational speed of the That is, according to the present embodiment, during start-up acceleration of the vehicle, first, synchronous switching from the electric torque converter mode to the first forward speed of the engine travel mode is possible, and further mode switching is not performed here. When accelerated, synchronous switching from the electric torque converter mode to the second forward gear in parallel mode is possible. And, in any of these mode switching, smooth switching can be performed without generating an impact associated with the engagement of the engagement element.
- the engine travel mode is a mode in which travel can be performed only by the driving force of the engine E without using the motor 'generator MG.
- the gear drive H has only the first forward gear in the engine travel mode.
- the second clutch C2, the first brake B1 and the second brake B2 are engaged.
- the first forward speed of this engine travel mode can be switched between the first forward speed of electric torque converter mode and the first forward speed of parallel mode. That is, the first forward speed in the engine travel mode is realized by engaging the electric torque converter mode force second brake B2. As described above, this electric torque converter mode force can be switched to the first forward speed by synchronous switching.
- the first forward speed in the engine running mode is realized by disengaging the first forward clutch force C1 in parallel mode and engaging the first brake B1.
- the absolute value of the rotational speed of the sun gear s2 of the second planetary gear train P2 to which the input shaft I is connected is decelerated, transmitted to the ring gear r2 of the second planetary gear train P2, and output from the output shaft O.
- the respective shift stages in the parallel mode of the hybrid drive system H according to the present embodiment have substantially the same configuration as that of the first embodiment. That is, in the parallel mode, the hybrid drive system H is configured such that the input shaft I and the motor 'generator MG are directly connected to each other, as the first gear and the second gear as the reduction gear.
- the motor's motor generator MG are directly connected, and the third forward gear as the direct connection stage that transmits the rotational speed of the input shaft I to the output shaft O at the same speed, and the absolute value of the rotational speed of the input shaft I Is transmitted to the output shaft O, and there is also a fourth forward gear as an accelerated gear to reduce the absolute value of the rotational speed of the motor 'generator MG and transmit it to the output shaft O.
- the operating state of the hybrid drive system H at each gear will be described.
- the first forward speed in the parallel mode can be switched between the first forward speed in the engine travel mode and the second forward speed and the third forward speed in the parallel mode. That is, the first forward gear in the Norel mode is realized by disengaging the first brake B1 in the engine travel mode and engaging the first clutch C1. Also, the first forward gear in the Norel mode is realized by disengaging the first brake B2 and engaging the second brake B2 in the Norel mode. Further, the first forward speed in the Norel mode is realized by disengaging the third clutch C3 from the third forward speed and engaging the second brake B2.
- the parallel mode can also be switched between the electric travel mode. Then, by releasing the engagement of the first clutch forward second clutch force C2 in the nominal mode, the electric travel mode is established. First forward gear is realized.
- the first clutch C1 and the second clutch C2 are engaged, whereby the second planetary gear unit is engaged.
- the input shaft 1 (engine E) and the motor 'generator MG are directly connected to the P2 sun gear s2, and they rotate together.
- the second brake B2 is engaged, the absolute value of the rotational speed of the sun gear s2 of the second planetary gear device P2 is decelerated and transmitted to the ring gear r2 of the second planetary gear device P2 for output.
- Output from axis O The gear ratio of the first forward gear is set to be the largest among the plurality of gear stages in the Nolarel mode. Also, this transmission gear ratio is the same as the first forward gear in the engine travel mode.
- the second forward gear in the Norel mode in the second forward gear in the Norel mode, the first clutch Cl, the second clutch C2, and the first brake B1 are engaged.
- the second forward gear can be switched between the electric torque converter mode and the first forward gear, the third forward gear and the fourth forward gear in the parallel mode. That is, the second forward gear in the Nolarel mode is realized by engaging the first clutch C1 from the electric torque converter mode. Further, the second forward gear in the Nolarel mode is realized by disengaging the second brake B2 from the first gear in the Nolarel mode and engaging the first brake B1. Further, the second forward gear in the norel mode is realized by disengaging the third clutch C3 and engaging the first brake B1.
- the second forward speed in the norel mode is realized by disengaging the third clutch C3 in the fourth forward speed gear and engaging the second clutch C2.
- the second forward gear in parallel mode is also disengaged from the second clutch C2, whereby the second forward gear in the electric travel mode is realized.
- the first clutch C1 and the second clutch C2 are engaged as in the first forward speed.
- the input shaft 1 (engine E) and the motor 'generator MG are directly coupled to the sun gear s2 of the second gear device P2, and they rotate together.
- the first brake B1 When the first brake B1 is engaged, the absolute value of the rotational speed of the sun gear s2 of the second planetary gear set P2 is reduced and transmitted to the ring gear r2 of the second planetary gear set P2, and the output shaft Output from O.
- This The gear ratio of the second gear in the forward mode is set to be smaller than the gear ratio of the first gear in the norel mode.
- the third forward gear can be switched among the first forward gear, the second forward gear and the fourth forward gear in the non-zero mode. That is, the third forward gear is realized by disengaging the first brake stage second force B2 in the Nolarel mode and engaging the third clutch C3. Further, the third forward gear is realized by disengaging the first brake B1 in the parallel mode and the first brake B1 and engaging the third clutch C3. Further, the third forward speed is realized by disengaging the first brake B1 from the first forward gear and engaging the second clutch C2.
- the Norel mode can be switched between the electric travel mode, in the present embodiment as well as in the first embodiment, the electric power is directly transmitted from the third forward gear in the parallel mode. It is not possible to switch to driving mode. Therefore, when switching to the electric travel mode also in the third forward gear in the Nolarel mode, control is performed to switch to the electric travel mode after switching to the second forward speed or the fourth forward speed in the parallel mode.
- the control process at this time can be performed in the same manner as described in “16. Special control process” according to the first embodiment.
- the first clutch C1 and the second clutch C2 are engaged as in the first forward speed in the parallel mode.
- the input shaft 1 (engine E) and the motor 'generator MG are directly coupled to the sun gear s2 of the second gear device P2, and they rotate together.
- the third clutch C3 is engaged, the first planetary gear unit P1 and the second planetary gear unit P2 are directly connected so that the whole is integrally rotated, and the rotation of the input shaft I and the motor generator MG The speed is transmitted to the output shaft O with the same speed and output. Therefore, the gear ratio of this third forward gear is 1.
- the fourth forward gear can be switched between the second forward gear and the third forward gear in the Nolarel mode. That is, the fourth forward speed disengages the second forward speed second clutch C2 and engages the third clutch C3. It is realized by Further, the fourth forward speed is realized by disengaging the third forward power second clutch C2 and engaging the first brake B1.
- the parallel mode can also be switched between the electric travel mode. Then, by releasing the engagement of the fourth forward speed third gear C3 in the parallel mode, the second forward speed in the electric travel mode is realized.
- the first clutch C1 is engaged, whereby the sun gear s2 of the second planetary gear unit P2 is motor generator MG Are directly connected and rotate together.
- the third clutch C3 and the first brake B1 are engaged, the absolute value of the rotational speed of the input shaft I (engine E) is increased and transmitted to the ring gear r2 of the second planetary gear device P2. Output shaft O. Therefore, the gear ratio of the fourth forward gear is less than one.
- the respective shift stages of the electric travel mode of the hybrid drive system H according to the present embodiment have substantially the same configuration as that of the first embodiment. That is, in the electric travel mode, this hybrid drive device H decelerates the absolute value of the rotational speed of the motor 'generator MG and transmits it to the output shaft O as the first gear and the second gear as the reduction gear. I have it. In the first forward gear and the second forward gear in these electric travel modes, the second clutch C2 is disengaged, so that the input shaft I is disconnected from the sun gear s2 of the second planetary gear unit P2.
- the first forward gear and the second forward gear in the parallel mode according to the present embodiment are the same as the first embodiment except for the above.
- the first forward speed in the electric travel mode is realized by disengaging the second clutch C2 also in the first forward speed in the parallel mode.
- the second forward gear is disengaged from the second forward gear second clutch C2 in the nolarel mode, or disengaged from the fourth forward gear fourth clutch C3 in the parallel mode. It is realized by Further, by engaging one of the first brake B1 and the second brake B2, it is possible to switch between the first forward gear and the second forward gear in the electric travel mode.
- the hybrid drive device H force electric torque converter mode according to the present embodiment
- a control process for determining which one of the operation mode capable of synchronous switching and the plurality of shift speeds are to be selected in the power mode switching will be described.
- the operation mode and the gear shift that can be synchronously switched from the electric torque converter mode there are a first forward gear in the engine travel mode and a second gear in the parallel mode.
- a control process is performed to determine whether to select these deviations.
- FIG. 28 is a flowchart showing this control process. This control process roughly uses a different battery charge threshold depending on the rotation direction of the motor 'generator MG, and uses the drive power of the motor' generator MG if the battery charge is higher than this threshold.
- the second forward gear in the parallel mode is selected, and if the battery charge amount is less than this threshold value, control is performed to select the first forward gear in the engine running mode without using the driving force of the motor generator MG.
- This control process is performed by the control device ECU making a determination based on the information from each portion of the vehicle and outputting a command signal to each portion of the hybrid drive device H such as the hydraulic control device 13 or the like. The details will be described below.
- the control unit ECU determines whether or not the current state of the hybrid drive unit H is the electric torque converter mode (step # 21). If the current state is not the electric torque converter mode (step # 21: No), the process ends since this control process does not need to be performed. Then, if the current state is the electric torque converter mode (step # 21: Yes), then the control unit ECU detects that the motor 'generator's rotation detection means 34 detects the motor' generator MG. Determine whether the rotation speed is less than zero (rotation speed is negative) (step # 22). If the rotational speed of the motor 'generator MG is less than zero (step # 22: Yes), the hybrid drive H will be in the state shown in the velocity diagram of FIG.
- the motor 'generator MG is generated until the rotational speed of motor' generator MG becomes zero, ie, the state shown in FIG. It is necessary to increase the rotational speed while
- the rotational speed of the motor / generator MG has become zero (the state shown in FIG. 27).
- the rotational speed of the motor MG must be increased to match the rotational speed of the input shaft I (engine E). That is, in order to switch the electric torque converter mode force to the second forward gear in the parallel mode, it is necessary to feed the motor generator MG using the electric power charged in the battery 11.
- control unit ECU determines whether or not the battery charge amount detected by battery state detection means 33 is equal to or greater than a predetermined first threshold (step # 23).
- a predetermined first threshold it is preferable to set the first threshold value to a value in which a certain amount of allowance is taken into consideration with respect to the lower limit value of the charge amount in the use range of the battery 11. If the battery charge amount is less than the predetermined first threshold (step # 23: No), it can be determined that the charge amount of the battery 11 is small.
- Step # 24 Set the forward target 1st gear of the engine running mode that does not consume 11 power as the switching target (Step # 24).
- step # 23: Yes if the battery charge amount is equal to or greater than the predetermined first threshold (step # 23: Yes), it can be determined that the charge amount of the battery 11 is sufficient, so the engine drive mode is not directly used.
- the mode selecting means 37 for shifting to the rel mode sets the second forward gear in the norel mode as the switching target (step # 25). Then, when the switching point of the operation mode set as the switching target is reached (step # 26), synchronous switching to the operation mode is executed (step # 27).
- the switching point of the operation mode set as the switching target is, as shown in the speed diagram of FIG.
- step # 22: Yes when the rotational speed of the motor 'generator MG detected by the motor' generator rotation detecting means 34 is equal to or more than zero (step # 22: Yes), the hybrid drive device H has the velocity diagram of FIG.
- the rotational speed of the motor 'generator MG is higher than that shown in FIG. Therefore, this state force is also forward 2 speed in parallel mode
- the motor 'generator MG is further cut from that state, and the rotational speed of the motor' generator MG is shown as a straight line representing the state of the second forward gear in the speed diagram of FIG. Needs to be increased to match the rotational speed of input shaft I (engine E).
- the motor 'generator MG is generating power until the rotational speed of the motor' generator MG becomes zero, ie, the state shown in FIG. The rotational speed needs to be reduced.
- control unit ECU determines whether or not the battery charge amount detected by battery state detection means 33 is equal to or greater than a predetermined second threshold (step # 28).
- the second threshold may be set to a value lower than the first threshold. That is, when the rotational speed of the motor generator MG is zero or more, it is necessary to switch by comparison with the case where the rotational speed of the motor generator MG is less than zero to the second forward gear in parallel mode. This is because it is possible to set the margin of the battery 11 less accordingly.
- the amount of surplus power is, for example, as shown in the speed diagram of FIG. 27, from the state where the rotational speed of the motor generator MG is zero, the rotational speed of the motor generator MG of the engine E It is preferable that the amount of power necessary to increase the speed to match the speed.
- the setting of the first threshold and the second threshold is merely an example, and it is of course possible to set to other values.
- the battery charge amount is equal to or more than the predetermined second threshold (step # 28: Yes)
- the rotational speed of motor 'generator MG is increased as it is to shift to the parallel mode.
- the gear selection means 37 sets the second forward gear in the parallel mode as the switching target (step # 25 ).
- the mode selection means 37 selects the first forward gear of the engine running mode. Set as the switching target (step # 29). However, in this case, if the motor 'generator MG is caused to generate a rotational torque in the negative direction in order to make the rotational speed of the motor' generator MG zero, the vehicle speed is lowered and the traveling condition can not be maintained. Therefore, in this case, the control unit ECU increases the rotational speed of the engine E while maintaining the rotational torque of the motor 'generator MG (step # 30).
- step # 31 the switching point of the operation mode, ie, the point at which the rotational speed of the motor 'generator MG becomes zero is reached.
- Step # 27 the synchronous switching to the forward 1st gear stage of the engine travel mode is performed.
- the process continues the process of step # 30 until the operation mode switching point is reached. The process ends here.
- the hybrid drive unit H according to the present embodiment is similar in configuration to the hybrid drive unit H according to the third embodiment, but has a configuration in which the noblel mode, the electric travel mode, and the engine travel mode are further multistaged. It has six gear stages in parallel mode, three gear stages in electric drive mode, and two gear stages in engine drive mode.
- the hybrid drive device H according to the present embodiment will be described focusing on the differences from the third embodiment.
- the system configuration of the hybrid drive device H according to the present embodiment is the same as that shown in FIG. 2, and thus the description thereof will be omitted. Further, the other configurations are the same as those of the third embodiment in the points which are not particularly described.
- FIG. 29 is a skeleton diagram showing a configuration of a hybrid drive device H according to the present embodiment.
- the hybrid drive device H also has an input shaft I connected to the engine E and an output shaft O connected to the wheels W (see FIG. 2), as in the above embodiments.
- a motor 'generator MG, a first planetary gear set P1, and a second planetary gear set P2 are provided. And these structures are stored in case Ds as a non-rotating member fixed to a vehicle body.
- the configuration of the first planetary gear device P1 is the third one except that the carrier cal is connected to the second sun gear s3 of the second planetary gear device P2.
- the second planetary gear unit P2 is configured to have four rotating elements, which is different from the third embodiment.
- the number of frictional engagement elements is correspondingly larger than in the third embodiment.
- the second planetary gear device P2 is formed of a Rabijo-type planetary gear device disposed coaxially with the input shaft I.
- the second planetary gear unit P2 is a long pinion gear that engages with both the first sun gear s2 and the second sun gear s3, the ring gear r2, and both the first sun gear s2 and the ring gear r2.
- It has a common carrier ca2 that supports a short gear and a short gear engaged with the second sun gear s3 as a rotation element.
- the ring gear r2 is connected to rotate integrally with the output shaft O.
- the first sun gear s2 is selectively connected to the sun gear si of the first planetary gear device P1 via the first clutch C1, and is selectively connected to the input shaft I via the second clutch C2. That is, in this first sun gear s2, the rotation of the input shaft I is selectively transmitted by the second clutch C2, and the rotation of the motor generator MG is selectively transmitted by the first clutch C1.
- the second sun gear s3 is connected to rotate integrally with the carrier cal of the first planetary gear unit P1.
- the carrier cal of the second sun gear s3 and the first planetary gear set P1 is selectively fixed to the case Ds via the second brake B2.
- the carrier ca2 is selectively fixed to the case Ds via the third brake B3 and selectively connected to the input shaft I via the third clutch C3.
- the first sun gear s2, the ring gear r2 and the second sun gear s3 respectively correspond to the “first rotating element (1)” and the “second rotating element (second) of the second freewheel device P2 according to the present invention. 2) ”and“ third rotation element (3) ”.
- the carrier ca2 is the middle of the second planetary gear device P2 in the present invention. It corresponds to "interrotation element (m)".
- FIG. 30 is an operation table showing the operating states of the respective frictional engagement elements Cl, C2, C3, Bl, B2, B3 in a plurality of operating modes and one or more shift speeds provided for each operating mode.
- FIGS. 31, 32, and 33 correspond to FIGS. 25, 26, and 27 related to the third embodiment. That is, these figures show the velocity diagrams of the first planetary gear unit P1 and the second planetary gear unit P2, FIG. 31 is a velocity diagram in the electric torque comparator mode, and FIG. 32 is a parallel diagram. Fig. 33 shows the velocity diagram in the engine running mode. Note that “1st”, “2nd”, and “3rd” in FIG.
- each of the plurality of vertical lines arranged in parallel corresponds to each rotating element of the first planetary gear device P1 and the second planetary gear device P2. It corresponds. That is, “sl”, “cal” and “rl” described on the upper side of each vertical line correspond to the sun gear si, carrier cal and ring gear rl of the first planetary gear unit PI, respectively, “s2” and “r2”.
- the “ca2” and “s3” correspond to the first sun gear s2, the ring gear r2, the carrier ca2 and the second sun gear s3 of the second planetary gear unit P2, respectively.
- the straight line L1 indicates the operating state of the first planetary gear device P1
- the straight line L2 indicates the operating state of the second planetary gear device P2.
- each straight line indicates the operating state of the first planetary gear unit P1 and the second planetary gear unit P2 at each shift speed.
- the hybrid drive device H includes an “electric torque converter mode”, a “parallel mode”, and an “electric travel mode” using one motor generator / generator MG.
- the fourth embodiment is the same as the third embodiment in that it is configured to be switchable between four operation modes of “engine travel mode” and “engine travel mode”.
- the drive drive device H has more gear stages than the third embodiment, and specifically, it has six gear stages in Nolarel mode and the electric traveling mode. There are three gear stages in the engine running mode and two gear stages in the engine running mode.
- the operation state of the hybrid drive device H in each operation mode will be described in detail.
- the second clutch C2 and the first brake B1 are engaged.
- the ring gear rl of the first planetary gear device P1 is fixed to the case Ds, and the first sun gear s2 of the second planetary gear device P2 is connected to rotate integrally with the input shaft I.
- the rotational speed of the ring gear rl on the other side with respect to the sun gear si on one side in the rotational speed order becomes zero.
- the absolute value of the rotational speed of the sun gear si connected so as to rotate integrally with the motor generator MG is decelerated and transmitted to the carrier cal which is intermediate in the order of the rotational speed. Therefore, the first planetary gear unit P1 reduces the absolute value of the rotational speed of the motor / generator MG and transmits it to the second sun gear s3 of the second planetary gear unit P2. As a result, the rotational torque of the motor / generator MG amplified according to the gear ratio by the first planetary gear unit P1 is transmitted to the second sun gear s3 of the second planetary gear unit P2.
- ring gear r 2 which is the second in order of rotational speed, rotates integrally with output shaft O, and the first in rotational speed order.
- the first sun gear s2 that rotates with the input shaft I rotates integrally.
- the rotation of the motor 'generator MG decelerated by the first planetary gear device P1 is transmitted to the second sun gear s3 that is the fourth in the order of rotational speed.
- the third carrier ca2 in the order of rotational speed is in a freely rotatable state.
- “the order of rotation speed” is the order from high speed to low speed.
- the second planetary gear unit P2 is The rotation of the motor 'generator MG and the rotation of the input shaft 1 (engine E) are synthesized and transmitted to the output shaft O. That is, in the second planetary gear device P2, the rotational torque force of the motor 'generator MG transmitted to the second sun gear s3 via the first planetary gear device P1 is transmitted to the first sun gear s2. These rotational torques are synthesized and transmitted to the output shaft O by being the reaction force of the rotational torque E).
- the second sun gear s3 is a negative rotation
- the first sun gear s2 integrally rotating with the engine E and the input shaft I is a positive rotation
- the rotational speed of the ring gear r2 located in the middle of these in the order of rotational speeds
- the absolute value is reduced relative to the absolute value of the rotational speed of the first sun gear s2. Therefore, as in the third embodiment, the second planetary gear device P2 decelerates the absolute value of the rotational speed of the input shaft I and transmits it to the output shaft O. Thereby, the rotational torque of the input shaft I is amplified and transmitted to the output shaft O.
- the hybrid drive device H functions as an electric torque converter by operating in the same manner as in the third embodiment.
- the hybrid drive device H operates in the same manner as the third embodiment, so that, in mode switching from the electric torque converter mode, the third forward gear in the nolarel mode and the forward in the engine travel mode 2 Synchronous switching to the high gear is possible.
- the third forward gear in the parallel mode corresponds to the second forward gear in the parallel mode in the third embodiment, and the second forward gear in the engine travel mode in the third embodiment. It corresponds to the first forward gear in the engine driving mode.
- the rotational speed of the rotation side member of the third brake B3 is set to zero. Synchronous switching to engage the brake B3 is configured to be possible.
- the carrier ca2 of the second planetary gear device P2 corresponds to the rotation side member of the third brake B3.
- the rotational torque in the positive direction of motor 'generator MG is further increased from the state shown in FIG. 31 to increase the rotational speed (the absolute value of the rotational speed in the negative direction is decreased).
- the rotation speed of the carrier ca2 of the second planetary gear device P2, which is the rotation side member of the third brake B3, as shown by the straight line L2 representing the state of the first forward speed in the speed diagram of FIG. Can be zero. Therefore, an impact etc. is generated It is possible to engage the third brake B3 without causing it. And, as shown in FIG. 30, by engaging the third brake B3, it is possible to switch from the electric torque converter mode to the first forward gear in the engine running mode, and accordingly, between them, Synchronous switching can be realized.
- the hybrid drive system H has the first forward gear and the second forward gear in the engine travel mode.
- the second clutch C2 in the first forward speed in the engine travel mode, the second clutch C2, the first brake B1 and the third brake B3 are engaged.
- the second clutch C2 is engaged, whereby the input shaft of the first sun gear s2 of the second planetary gear unit P2 is 1 (Engine E) is directly connected and rotates together.
- the first brake B1 and the third brake B3 are engaged, the rotation of the ring gear rl of the first planetary gear device P1 and the carrier ca2 of the second planetary gear device P2 is stopped.
- the carrier ca2 of the second planetary gear unit P2 fixed to the case Ds by the third brake B3 receives the reaction force of the rotational torque of the input shaft 1 (engine E), and the rotational torque of the motor 'generator MG It becomes an unnecessary state.
- the absolute value of the rotational speed of the sun gear s2 of the second planetary gear train P2 to which the input shaft I is connected is decelerated, transmitted to the ring gear of the second planetary gear train P2, and output from the output shaft O.
- the second sun gear s3 of the second planetary gear unit P2 fixed to the case Ds by the second brake B2 receives the reaction force of the rotational torque of the input shaft 1 (engine E), and the motor 'generator MG rotates The torque is not required.
- the absolute value of the rotational speed of the sun gear s2 of the second planetary gear set P2 to which the input shaft I is connected is decelerated to provide a second planetary gear It is transmitted to the ring gear r2 of position P2 and output from the output shaft O.
- hybrid drive device H in the parallel mode, is configured as the first gear, the second gear, and the second gear as the reduction gear that is configured by connecting input shaft I and motor 'generator MG directly.
- the third gear stage is also configured by connecting the input shaft I and the motor generator / generator MG directly, and the fourth forward gear as a direct coupling stage that transmits the rotational speed of the input shaft I to the output shaft O at the same speed.
- the absolute value of the rotational speed of the input shaft I is accelerated and transmitted to the output shaft O, and the absolute value of the rotational speed of the motor 'generator MG is decelerated and transmitted to the output shaft O It has five gears and six forward gears.
- the operating state of the hybrid drive device H at each speed change stage will be described.
- the first clutch Cl, the second clutch C2, and the third brake B3 are engaged in the first forward speed. Then, as shown in FIGS. 29 and 32, in the first forward speed, the first clutch C1 and the second clutch C2 are engaged, whereby the first sun gear s2 of the second planetary gear device P2 is engaged.
- the input shaft 1 (engine E) and the motor 'generator MG are directly connected, and they rotate together.
- the third brake B3 is engaged, the absolute value of the rotational speed of the first sun gear s2 of the second planetary gear set P2 is decelerated and transmitted to the ring gear r2 of the second planetary gear set P2, Output from output axis O.
- the gear ratio of the first forward gear is set to be the largest among the plurality of gear stages in the non-zero mode.
- the gear ratio of the second forward gear is set to be smaller than the gear ratio of the first forward gear.
- the first clutch Cl, the second clutch C2, and the first brake B1 are engaged.
- the first clutch C1 and the second clutch C2 are engaged, whereby the second planetary gear unit
- the input shaft 1 (engine E) and the motor generator MG are directly connected to the first sun gear s2 of P2, and they rotate together.
- the first brake B1 is engaged, the absolute value of the rotational speed of the first sun gear s2 of the second planetary gear set P2 is reduced and transmitted to the ring gear r2 of the second planetary gear set P2.
- the gear ratio of the third forward gear is set to be smaller than the gear ratio of the second forward gear.
- the gear ratio of this fourth forward gear is 1.
- the hybrid drive system H according to the present embodiment also has a configuration that can not realize the shift ratio of the transmission ratio force with the input shaft 1 (engine E) separated as in the first embodiment.
- the fourth forward gear in parallel mode can not be directly switched to electric travel mode. Therefore, as in the control process described in “1-6. Special control process” according to the first embodiment, when switching from the fourth forward speed in the parallel mode to the electric travel mode, the forward mode in the parallel mode After switching to 3rd gear or 5 forward gears, control to switch to electric travel mode is performed.
- the first clutch Cl, the third clutch C3, and the first brake B1 are engaged.
- the first clutch C1 is engaged, whereby the motor 'generator MG is engaged with the first sun gear s2 of the second planetary gear device P2. It will be in a state where it is directly connected and rotates integrally.
- the third With the clutch C3 and the first brake Bl engaged the absolute value of the rotational speed of the input shaft I (engine E) is increased and transmitted to the ring gear r2 of the second planetary gear set P2, and the output power Output from axis O. Therefore, the gear ratio of the fifth forward gear is less than one.
- the first clutch Cl, the third clutch C3, and the second brake B2 are engaged.
- the first clutch C1 is engaged, whereby the motor 'generator MG is engaged with the first sun gear s2 of the second planetary gear unit P2. It will be in a state where it is directly connected and rotates integrally.
- the third clutch C3 and the second brake B2 are engaged, the absolute value of the rotational speed of the input shaft I (engine E) is increased and transmitted to the ring gear r2 of the second planetary gear set P2. And output from the output axis O.
- the gear ratio of the sixth forward gear is set to be smaller than the gear ratio of the fifth forward gear.
- the drive device H decelerates the absolute value of the rotational speed of the motor's generator MG and transmits it to the output shaft O as the first forward gear as the reduction gear. , 2nd gear forward, and 3rd gear forward.
- the input shaft I is moved to the second planetary gear unit by disengaging the second clutch C2. It is the same as the first forward gear, the second forward gear and the third forward gear in the parallel mode except that the first sun gear s2 force of P2 is separated.
- FIGS. 34 to 36 show an example in which the first planetary gear device P1 has three rotating elements and the second planetary gear device P2 has four rotating elements, as shown in FIG. 37.
- FIG. 40 shows an example in which the first planetary gear device P1 has four rotating elements and the second planetary gear device P2 has three rotating elements.
- the following points are common. That is, in the first planetary gear unit P1, the motor 'generator MG is connected to the first rotating element (1), and the third rotating element (3) is fixed to the case Ds by the brake.
- the input shaft I is connected to the first rotating element (1)
- the output shaft O is connected to the second rotating element (2)
- the first rotating element (3) is connected to the first
- the second rotating element (2) of the planetary gear set P1 is connected.
- the arrangement of vertical lines corresponding to the respective rotating elements in these velocity diagrams is determined by the setting of the gear ratios of the first planetary gear device P1 and the second planetary gear device P2.
- various configurations capable of realizing the number of rotating elements required in each example can be applied. .
- the arrangement of the vertical lines corresponding to each rotation element is from the low speed side to the high speed side (right side to left side in the drawing) of the first planetary gear device P1.
- the vertical line corresponding to the fourth rotation element (4) of 2 and the vertical line corresponding to the third rotation element (3) of the first planetary gear device P1 are arranged in the order listed.
- the arrangement of the vertical lines corresponding to each rotating element is the low speed side force high speed side of the rotational speed of the first planetary gear device P1 (see FIG. A vertical line corresponding to the first rotating element (1) of the first planetary gear unit P1 and the second planetary gear unit P2, and a second rotating element (2 of the second planetary gear unit P2) ), A vertical line corresponding to the intermediate rotating element (m) of the second planetary gear unit P2, a second rotating element (2) of the first planetary gear unit P1 and a third of the second planetary gear unit P2
- the vertical line corresponding to the rotating element (3) and the vertical line corresponding to the third rotating element (3) of the first planetary gear device P1 are arranged in this order.
- the second planetary gear unit P2 is replaced by the intermediate rotation element (m), and the fourth rotation element (4) following the third rotation element (3) is arranged in the order of rotational speed.
- the vertical line corresponding to the fourth rotating element (4) corresponds to the second rotating element (2) of the first planetary gear train P1 and the third rotating element (second planetary gear train P2) in the order of rotational speed.
- This embodiment differs from the example shown in FIG. 31 in that it is disposed between the vertical line corresponding to 3) and the vertical line corresponding to the third rotating element (3) of the first planetary gear device P1.
- the arrangement of the vertical lines corresponding to each of the rotating elements is as follows from the low speed side of the rotation speed of the first planetary gear device P1 toward the high speed side (right Vertical line corresponding to the first rotation element (1) of the first planetary gear unit P1 and the second planetary gear unit P2, vertical line corresponding to the second rotating element (2) of the second planetary gear unit P2, first planet Vertical line corresponding to the second rotating element (2) of the gear unit P1 and the third rotating element (3) of the second planetary gear unit P2, corresponding to the third rotating element (3) of the first planetary gear unit P1
- the vertical lines are in the order of the vertical lines corresponding to the fourth rotation element (4) of the second planetary gear device P2. That is, in the example shown in FIG.
- the second planetary gear unit P2 is used as an intermediate rotating element (m). Instead, it has the fourth rotation element (4) following the third rotation element (3) in the order of rotation speed, and the vertical line corresponding to this fourth rotation element (4) is the first in the order of rotation speed. It differs from the example shown in FIG. 31 in that it is arranged next to the vertical line corresponding to the third rotation element (3) of the planetary gear device P1.
- the arrangement of the vertical lines corresponding to each of the rotating elements is as follows from the low speed side of the rotation speed of the first planetary gear device P1 toward the high speed side (right side to left side in the drawing).
- Vertical line corresponding to the first rotation element (1) of the first planetary gear unit P1 and the second planetary gear unit P2 vertical line corresponding to the second rotating element (2) of the second planetary gear unit P2, first planet Longitudinal line corresponding to the second rotating element (2) of the gear unit P1 and the third rotating element (3) of the second planetary gear unit P2, the third rotating element (3) of the first planetary gear unit P1 and the second planet
- the vertical lines correspond to the fourth rotation element (4) of the gear unit P2. That is, in the example shown in FIG.
- the second planetary gear device P2 is replaced by the intermediate rotating element (m) and the fourth rotating element (4) following the third rotating element (3) is arranged in the order of rotational speed.
- the vertical line corresponding to the fourth rotation element (4) is arranged to coincide with the vertical line corresponding to the third rotation element (3) of the first planetary gear device P1.
- “A1”, “B1”, “C1”, and “D1” arranged in the order of the rotational speeds described on the upper side of the vertical lines in the velocity diagram shown in FIG. 37 are respectively the first planetary gears It corresponds to the first rotational element (1), the second rotational element (2), the intermediate rotational element (m) and the third rotational element (3) of the apparatus PI. Further, “a2”, “b2” and “c2” arranged in the order of rotational speed on the upper stage of these are the first rotating element (1) and the second rotating element (2) of the second planetary gear device P2, respectively. ), Corresponds to the third rotation element (3). In the example shown in FIG.
- the arrangement of the vertical lines corresponding to the respective rotating elements is as follows from the low speed side of the rotational speed of the first planetary gear device P1 to the high speed side (right side to left side in the drawing).
- the first planetary gear device P1 and the first of the second planetary gear device P2 The longitudinal line corresponding to the rotating element (1), the longitudinal line corresponding to the second rotating element (2) of the second planetary gear set P2, the second rotating element (2) of the first planetary gear set P1 and the second planet Longitudinal line corresponding to the third rotating element (3) of the gear train P2, vertical line corresponding to the intermediate rotating element (m) of the first planetary gear train P1, third rotating element of the first planetary gear train P1 (3 The order of the vertical lines corresponding to).
- the first planetary gear unit P1 has an intermediate rotating element (m), which is the second rotating element (2) of the first planetary gear unit P1 and the second planetary gear unit P2. 31 in that it is disposed between the vertical line corresponding to the third rotation element (3) of the first embodiment and the vertical line corresponding to the third rotation element (3) of the first planetary gear device P1 It is different.
- the arrangement of the vertical lines corresponding to the respective rotating elements is as follows from the low speed side of the rotational speed of the first planetary gear unit P1 to the high speed side (right side to left side in the drawing).
- Vertical line corresponding to the first rotating element (1) of the first planetary gear unit P1 and the second planetary gear unit P2 vertical line corresponding to the second rotating element (2) of the second planetary gear unit P2, first planet A vertical line corresponding to the intermediate rotating element (m) of the gear unit P1, a second rotating element (2) of the first planetary gear unit P1, and a third rotating element (3) of the second planetary gear unit P2.
- the vertical lines are in the order of the vertical lines corresponding to the third rotating element (3) of the first planetary gear unit P1. That is, in the example shown in FIG.
- the first planetary gear unit P1 has an intermediate rotating element (m 2), which corresponds to the vertical line corresponding to the second rotating element (2) of the second planetary gear unit P2, and 31.
- the example shown in FIG. 31 in that it is disposed between the second rotary element (2) of the planetary gear unit P1 and the vertical line corresponding to the third rotary element (3) of the second planetary gear unit P2. It is different.
- the arrangement of the vertical lines corresponding to the respective rotating elements is as follows from the low speed side of the rotational speed of the first planetary gear unit P1 to the high speed side (right side to left side in the drawing).
- Vertical line corresponding to the first rotating element (1) of the first planetary gear unit P1 and the second planetary gear unit P2 vertical line corresponding to the intermediate rotating element (m) of the first planetary gear unit P1, second planetary gear unit
- the lines are in the order of the longitudinal lines corresponding to the third rotating element (3) of the first planetary gear unit P1.
- the first planetary gear set P1 has an intermediate rotating element (m), which is the first rotating element (1) of the first planetary gear set P1 and the second planetary gear set P2.
- m intermediate rotating element
- “A1”, “B1”, “C1”, and “D1” arranged in the order of the rotational speeds described on the upper side of the vertical lines in the velocity diagram shown in FIG. It corresponds to the first rotational element (1), the intermediate rotational element (m), the second rotational element (2) and the third rotational element (3) of the apparatus PI. Further, “a2”, “b2” and “c2” arranged in the order of rotational speed on the upper stage of these are the first rotating element (1) and the second rotating element (2) of the second planetary gear device P2, respectively. ), Corresponds to the third rotation element (3). In the example shown in FIG.
- the arrangement of the vertical lines corresponding to the respective rotating elements is as follows from the low speed side of the rotational speed of the first planetary gear device P1 to the high speed side (right side to left side in the drawing).
- the power hybrid drive device H described in the configuration including only one motor 'generator MG as a rotating electrical machine may be configured to include two or more motor' generator MG's. It is one of the preferred embodiments of the invention.
- FIG. 41 it is preferable to further include a second motor 'generator MG2 and a rotor Ro2 of the second motor' generator MG2 is connected to the input shaft I.
- This rotor Ro2 is a drive transmission member such as a gear or a belt. It may be configured to be connected via the input shaft I.
- the hybrid drive unit H is configured to be able to switch between three operation modes, that is, the electric torque converter mode, the parallel mode, and the electric travel mode.
- the hybrid drive system H has been described as being switchable to the engine travel mode in addition to these three operation modes.
- the configuration of the hybrid drive device H to which the present invention is applicable is not limited to these. That is, the hybrid drive device H can be configured to realize only the electric torque converter mode or to realize either the electric torque converter mode, the parallel mode, or the electric travel mode. It is one of the preferred embodiments of the present invention.
- the present invention can be used as a drive device for a hybrid vehicle.
- FIG. 1 A skeleton diagram of a hybrid drive system according to a first embodiment of the present invention
- FIG. 2 A system configuration diagram of a drive system for a hybrid vehicle according to a first embodiment
- FIG. 3 The schematic diagram showing the connection state of each component of embodiment
- FIG. 5 A diagram showing the relationship between switchable operation modes and shift speeds of the first embodiment.
- FIG. 6 A diagram showing an example of a control map of the first embodiment
- FIG. 7 A velocity diagram in the electric torque converter mode of the first embodiment
- FIG. 9 A diagram showing a flowchart of special control processing of the first embodiment.
- FIG. 10 A skeleton diagram of a hybrid drive system according to a second embodiment of the present invention
- FIG. 11 A diagram showing an operation table of the second embodiment
- FIG. 12 A velocity diagram in the electric torque converter mode of the second embodiment
- FIG. 14 A velocity diagram (1) showing another configuration example of the second embodiment
- FIG. 15 A velocity diagram (2) showing another configuration example of the second embodiment
- FIG. 16 A velocity diagram (3) showing another configuration example of the second embodiment
- FIG. 17 A velocity diagram showing another configuration example of the second embodiment (4)
- FIG. 18 A velocity diagram (5) showing another configuration example of the second embodiment
- FIG. 19 A velocity diagram (6) showing another configuration example of the second embodiment
- FIG. 20 A skeleton diagram of a hybrid drive system according to a third embodiment of the present invention
- FIG. 21 A schematic view showing the connection state of each component of the third embodiment
- FIG. 22 A diagram showing an operation table of the third embodiment
- FIG. 23 A diagram showing the relationship between switchable operation modes and shift speeds of the third embodiment.
- FIG. 24 A diagram showing an example of a control map of the third embodiment
- FIG. 27 A velocity diagram in the engine travel mode of the third embodiment
- FIG. 28 A diagram showing a flowchart of special control processing of the third embodiment.
- FIG. 29 A skeleton diagram of a hybrid drive system according to a fourth embodiment of the present invention
- FIG. 30 A diagram showing an operation table of the fourth embodiment
- FIG. 31 A velocity diagram in the electric torque converter mode of the fourth embodiment
- FIG. 32 Velocity diagram in parallel mode of the fourth embodiment
- FIG. 33 A velocity diagram in the engine travel mode of the fourth embodiment
- FIG. 34 Velocity diagram (1) showing another configuration example of the fourth embodiment
- FIG. 35 A velocity diagram (2) showing another configuration example of the fourth embodiment
- FIG. 36 A velocity diagram (3) showing another configuration example of the fourth embodiment
- FIG. 37 Velocity diagram showing another configuration example of the fourth embodiment (4)
- FIG. 38 Velocity diagram (5) showing another configuration example of the fourth embodiment
- FIG. 39 A velocity diagram (6) showing another configuration example of the fourth embodiment
- FIG. 40 Velocity diagram (7) showing another configuration example of the fourth embodiment
- FIG. 41 A skeleton diagram of a hybrid drive system according to another embodiment of the present invention.
- FIG. 42 A skeleton diagram of a hybrid drive system according to the background art
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
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CN2007800010336A CN101351352B (zh) | 2006-05-25 | 2007-03-16 | 混合驱动装置 |
DE112007000041T DE112007000041B4 (de) | 2006-05-25 | 2007-03-16 | Hybridantriebsvorrichtung |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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JP2006145570A JP4158122B2 (ja) | 2006-05-25 | 2006-05-25 | ハイブリッド駆動装置 |
JP2006-145570 | 2006-05-25 |
Publications (1)
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WO2007138777A1 true WO2007138777A1 (ja) | 2007-12-06 |
Family
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PCT/JP2007/055344 WO2007138777A1 (ja) | 2006-05-25 | 2007-03-16 | ハイブリッド駆動装置 |
Country Status (5)
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US (1) | US7931555B2 (ja) |
JP (1) | JP4158122B2 (ja) |
CN (1) | CN101351352B (ja) |
DE (1) | DE112007000041B4 (ja) |
WO (1) | WO2007138777A1 (ja) |
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JP7062333B2 (ja) * | 2018-01-10 | 2022-05-06 | ジヤトコ株式会社 | パワートレイン |
CN108859730B (zh) * | 2018-06-19 | 2021-04-20 | 江苏大学 | 一种多离合器无动力中断换挡混合动力装置及其工作方法 |
DE102019205749A1 (de) * | 2019-04-23 | 2020-10-29 | Zf Friedrichshafen Ag | Getriebevorrichtung für ein Hybridfahrzeug |
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2007
- 2007-03-16 DE DE112007000041T patent/DE112007000041B4/de not_active Expired - Fee Related
- 2007-03-16 WO PCT/JP2007/055344 patent/WO2007138777A1/ja active Application Filing
- 2007-03-16 CN CN2007800010336A patent/CN101351352B/zh not_active Expired - Fee Related
- 2007-05-24 US US11/802,741 patent/US7931555B2/en not_active Expired - Fee Related
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Also Published As
Publication number | Publication date |
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DE112007000041B4 (de) | 2012-05-24 |
JP4158122B2 (ja) | 2008-10-01 |
CN101351352B (zh) | 2011-11-23 |
DE112007000041T5 (de) | 2008-08-28 |
CN101351352A (zh) | 2009-01-21 |
JP2007314032A (ja) | 2007-12-06 |
US7931555B2 (en) | 2011-04-26 |
US20070275808A1 (en) | 2007-11-29 |
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