WO2011045964A1 - ハイブリッド車両 - Google Patents
ハイブリッド車両 Download PDFInfo
- Publication number
- WO2011045964A1 WO2011045964A1 PCT/JP2010/062475 JP2010062475W WO2011045964A1 WO 2011045964 A1 WO2011045964 A1 WO 2011045964A1 JP 2010062475 W JP2010062475 W JP 2010062475W WO 2011045964 A1 WO2011045964 A1 WO 2011045964A1
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- WIPO (PCT)
- Prior art keywords
- rotor
- stator
- power
- torque
- rotating machine
- 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]
- B60L58/15—Preventing overcharging
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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
- B60K6/26—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 motors or the generators
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
- B60K6/44—Series-parallel type
- B60K6/448—Electrical distribution type
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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
- 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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- 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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- B60L50/00—Electric propulsion with power supplied within the vehicle
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- B60L50/16—Electric propulsion with power supplied within the vehicle using propulsion power supplied by engine-driven generators, e.g. generators driven by combustion engines with provision for separate direct mechanical propulsion
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- B—PERFORMING OPERATIONS; TRANSPORTING
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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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- B—PERFORMING OPERATIONS; TRANSPORTING
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/04—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units
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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
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- B60W10/24—Conjoint control of vehicle sub-units of different type or different function including control of energy storage means
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- B60W50/00—Details of control systems for road vehicle drive control not related to the control of a particular sub-unit, e.g. process diagnostic or vehicle driver interfaces
- B60W50/04—Monitoring the functioning of the control system
- B60W50/045—Monitoring control system parameters
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K51/00—Dynamo-electric gears, i.e. dynamo-electric means for transmitting mechanical power from a driving shaft to a driven shaft and comprising structurally interrelated motor and generator parts
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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
- B60L2220/00—Electrical machine types; Structures or applications thereof
- B60L2220/10—Electrical machine types
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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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- B—PERFORMING OPERATIONS; TRANSPORTING
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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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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
- F16H37/10—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing at both ends of intermediate shafts
- F16H2037/102—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing at both ends of intermediate shafts the input or output shaft of the transmission is connected or connectable to two or more differentials
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/62—Hybrid vehicles
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/64—Electric machine technologies in electromobility
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/70—Energy storage systems for electromobility, e.g. batteries
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/7072—Electromobility specific charging systems or methods for batteries, ultracapacitors, supercapacitors or double-layer capacitors
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/72—Electric energy management in electromobility
Definitions
- the present invention relates to a hybrid vehicle driven by a power unit for driving a driven part.
- Patent Document 1 As a conventional power plant of this type, for example, one disclosed in Patent Document 1 is known.
- This power plant is for driving the left and right drive wheels of the vehicle, and includes an internal combustion engine as a power source, and a transmission connected to the internal combustion engine and the drive wheels.
- This transmission has a first and a second planetary gear set constructed in a general single pinion type, and a first and a second rotating machine provided with one rotor and one stator, respectively.
- the first ring gear, the first carrier, and the first sun gear of the first planetary gear set are mechanically connected to the internal combustion engine, the second carrier of the second planetary gear set, and the first rotating machine, respectively. It is done.
- the second sun gear, the second carrier, and the second ring gear of the second planetary gear set are mechanically connected to the second rotating machine, the driving wheel, and the first rotating machine, respectively.
- the first and second rotating machines are electrically connected to each other via a controller.
- mechanical connections are indicated by solid lines and electrical connections are indicated by dashed dotted lines in connection with elements.
- the flow of power and power is indicated by thick solid lines with arrows.
- the power of the internal combustion engine is transmitted to the drive wheels, for example, in the following manner while the vehicle is traveling. That is, as shown in FIG. 141, after the power of the internal combustion engine is transmitted to the first ring gear, it is synthesized with the power transmitted to the first sun gear as described later, and this synthesized power is transmitted through the first carrier. Is transmitted to the second carrier. Further, in this case, power generation is performed by the second rotating machine, and the generated electric power is supplied to the first rotating machine via the controller. With this power generation, a part of the combined power transmitted to the second carrier is distributed to the second sun gear and the second ring gear, and the remaining combined power is transferred to the drive wheels.
- the power distributed to the second sun gear is transmitted to the second rotating machine, and the power distributed to the second ring gear is transmitted to the first sun gear via the first rotating machine. Further, the power of the first rotating machine generated along with the supply of the power described above is transmitted to the first sun gear.
- the power plant in addition to the first and second rotating machines, at least two planetary gear units for distributing and combining the power are essential in its construction, and accordingly, the power plant has a large size Will lead to
- the path consisting of the first carrier ⁇ second carrier ⁇ second ring gear ⁇ first rotating machine ⁇ first sun gear ⁇ first carrier, and the first carrier ⁇ second carrier ⁇ Power is recirculated in a path consisting of second sun gear ⁇ second rotating machine ⁇ first rotating machine ⁇ first sun gear ⁇ first carrier. Because the very large combined power from the first ring gear and the first sun gear passes through the first carrier and passes directly through the second carrier by this power recirculation, in order to withstand this large combined power.
- the size of the first and second planetary gear units has to be increased, which leads to a further increase in size and cost of the power plant. Furthermore, with the enlargement of such a power plant and the increase in the power passing through the power plant, the loss generated in the power plant is also increased, and the drive efficiency of the power plant is lowered.
- An object of the present invention is to provide a hybrid vehicle driven by a power plant that can achieve downsizing and cost reduction and can improve driving efficiency.
- a hybrid vehicle is a first rotor in which two adjacent magnetic poles have circumferentially arranged pole rows having mutually different polarities ((1) For example, due to changes in the magnetic poles generated in the plurality of armatures arranged in the circumferential direction and arranged to face the A1 rotor 24 and the first rotor 14) and the first rotor in the radial direction in the embodiment.
- a first stator (for example, the stator 23 and the stator 16 in the embodiment) having an armature row generating a rotating magnetic field moving in the circumferential direction, and the first rotor and the first stator, which are disposed between each other
- a second rotor (for example, the A2 rotor 25 and the second rotor 15 in the embodiment) having a plurality of soft magnetic bodies arranged in the circumferential direction at intervals; and the electric machine of the first stator Child row
- the ratio of the number of generated magnetic poles, the number of magnetic poles of the magnetic pole row of the first rotor, and the number of soft magnetic bodies of the second rotor is 1: m: (1 + m) / 2 (where m is an integer)
- a first rotating machine (for example, the first rotating machine 21 and the first rotating machine 10 in the embodiment) in which the first rotor and one of the second rotors are connected to the drive shaft
- a motor for example, the engine 3 in the embodiment) whose output shaft is
- a capacitor capable of transferring power between the first rotating machine and the second rotating machine e.g. And a battery 33, a battery 33
- the battery is a state detection unit (for example, a current / voltage sensor 56 in the embodiment) for detecting the charge state of the capacitor.
- a control unit for example, the ECU 2 in the embodiment for controlling the power unit, the control unit controlling the remaining capacity of the storage battery when driving the prime mover to start the hybrid vehicle It is characterized by controlling the output of said motor based on it.
- the control unit controls the power unit such that the remaining capacity of the capacitor falls within the range from the lower limit value to the upper limit value, and the remaining capacity of the capacitor is When driving the motor for forward start of the hybrid vehicle at a first threshold value or lower lower than the upper limit value, the rotational magnetic field generated in the first stator of the first rotating machine It is characterized in that the output of the prime mover is lowered by controlling the rotational speed of the magnetic field so as to limit the number of turns of the prime mover low.
- the control unit controls the power unit such that the remaining capacity of the capacitor falls within the range from the lower limit value to the upper limit value, and the remaining capacity of the capacitor is When driving the motor for backward start of the hybrid vehicle under a second threshold value higher than the lower limit value, the rotating magnetic field generated in the first stator of the first rotating machine It is characterized in that the output of the prime mover is lowered by controlling the rotational speed of the magnetic field so as to limit the number of turns of the prime mover low.
- control unit controls the prime mover to maintain an output torque of the prime mover.
- control unit is configured to calculate a predetermined value of the regenerative energy per unit time generated in the first stator of the first rotating machine with respect to the torque required for the prime mover. If so, it is characterized in that the prime mover is controlled to limit the output torque of the prime mover low.
- the control unit controls the power unit such that the remaining capacity of the storage battery falls within the range from the lower limit value to the upper limit value, and the hybrid vehicle
- the motor is driven to drive the first stator of the first rotating machine It controls so that the magnetic field rotational speed of the said rotating magnetic field which generate
- the second rotating machine includes a rotor (for example, the rotor 103 in the embodiment) and an armature (for example, the stator 102 in the embodiment).
- a first rotating element for example, a first sun gear S1 in the embodiment
- a second rotating element for example, in the embodiment that operate in alignment with a motor (for example, the rotating machine 101 in the embodiment).
- a third rotating element (for example, the first ring gear R1 in the embodiment) connected to the rotor, and the energy input to the second rotating element is It has a function of distributing to the first rotating element and the third rotating element, and a function of combining the respective energy inputted to the first rotating element and the third rotating element and outputting the energy to the second rotating element.
- Rotation mechanism eg A first planetary gear unit PS1 in the embodiment, one of the first rotor and the second rotating element, and the second rotor and the first rotating element is the motor It is characterized in that it is connected to an output shaft and the other is connected to the drive shaft.
- a third rotor (for example, an embodiment) in which magnetic pole arrays having two adjacent magnetic poles having different polarities are provided in the circumferential direction.
- B1 rotor 34 the B1 rotor 34
- the third rotor and a rotating magnetic field moving in the circumferential direction is generated due to changes in the magnetic poles generated in the plurality of armatures aligned in the circumferential direction.
- a second stator (for example, a stator 33 in the embodiment) having an armature row, and a plurality of soft members arranged between the third rotor and the second stator and spaced apart from each other in the circumferential direction
- a fourth rotor (for example, the B2 rotor 35 in the embodiment) having a magnetic body, and the number of magnetic poles generated in the armature row of the second stator, and the magnetic pole row of the third rotor Number of magnetic poles,
- the ratio of the fourth rotor to the number of the soft magnetic members is set to 1: m: (1 + m) / 2 (where m ⁇ 1), the first rotor is connected to the drive shaft, and the motor
- the fourth rotor When the second rotor is connected to the output shaft, the fourth rotor is connected to the drive shaft, the third rotor is connected to the output shaft of the motor, and the second drive shaft is connected to the second drive shaft.
- the third rotor is connected to the output shaft of
- the hybrid vehicle of the first aspect of the present invention it is possible to prevent overcharge and discharge of the storage battery.
- FIG. 1 schematically shows a power plant according to a first embodiment
- FIG. It is a block diagram which shows the control apparatus which controls the engine etc. which are shown in FIG. It is an expanded sectional view of the 1st rotary machine shown in FIG. It is a figure which develops the stator of the 1st rotating machine shown in Drawing 1, and the rotor of A1 and A2 in the peripheral direction, and is schematically shown. It is a figure which shows the equivalent circuit of a 1st rotary machine.
- FIG. 6 is a velocity collinear diagram showing an example of the relationship between the first magnetic field electrical angular velocity and the rotor electrical angular velocities A1 and A2 in the first rotary machine shown in FIG.
- FIGS. 7 (a) to 7 (d) are diagrams for explaining the subsequent operation of FIGS. 7 (a) to 7 (c).
- (A), (b) is a figure for demonstrating the operation
- FIG. 8 is a view for explaining the positional relationship between the first stator magnetic pole and the core when the first stator magnetic pole is rotated by an electrical angle 2 ⁇ from the states shown in FIGS. 7 (a) to 7 (c).
- FIG. 7 is a diagram showing an example of transition of back electromotive force of U-phase to W-phase when the A1 rotor of the first rotating machine is held non-rotatable.
- FIG. 8 is a diagram showing an example of transition of back electromotive force of U-phase to W-phase when the A2 rotor of the first rotating machine is held non-rotatable. It is a figure which shows an example of transition of the rotor transmission torque of 1st driving equivalent torque and A1 and A2 in, when holding A2 rotor of a 1st rotary machine non-rotatably. It is an expanded sectional view of the 2nd rotary machine shown in FIG.
- FIG. 20 is a diagram for describing a shift operation of the power plant shown in FIG. 19;
- FIG. 21 is a view showing an example of the relationship between rotational speeds and torques of various types of rotary elements in the power plant shown in FIG. 19, in the case of starting the heat engine while the driven parts are being driven by the first and second rotary machines.
- FIG. 20 is a view showing an example of the relationship between rotational speeds and torques of various types of rotary elements in the power plant shown in FIG. 19 in the case of rapidly increasing the speed of the driven portion.
- FIG. 5 is a diagram showing a state of transmission of torque in the power plant of FIG. 1 during EV creep.
- (A) is each velocity alignment chart of the 1st and 2nd rotary machines 21 and 31 during EV creep of the power plant shown in FIG. 1
- (b) is the velocity alignment chart which synthesize
- (A) is an example of each speed alignment chart of the 1st and 2nd rotary machines 21 and 31 at the time of EV start of the power plant shown in FIG.
- FIG. 7 is a diagram showing a state of transmission of torque in the power plant shown in FIG. 1 at the time of ENG start during EV traveling.
- FIG. 6 is a velocity collinear chart of first and second rotating machines 21 and 31 at the time of ENG start during EV traveling of the power plant shown in FIG. 1. It is the speed alignment chart which synthesize
- FIG. 7 is a diagram showing a state of transmission of torque in the power plant shown in FIG. 1 during ENG traveling in a battery input / output zero mode.
- FIG. 7 is a diagram showing a state of transmission of torque in the power plant shown in FIG. 1 during ENG traveling in the assist mode.
- FIG. 6 is a diagram showing a state of transmission of torque in the power plant shown in FIG. 1 during ENG travel in a drive charging mode.
- (A) is an example of each speed alignment chart of the 1st and 2nd rotary machines 21 and 31 at the time of the start of the sudden acceleration operation under ENG driving of the power plant shown in FIG.
- FIG. 7 is a diagram showing a state of transmission of torque in the power plant shown in FIG. 1 at the time of ENG start while the vehicle is stopped.
- A) is an example of each speed alignment chart of the 1st and 2nd rotating machines 21 and 31 at the time of ENG start during stop of the power plant shown in FIG.
- FIG. 7 is a diagram showing a state of transmission of torque in the power plant shown in FIG. 1 during ENG creep.
- A) is an example of each speed alignment chart of the 1st and 2nd rotating machines 21 and 31 during ENG creep of the power plant shown in FIG. 1,
- FIG. 7 is a diagram showing a state of transmission of torque in the power plant shown in FIG. 1 at the time of ENG start.
- A) is an example of each speed alignment chart of the 1st and 2nd rotary machines 21 and 31 at the time of ENG start of the power plant shown in FIG.
- FIG. 7 is a diagram showing a state of transmission of torque in the power plant shown in FIG. 1 at the time of EV reverse start.
- (A) is an example of each speed alignment chart of the 1st and 2nd rotary machines 21 and 31 at the time of EV reverse start of the power plant shown in FIG. 1
- (b) is a composition of two speed alignment charts It is a velocity alignment chart.
- FIG. 7 is a diagram showing a state of transmission of torque in the power plant shown in FIG. 1 at the time of ENG backward start.
- A) is an example of each speed alignment chart of the 1st and 2nd rotary machines 21 and 31 at the time of ENG reverse start of the power plant shown in FIG.
- (b) is a composition of two speed alignment charts It is a velocity alignment chart. It is a figure which shows the range of battery SOC by which charging / discharging is repeated.
- (A), (b) shows the speed alignment chart when (a) battery SOC is less than the first threshold when the operation mode of the operation apparatus 1 is "ENG start", (b) (b) the battery SOC is The velocity alignment chart at one threshold or more is shown.
- (A), (b) shows the speed alignment chart when (a) the battery SOC is higher than the second threshold when the operation mode of the operation apparatus 1 is "EV travel”, (b) (b) the battery SOC is The velocity alignment chart at the time of 2 threshold values or less is shown.
- (A), (b) shows the speed alignment chart when (a) the battery SOC is higher than the second threshold when the operation mode of the operating device 1 is "ENG backward start", (b) the battery SOC is The velocity alignment chart at the time of below a 2nd threshold value is shown. It is a figure showing roughly the power plant by a 2nd embodiment. It is a figure showing roughly the power plant by a 3rd embodiment. It is a figure showing roughly the power plant by a 4th embodiment. It is a figure showing roughly the power plant by a 5th embodiment. It is a figure showing roughly the power plant by a 6th embodiment. It is a figure showing roughly the power plant by a 7th embodiment.
- FIG. 60 is a diagram for illustrating a shift operation of the first power unit shown in FIG. 59.
- the figure which shows an example of the relationship between the rotational speed of various rotation elements in the 1st power plant shown in FIG. 59, and a torque about the case where a heat engine is started during driving of the driven part by the 1st and 2nd rotary machine. It is.
- FIG. 60 A diagram showing an example of a relationship between rotational speeds and torques of various types of rotary elements in the first power plant shown in FIG. 59 in the case of rapidly increasing the speed of the driven portion.
- FIG. 64 is a diagram for illustrating a shift operation of the second power unit shown in FIG. 63.
- the figure which shows an example of the relationship between the rotational speed of various rotation elements in the 2nd power plant shown in FIG. 63, and a torque about the case where a heat engine is started during driving of the driven part by the 1st and 2nd rotary machine. It is.
- FIG. 64 is a diagram showing an example of the relationship between rotational speeds and torques of various types of rotary elements in the second power plant shown in FIG. 63, in the case of rapidly increasing the speed of the driven portion.
- FIG. 64 is a diagram for illustrating a shift operation of the second power unit shown in FIG. 63.
- the figure which shows an example of the relationship between the rotational speed of various rotation elements in the 2nd power plant shown in FIG. 63, and a torque about the case where a heat engine is started during driving of the driven part by the 1st and 2nd rotary machine. It is.
- FIG. 64 is a diagram showing
- FIG. 59 is a block diagram showing a control device that controls an engine and the like shown in FIG. 58. It is a block diagram which shows the driving force control in the power plant 1F of FIG. It is a speed collinear diagram in the power unit 1F which has the structure of 1 collinear 4 elements.
- FIG. 59 is a diagram showing an example of the relationship between rotational speeds and torques of various types of rotary elements in the power plant shown in FIG. 58, at the start of ENG start during EV travel.
- FIG. 61 is a diagram for describing a speed change operation by the first rotating machine or the rotating machine in the power plant shown in FIG. 58.
- FIG. 59 is a diagram showing an example of a relationship between rotational speeds and torques of various types of rotary elements in the power plant shown in FIG. 58 at the start of a sudden acceleration operation during ENG traveling.
- FIG. 18 schematically shows a power plant according to an eighth embodiment. It is a figure showing roughly the power plant by a 9th embodiment. It is a figure showing roughly the power plant by a 10th embodiment.
- FIG. 21 schematically shows a power plant according to an eleventh embodiment. It is a figure showing roughly the power plant by a 12th embodiment. It is a figure showing roughly the power plant by a 13th embodiment.
- a velocity collinear chart showing an example of the relationship between the first sun gear rotational speed, the first carrier rotational speed and the first ring gear rotational speed, for the second sun gear rotational speed, the second carrier rotational speed and the second ring gear rotational speed A diagram showing a velocity collinear diagram showing an example of the relationship, (b) an example of the relationship between the rotational speeds of four rotating elements configured by coupling of the first and second planetary gear devices in the power plant shown in FIG. It is a velocity alignment chart shown.
- FIG. 6 is a velocity collinear diagram showing an example of the relationship between the rotational speeds of the five rotating elements.
- A shows an example of the relationship between the rotational speeds of various types of rotary elements in the power plant shown in FIG. 78, (a) in the first shift mode, (b) in the second shift mode It is a velocity alignment chart.
- (A), (b) shows an example of the relationship between the rotational speeds and torques of various rotating elements at the start of the rapid acceleration operation during ENG traveling in the power unit shown in FIG. 78; 7B is a view showing (b) during the second shift mode.
- (A), (b) shows an example of the relationship between the rotational speeds of various types of rotary elements in the power plant, (a) a speed alignment chart showing each during the first shift mode and (b) during the second shift mode It is.
- (A) and (b) show an example of the relationship between the rotational speeds and torques of various types of rotary elements in the power plant when the speed of the driven part is to be rapidly increased, and (a) in the first shift mode (B) It is a figure shown about during 2nd speed change mode, respectively.
- FIG. 90 is a diagram showing an example of a relationship between rotational speeds and torques of various rotating elements in the power plant shown in FIG. 87 at the start of ENG start during EV traveling.
- FIG. 90 is a diagram for describing a speed change operation by the rotating machine or the second rotating machine in the power plant shown in FIG. 87.
- FIG. 90 is a diagram showing an example of a relationship between rotational speeds and torques of various types of rotary elements in the power plant shown in FIG.
- a velocity collinear chart showing an example of the relationship between the first sun gear rotational speed, the first carrier rotational speed and the first ring gear rotational speed, for the second sun gear rotational speed, the second carrier rotational speed and the second ring gear rotational speed A diagram showing a velocity collinear diagram showing an example of the relationship, (b) an example of the relationship between the rotational speeds of four rotating elements configured by the connection of the first and second planetary gear devices in the power plant shown in FIG. It is a velocity alignment chart shown.
- FIG. 6 is a velocity collinear diagram showing an example of the relationship between the rotational speeds of the five rotating elements.
- (A) shows an example of the relationship between the rotational speeds of various types of rotary elements in the power plant shown in FIG. 95, (a) in the first shift mode, (b) in the second shift mode It is a velocity alignment chart.
- (A) and (b) show an example of the relationship between the rotational speeds and torques of various rotating elements at the start of ENG start during EV traveling in the power unit shown in FIG. (B) It is a figure shown about during 2nd speed change mode, respectively.
- (A), (b) shows an example of the relationship between the rotational speeds of various types of rotary elements in the power plant, (a) a speed alignment chart showing each during the first shift mode and (b) during the second shift mode It is.
- (A) and (b) show an example of the relationship between the rotational speeds and torques of various types of rotary elements in the power plant when starting the heat engine during driving of the driven parts by the first and second rotary machines, And (a) shows during the first shift mode and (b) shows during the second shift mode.
- FIG. 24 schematically shows a power plant according to a twenty-second embodiment. It is a figure which shows schematic structure of the power plant which concerns on 23rd Embodiment, and a hybrid vehicle to which this is applied. It is a figure which shows schematic structure of the power plant of 23rd Embodiment. It is sectional drawing which shows typically schematic structure of a 1st rotary machine and a 2nd rotary machine.
- FIG. 107 is a diagram schematically showing, in a straight line, an annular cross section broken along the circumferential direction at the position of the AA line in FIG. 106.
- FIG. 2 is a diagram showing an equivalent circuit corresponding to the first rotating machine 10.
- FIG. 5 is a velocity collinear diagram showing an example of the relationship between the magnetic field electrical angular velocity ⁇ mf, the first rotor electrical angular velocity ⁇ e1, and the second rotor electrical angular velocity ⁇ e2 in the first rotating machine 10.
- FIG. 16 is a velocity collinear diagram showing an example of the relationship between the magnetic field electrical angular velocity ⁇ MFR, the first rotor electrical angular velocity ⁇ ER1, and the second rotor electrical angular velocity ⁇ ER2.
- (A)-(c) is a figure for demonstrating the operation
- FIG. 110 is a diagram for describing a positional relationship between stator magnetic poles and a soft magnetic core when the stator magnetic poles rotate by an electrical angle 2 ⁇ from the state shown in FIG. 110.
- (A)-(c) is a figure for demonstrating the operation
- FIG. 115 (a)-(c).
- (A), (b) is a figure for demonstrating the operation
- It is a block diagram which shows the driving force control in the power plant 1 of FIG.
- It is a velocity collinear diagram in the power unit 1 which has the structure of 1 collinear 3 elements.
- It is a velocity collinear chart showing an example of a relation of three electric angular velocities and three torques in case pole number ratio alpha in the 1st rotation machine of a power plant of a 23rd embodiment is made into an arbitrary value.
- FIG. 1 It is a figure which shows another example at the time of providing a transmission in the power plant of 23rd Embodiment. It is a figure which shows the range of battery SOC by which charging / discharging is repeated.
- (A), (b) shows the speed alignment chart when (a) the battery SOC is less than the first threshold when the operation mode of the operating device 1 is "in engine operation", (b) the battery SOC is The velocity alignment chart at the time of more than a 1st threshold is shown.
- (A), (b) shows the speed alignment chart when (a) the battery SOC is higher than the second threshold when the operation mode of the operation apparatus 1 is "EV travel", (b) (b) the battery SOC is The velocity alignment chart at the time of 2 threshold values or less is shown.
- (A), (b) shows the speed alignment chart when (a) the battery SOC is less than the first threshold when the operation mode of the operating device 1 is "ENG backward start", (b) the battery SOC is The velocity alignment chart at the time of more than a 1st threshold is shown. It is a figure showing the schematic structure of the power plant concerning a 24th embodiment. It is a figure which shows an example at the time of providing a transmission in the power plant of 24th Embodiment. It is a figure showing the schematic structure of the power plant concerning a 25th embodiment. It is a figure showing the schematic structure of the power plant concerning a 26th embodiment.
- First Embodiment 1 and 2 schematically show a power plant 1 according to a first embodiment.
- the power plant 1 is for driving the left and right drive wheels DW, DW (driven parts) of a vehicle (not shown), and as shown in FIG. Engine), the first rotary machine 21 and the second rotary machine 31, the differential gear mechanism 9 coupled to the drive wheels DW, DW via the drive shafts 10, 10, and the first power drive unit (hereinafter "the first PDU” And a second power drive unit (hereinafter referred to as “second PDU”) 42 and a bidirectional buck-boost converter (hereinafter referred to as “VCU”) 44.
- the power plant 1 includes an ECU 2 for controlling the operation of the internal combustion engine 3 and the first and second rotating machines 21 and 31.
- the first and second rotating machines 21 and 31 also function as a continuously variable transmission as described later.
- An internal combustion engine (hereinafter referred to as “engine”) 3 is, for example, a gasoline engine, and a first rotation shaft 4 rotatably supported by bearings 4 a is mounted on a crankshaft 3 a of the engine 3 via a flywheel 5. It is directly connected. Further, the connecting shaft 6 and the second rotating shaft 7 are concentrically arranged with respect to the first rotating shaft 4 and the idler shaft 8 is arranged in parallel with each other. The connecting shaft 6, the second rotating shaft 7 and the idler shaft 8 are rotatably supported by bearings 6a, 7a and 8a, 8a, respectively.
- the connecting shaft 6 is formed hollow, and the above-mentioned first rotating shaft 4 is rotatably fitted inside thereof.
- the idler shaft 8 is integrally provided with a first gear 8b and a second gear 8c.
- the former 8b is a gear 7b integral with the second rotary shaft 7, and the latter 8c is a gear 9a of the differential gear mechanism 9. , Each meshing.
- the second rotation shaft 7 is connected to the drive wheels DW and DW via the idler shaft 8 and the differential gear mechanism 9.
- the circumferential direction, the axial direction and the radial direction of the first rotation shaft 4, the connection shaft 6 and the second rotation shaft 7 will be simply referred to as “circumferential direction”, “axial direction” and “radial direction”.
- the first rotating machine 21 includes a stator 23, an A1 rotor 24 provided so as to face the stator 23, and a space between the two 23 and 24.
- An A2 rotor 25 is provided.
- the stator 23, the A2 rotor 25 and the A1 rotor 24 are arranged in this order from the outer side in the radial direction and arranged concentrically.
- some elements such as the first rotation axis 4 are depicted in a skeleton diagram for the convenience of illustration.
- the above-mentioned stator 23 generates the first rotating magnetic field, and as shown in FIGS. 3 and 4, the iron core 23a and U-phase, V-phase and W-phase coils provided on the iron core 23a. 23c, 23d, and 23e. In FIG. 3, only the U-phase coil 23 c is shown for convenience.
- the iron core 23a has a cylindrical shape in which a plurality of steel plates are stacked, extends in the axial direction, and is fixed to the immovable case CA. Further, twelve slots 23b are formed on the inner peripheral surface of the iron core 23a, and the slots 23b extend in the axial direction and are arranged at equal intervals in the circumferential direction.
- the U-phase to W-phase coils 23c to 23e are wound in the slots 23b by distributed winding (wave winding), and are connected to the battery 43 via the first PDU 41 and the VCU 44 described above.
- the first PDU 41 is formed of an electric circuit including an inverter or the like, and is connected to the second PDU 42 and the ECU 2 (see FIG. 1).
- the iron core is supplied with electric power from the battery 43 and current flows to the U-phase to W-phase coils 23c to 23e, or when power generation is performed as described later.
- Four magnetic poles are generated at equal intervals in the circumferential direction at the end on the A1 rotor 24 side of 23a (see FIGS. 7A to 7C), and the first rotating magnetic field by these magnetic poles is circumferentially Moving.
- the magnetic pole generated on the iron core 23 a is referred to as “first stator magnetic pole”.
- the polarities of the two first stator magnetic poles adjacent in the circumferential direction are different from each other. 7 (a) to 7 (c) and other drawings described later, (N) and (S) the first stator magnetic pole on the iron core 23a and the coils 23c to 23e of U phase to W phase. Indicated in.
- the A1 rotor 24 has a first magnetic pole row consisting of eight permanent magnets 24a.
- the permanent magnets 24 a are arranged at equal intervals in the circumferential direction, and the first magnetic pole row faces the iron core 23 a of the stator 23.
- Each permanent magnet 24 a extends in the axial direction, and the length in the axial direction is set to the same as that of the iron core 23 a of the stator 23.
- the permanent magnet 24a is attached to the outer peripheral surface of the ring-shaped fixed portion 24b.
- the fixing portion 24 b is formed of a soft magnetic material, for example, a lamination of iron or a plurality of steel plates, and the inner peripheral surface thereof is attached to the outer peripheral surface of the donut plate-like flange.
- the flange is integrally provided on the connecting shaft 6 described above.
- the A1 rotor 24 including the permanent magnet 24 a is rotatable integrally with the connecting shaft 6.
- each permanent magnet 24a since the permanent magnets 24a are attached to the outer peripheral surface of the fixed portion 24b made of the soft magnetic material as described above, each permanent magnet 24a has (N) or (N) One pole of S) appears.
- the magnetic poles of the permanent magnet 24 a are denoted by (N) and (S). Further, the polarities of the two permanent magnets 24a adjacent in the circumferential direction are different from each other.
- the A2 rotor 25 has a first soft magnetic material array consisting of six cores 25a. These cores 25a are arranged at equal intervals in the circumferential direction, and this first soft magnetic material row has a predetermined interval between the iron core 23a of the stator 23 and the first magnetic pole row of the A1 rotor 24, respectively. It is placed apart. Each core 25a is formed by laminating a soft magnetic material, for example, a plurality of steel plates, and extends in the axial direction. Moreover, the length of the axial direction of the core 25a is set to the same as that of the iron core 23a of the stator 23 like the permanent magnet 24a.
- the core 25a is attached to the outer end of the disk-shaped flange 25b via a cylindrical connecting portion 25c which slightly extends in the axial direction.
- the flange 25 b is integrally provided on the first rotation shaft 4 described above.
- the A2 rotor 25 including the core 25 a is rotatable integrally with the first rotation shaft 4.
- the connecting portion 25c and the flange 25b are omitted for the sake of convenience.
- first stator 23 is referred to as a "first stator”
- A1 rotor 24 is referred to as a "first rotor”
- the A2 rotor 25 is referred to as a “second rotor”.
- first driving equivalent torque Te1 a torque equivalent to the electric power supplied to the first stator and the electric angular velocity ⁇ mf of the first rotating magnetic field.
- first rotor transmission torque T1 first driving equivalent torque Te1 and the torques transmitted to the first and second rotors
- second rotor transmission torque T2 respectively
- the first stator has three-phase coils of U-phase, V-phase and W-phase (B) Two first stator poles and four first poles, that is, the N pole and S of the first stator pole The number of pole pairs is 1 and the number of pole pairs is 1.
- the first soft magnetic material is a first core, a second core and a third pole.
- the “pole pair” used in the present specification refers to one pair of an N pole and an S pole.
- the magnetic flux ⁇ k1 of the first magnetic pole passing through the first core of the first soft magnetic body is expressed by the following equation (1).
- ⁇ f is the maximum value of the magnetic flux of the first magnetic pole
- ⁇ 1 and ⁇ 2 are the rotational angular position of the first magnetic pole relative to the U-phase coil and the rotational angular position of the first core.
- the magnetic flux ⁇ u1 of the first magnetic pole passing through the U-phase coil via the first core is expressed by the following equation (2) obtained by multiplying the equation (1) by cos ⁇ 2.
- the magnetic flux ⁇ u2 of the first magnetic pole passing through the U-phase coil via the second core is expressed by the following equation (4) obtained by multiplying the equation (3) by cos ( ⁇ 2 + 2 ⁇ / 3) .
- the magnetic flux ⁇ u3 of the first magnetic pole passing through the U-phase coil through the third core of the first soft magnetic body is expressed by the following equation (5).
- the magnetic flux ⁇ u of the first magnetic pole passing through the U-phase coil through the first soft magnetic material is represented by the above formulas (2), (4) and (5).
- the resultant magnetic fluxes 1u1 to ⁇ u3 are added together, which is expressed by the following equation (6).
- the magnetic flux ⁇ u of the first magnetic pole passing through the U-phase coil via the first soft magnetic body is expressed by the following equation (7).
- a, b and c are the number of pole pairs of the first magnetic pole, the number of first soft magnetic bodies, and the number of pole pairs of the first stator pole.
- equation (7) can be modified based on the formula of the sum and product of trigonometric functions to obtain the following equation (8).
- the second term of the right side of the equation (10) becomes a value 0 as apparent from the following equation (11) when it is arranged based on the sum of series and the Euler's formula, with ac ⁇ 0 as a condition.
- the third term of the right side of the above equation (10) is also a value 0 as apparent from the following equation (12) when it is arranged based on the sum of series and Euler's formula, with ac ⁇ 0 as a condition. become.
- the electrical angle position of the first core with respect to the U-phase coil Represents Further, as apparent from the fact that ⁇ e1 multiplies the rotational angle position ⁇ 1 of the first magnetic pole with respect to the U-phase coil by the pole count c of the first stator magnetic pole, the electrical angular position of the first magnetic pole with respect to the U-phase coil is Represent.
- the magnetic flux ⁇ v of the first magnetic pole passing through the V phase coil through the first soft magnetic material is because the electrical angle position of the V phase coil is advanced by an electrical angle 2 ⁇ / 3 with respect to the U phase coil It is represented by following Formula (16). Further, since the electric angle position of the W phase coil is delayed by the electric angle 2 ⁇ / 3 with respect to the U phase coil, the magnetic flux ⁇ w of the first magnetic pole passing through the W phase coil via the first soft magnetic body is It is expressed by the following equation (17).
- ⁇ e1 is a time differential value of ⁇ e1, that is, a value obtained by converting the angular velocity of the first rotor with respect to the first stator to an electrical angular velocity (hereinafter referred to as “first rotor electrical angular velocity”)
- ⁇ e2 is a time of ⁇ e2 It is a differential value, that is, a value obtained by converting the angular velocity of the second rotor with respect to the first stator into an electrical angular velocity (hereinafter referred to as “second rotor electrical angular velocity”).
- the magnetic flux of the first magnetic pole that passes directly through the U-phase to W-phase coils without passing through the first soft magnetic material is extremely small, and its effect can be ignored.
- the time derivative values d ⁇ u / dt to d ⁇ w / dt of the magnetic flux ⁇ u to ⁇ w of the first magnetic pole passing through the U-phase to W-phase coils through the first soft magnetic body (Equations (18) to (20) Shows the counter electromotive voltage (induced electromotive voltage) generated in the U-phase to W-phase coils as the first magnetic pole and the first soft magnetic material rotate with respect to the first stator row.
- I is the amplitude (maximum value) of the current flowing through the U-phase to W-phase coils.
- the electrical angle position ⁇ mf of the vector of the first rotating magnetic field with respect to the U phase coil is expressed by the following equation (24), and the first rotating magnetic field for the U phase coil
- the electric angular velocity (hereinafter referred to as “magnetic field electric angular velocity”) ⁇ mf of is expressed by the following equation (25).
- the mechanical output (power) W output to the first and second rotors by the currents Iu to Iw flowing respectively through the U-phase to W-phase coils has the following formula (26) when the reluctance component is removed. Is represented by
- the first stator magnetic pole It represents that the ratio of the number, the number of first magnetic poles, and the number of first soft magnetic bodies is 1: m: (1 + m) / 2. Further, that the condition of a ⁇ c ⁇ 0 holds indicates that m ⁇ 1.0.
- the ratio of the number of first stator magnetic poles, the number of first magnetic poles, and the number of first soft magnetic bodies is 1: m: (1 + m) / 2 (m ⁇ 1. Since it is set to 0), it is understood that the relationship between the electric angular velocity shown in equation (25) and the torque shown in equation (32) holds, and the first rotating machine 21 operates properly.
- ⁇ a / c, that is, the ratio of the pole pair number of the first magnetic pole to the pole pair number of the first stator pole (hereinafter referred to as “first pole number ratio”
- first pole number ratio the ratio of the pole pair number of the first magnetic pole to the pole pair number of the first stator pole
- the first rotating machine 21 when the first rotating magnetic field is generated by the power supply to the first stator, the magnetic lines of force connecting the first magnetic pole, the first soft magnetic body, and the first stator magnetic pole described above.
- the electric power supplied to the first stator is converted into motive power by the action of the magnetic force due to the magnetic lines of force, and the motive power is output from the first rotor and the second rotor, and the electric angular velocity or electric power as described above
- the relationship of torque is established. Therefore, when at least one of the first and second rotors is rotated with respect to the first stator by inputting power to at least one of the first and second rotors while power is not supplied to the first stator.
- the first stator power generation is performed and a first rotating magnetic field is generated, and also in this case, magnetic lines of force connecting the first magnetic pole, the first soft magnetic body, and the first stator magnetic pole are generated.
- the relationship between the electrical angular velocity shown in the above-mentioned equation (25) and the relationship between the torque shown in the equation (32) are established by the action of the magnetic force due to.
- the first rotating machine 21 of the present embodiment has the same function as a device combining a planetary gear device and a general one-rotor type rotating machine.
- first magnetic poles there are four first stator magnetic poles, eight magnetic poles of the permanent magnet 24a (hereinafter referred to as "first magnetic poles"), and six cores 25a. That is, the ratio of the number of first stator magnetic poles to the number of first magnetic poles and the number of cores 25a is set to 1: 2.0: (1 + 2.0) / 2, and the number of pole pairs of the first stator magnetic pole is The ratio of the number of pole pairs of the first magnetic pole to the pole number (hereinafter referred to as the “first number of pole pairs ratio ⁇ ”) is set to the value 2.0.
- ⁇ F is the maximum value of the magnetic flux of the first magnetic pole.
- ⁇ ER1 is an A1 rotor electrical angle
- the rotational angle position of a specific permanent magnet 24a of the A1 rotor 24 with respect to a specific U phase coil 23c (hereinafter referred to as “first reference coil”) is converted into an electrical angle position. It is a value. That is, the A1 rotor electrical angle ⁇ ER1 is a value obtained by multiplying the number of pole pairs of the first stator magnetic pole, that is, the value 2 by the rotation angle position of the specific permanent magnet 24a (hereinafter referred to as “A1 rotor rotation angle ⁇ A1”).
- ⁇ ER2 is an A2 rotor electrical angle, which is a value obtained by converting the rotational angle position of the specific core 25a of the A2 rotor 25 with respect to the first reference coil described above into an electrical angle position. That is, the A2 rotor electrical angle ⁇ ER2 is a value obtained by multiplying the rotation angle position of the specific core 25a (hereinafter referred to as "A2 rotor rotation angle ⁇ A2") by the number of pole pairs (value 2) of the first stator magnetic pole.
- ⁇ ER1 in the above equations (33) to (35) is a time differential value of ⁇ ER1, that is, a value obtained by converting the angular velocity of the A1 rotor 24 with respect to the stator 23 into an electrical angular velocity (hereinafter referred to as “A1 rotor electrical angular velocity”) is there.
- ⁇ ER2 is a time differential value of ⁇ ER2, that is, a value obtained by converting the angular velocity of the A2 rotor 25 with respect to the stator 23 into an electrical angular velocity (hereinafter referred to as “A2 rotor electrical angular velocity”).
- I is the amplitude (maximum value) of the current flowing through the U-phase to W-phase coils 23c to 23e.
- first magnetic field electrical angular position ⁇ MFR is expressed by the following equation (39), and the electrical angular velocity of the first rotating magnetic field relative to the stator 23 (hereinafter referred to as “first magnetic field electrical angular velocity ⁇ MFR”) is represented by the following equation (40) It is represented by).
- the relationship between the first magnetic field electrical angular velocity ⁇ MFR, the A1 rotor electrical angular velocity ⁇ ER1 and the A2 rotor electrical angular velocity ⁇ ER2 is represented as a so-called collinear diagram, for example, as shown in FIG.
- FIGS. 7 (a) to 7 (c) to 9 (a) and 9 (b) the case where power is supplied to the stator 23 in a state where the A1 rotor 24 is held non-rotatable will be described with reference to FIGS. 7 (a) to 7 (c) to 9 (a) and 9 (b).
- FIGS. 7 (a) to 7 (c) to 9 (a) and 9 (b) reference numerals of a plurality of constituent elements are omitted for convenience. The same applies to the other drawings described later. Further, for ease of understanding, the same one first stator magnetic pole and core 25a shown in FIGS. 7 (a) to (c) to FIGS. 9 (a) and 9 (b) are hatched. .
- the center of one core 25a and the center of one permanent magnet 24a coincide with each other in the circumferential direction, and the third core 25a from the core 25a From the state in which the center and the center of the fourth permanent magnet 24a from the permanent magnet 24a coincide with each other in the circumferential direction, the first rotating magnetic field is generated so as to rotate to the left in the figure.
- the positions of every other first stator pole having the same polarity are made to coincide with the center of each permanent magnet 24a whose center coincides with the core 25a, and The polarity of one stator pole is made different from the polarity of the first pole of the permanent magnet 24a.
- the first rotating magnetic field generated by the stator 23 is generated between itself and the A1 rotor 24, and the A2 rotor 25 having the core 25a is disposed between the stator 23 and the A1 rotor 24.
- Each core 25a is magnetized by the stator magnetic pole and the first magnetic pole. Because of this and the gaps between the adjacent cores 25a, lines of magnetic force ML connecting the first stator magnetic pole, the core 25a, and the first magnetic pole are generated.
- FIGS. 7A to 7C to 9A and 9B the magnetic lines of force ML in the iron core 23a and the fixing portion 24b are omitted for the sake of convenience. The same applies to the other drawings described later.
- the magnetic lines of force ML connect the first stator magnetic pole, the core 25a and the first magnetic pole whose circumferential positions coincide with each other, and these first stator magnetic poles, the core 25a and The first stator magnetic pole, the core 25a, and the first magnetic pole adjacent to both sides in the circumferential direction of the first magnetic pole are generated so as to be connected. Further, in this state, since the magnetic lines of force ML are linear, no magnetic force for circumferentially rotating the core 25a acts on the core 25a.
- the magnetic lines of force ML are bent.
- a magnetic force acts on the core 25a so that ML is linear.
- the magnetic field line ML corresponds to the rotation direction of the first rotating magnetic field (hereinafter referred to as "magnetic field rotation direction") in this core 25a.
- the magnetic force acts to drive the core 25 a in the direction of the magnetic field rotation because the magnetic force in the opposite direction is bent in the opposite direction.
- the core 25a is driven in the direction of magnetic field rotation by the action of the magnetic force due to the magnetic lines of force ML and rotates to the position shown in FIG. 7C, and the A2 rotor 25 provided with the core 25a also rotates in the direction of magnetic field rotation.
- the broken lines in FIGS. 7B and 7C indicate that the magnetic flux amount of the magnetic field lines ML is extremely small, and the magnetic connection between the first stator magnetic pole, the core 25a, and the first magnetic pole is weak. The same applies to the other drawings described later.
- the power supplied to the stator 23 is motive power by the action of the magnetic force due to the magnetic lines of force ML as described above.
- the power is output from the A2 rotor 25.
- FIGS. 11 (a) to (c) to FIGS. 13 (a) and 13 (b) the operation when power is supplied to the stator 23 with the A2 rotor 25 held unrotatable explain.
- FIGS. 11 (a) to (c) to 13 (a) and (b) the same one first stator magnetic pole and permanent magnet 24a are hatched for easy understanding. .
- FIG. 11A as in the case of FIG. 7A described above, the center of a certain core 25a and the center of a certain permanent magnet 24a coincide with each other in the circumferential direction.
- the first rotating magnetic field is It generates to rotate in the direction.
- the positions of every other first stator pole having the same polarity are made to coincide with the center of each permanent magnet 24a whose center coincides with the core 25a, and The polarity of one stator pole is made different from the polarity of the first pole of the permanent magnet 24a.
- the magnetic field lines ML connect the first stator magnetic pole, the core 25a, and the first magnetic pole whose circumferential positions coincide with each other, and The first stator magnetic pole, the core 25a and the first magnetic pole are generated so as to connect the first stator magnetic pole, the core 25a and the first magnetic pole adjacent to both sides in the circumferential direction of each of the cores. Further, in this state, since the magnetic force lines ML are linear, no magnetic force for circumferentially rotating the permanent magnet 24 a acts on the permanent magnet 24 a.
- the magnetic lines of force ML are bent.
- a magnetic force acts on the permanent magnet 24 a so that the ML is linear.
- the above magnetic force is a permanent magnet on the extension It acts to position the permanent magnet 24a, that is, to drive the permanent magnet 24a in the direction opposite to the magnetic field rotation direction.
- the permanent magnet 24a By the action of the magnetic force due to such magnetic lines of force ML, the permanent magnet 24a is driven in the direction opposite to the magnetic field rotation direction, rotates to the position shown in FIG. 11C, and the A1 rotor 24 provided with the permanent magnet 24a is also It rotates in the direction opposite to the magnetic field rotation direction.
- the above-described series of operations that is, “the permanent magnet is bent more than the extension of the first stator magnetic pole and the core 25a mutually connected by the magnetic field lines ML, 24a is located at a position where the magnetic field rotates in the direction of the magnetic field rotation ⁇ A magnetic force acts on the permanent magnet 24 a so that the magnetic lines of force ML are linear ⁇ the permanent magnet 24 a and the A1 rotor 24 rotate in the direction opposite to the magnetic field rotation direction
- This operation is repeated as shown in FIGS. 12 (a) to 12 (d) and FIGS. 13 (a) and 13 (b).
- the power supplied to the stator 23 is motive power by the action of the magnetic force by the magnetic lines of force ML as described above.
- the power is output from the A1 rotor 24.
- FIG. 13 (b) shows a state in which the first stator magnetic pole is rotated by an electrical angle 2 ⁇ from the state of FIG. 11 (a), which is apparent from the comparison of FIG. 13 (b) and FIG. 11 (a).
- the permanent magnet 24a is rotating in the reverse direction by a 1/2 rotation angle with respect to the first stator pole.
- FIG. 14 shows an example of the transition of the back electromotive voltages Vcu to Vcw of the U phase to the W phase while the A2 rotor electrical angle ⁇ ER2 changes to a value of 0 to 2 ⁇ .
- the A1 rotor 24 is held non-rotatable, the pole pairs of the first stator magnetic pole and the first magnetic pole have the values 8 and 10, respectively, and from the equation (25), the first magnetic field
- ⁇ MFR 2.25 ⁇ ⁇ ER2.
- counter electromotive voltages Vcu to Vcw of U phase to W phase are generated for approximately 2.25 cycles.
- FIG. 15 shows an example of the transition of the rotor transmission torques TRA1 and TRA2 of the first driving equivalent torques TSE1, A1 and A2.
- the number of pole pairs of the first stator magnetic pole and the first magnetic pole is 8 and 10, respectively, and from the equation (32), the rotor transmission torques TRA1, TRA1 of the first driving equivalent torques TSE1, A1 and A2.
- the first driving equivalent torque TSE1 is approximately ⁇ TREF
- the A1 rotor transmission torque TRA1 is approximately 1.25 ⁇ ( ⁇ TREF)
- the A2 rotor transmission torque TRA2 is approximately 2.25. ⁇ It is TREF.
- This TREF is a predetermined torque value (for example, 200 Nm).
- FIG. 16 and 17 set the number of first stator magnetic poles, cores 25a and permanent magnets 24a in the same manner as in FIGS. 14 and 15, and instead of A1 rotor 24, keep A2 rotor 25 unrotatable.
- FIG. 16 shows an example of the transition of the U-phase to W-phase counter electromotive voltages Vcu to Vcw while the A1 rotor electrical angle ⁇ ER1 changes to a value of 0 to 2 ⁇ .
- the A2 rotor 25 is held non-rotatable, the number of pole pairs of the first stator magnetic pole and the first magnetic pole is 8 and 10 respectively, and from the equation (25), the magnetic field electrical angular velocity
- ⁇ MFR ⁇ 1.25 ⁇ ⁇ ER1.
- FIG. 17 shows an example of the transition of the rotor transmission torques TRA1 and TRA2 of the first driving equivalent torques TSE1, A1 and A2.
- the first driving equivalent torque TSE1 is approximately TREF
- the A1 rotor transmission torque TRA1 is approximately 1.25 ⁇ TREF
- the A2 rotor transmission torque TRA2 is approximately ⁇ 2.25 ⁇ TREF. It has become.
- the magnetic lines of magnetic force ML connecting the first magnetic pole, the core 25 a and the first stator magnetic pole are generated.
- the power supplied to the stator 23 is converted into motive power by the action of the magnetic force due to the magnetic force lines ML, and the motive power is output from the A1 rotor 24 or the A2 rotor 25.
- the relationship shown in the equation (40) is established between the rotor electrical angular velocities ⁇ ER1, ⁇ ER2 of the magnetic field electrical angular velocity ⁇ MFR, A1 and A2, and the rotor transmission torque of the first equivalent torque TSE1, A1 and A2 for driving.
- the relationship shown in the equation (41) is established between TRA1 and TRA2.
- stator 23 when power is supplied to at least one of A1 and A2 rotors 34 and 35 while power is not supplied to stator 23, rotation of at least one of them relative to stator 23 causes stator 23 to rotate. Power generation is performed, and a first rotating magnetic field is generated. Also in this case, a magnetic line of magnetic force ML is generated to connect the first magnetic pole, the core 25a, and the first stator magnetic pole, and the magnetic force by the magnetic line of magnetic force acts.
- the relationship between the electrical angular velocity shown in equation (40) and the relationship between torques shown in equation (41) is established.
- first magnetic field rotational speed VMF1 the rotational speed of the first rotating magnetic field
- the following equation (43) is established between the A1 rotor rotational speed VRA1 and the A2 rotor rotational speed VRA2.
- the first rotating machine 21 has the same function as a device combining a planetary gear device and a general one-rotor type rotating machine.
- the second rotary machine 31 is configured in the same manner as the first rotary machine 21.
- the configuration and operation of the second rotary machine 31 will be briefly described below.
- the second rotating machine 31 includes a stator 33, a B1 rotor 34 provided to face the stator 33, and a B2 rotor 35 provided between the two.
- the stator 33, the B2 rotor 35, and the B1 rotor 34 are arranged radially in this order from the outside in this order and arranged concentrically.
- FIG. 18, as in FIG. 3, some elements such as the first rotation shaft 4 are drawn in a skeleton diagram for convenience of illustration.
- the above-mentioned stator 33 generates a second rotating magnetic field, and as shown in FIG. 18, it has an iron core 33a and U-phase, V-phase and W-phase coils 33b provided on the iron core 33a. doing.
- the iron core 33a has a cylindrical shape in which a plurality of steel plates are stacked, extends in the axial direction, and is fixed to the case CA.
- 12 slots are formed in the inner peripheral surface of the iron core 33a, and these slots are located in a line at equal intervals in the circumferential direction.
- the U-phase to W-phase coils 33b are wound in slots in distributed winding (wave winding), and are connected to the battery 43 via the second PDU 42 and the VCU 44 described above.
- the second PDU 42 is configured by an electric circuit including an inverter or the like, and is connected to the first PDU 41 and the ECU 2 (see FIG. 1).
- stator 33 In the stator 33 configured as described above, when power is supplied from the battery 43 and current flows through the U-phase to W-phase coils 33b, or when power generation is performed as described later, Four magnetic poles are generated at equal intervals in the circumferential direction at the end on the B1 rotor 34 side, and the second rotating magnetic field by these magnetic poles moves in the circumferential direction.
- the magnetic pole generated on the iron core 33a is referred to as "second stator magnetic pole”. Further, the polarities of the two second stator magnetic poles adjacent in the circumferential direction are different from each other.
- the B1 rotor 34 has a second magnetic pole row consisting of eight permanent magnets 34a (only two are shown).
- the permanent magnets 34 a are arranged at equal intervals in the circumferential direction, and the second magnetic pole row faces the iron core 33 a of the stator 33.
- Each permanent magnet 34 a extends in the axial direction, and the length in the axial direction is set to the same as that of the iron core 33 a of the stator 33.
- the permanent magnet 34a is attached to the outer peripheral surface of the ring-shaped fixed portion 34b.
- the fixing portion 34b is formed of a soft magnetic material, for example, a laminated member of iron or a plurality of steel plates, and the inner peripheral surface thereof is attached to the outer peripheral surface of the disk-shaped flange 34c.
- the flange 34 c is provided integrally with the first rotation shaft 4 described above.
- the B1 rotor 34 including the permanent magnet 34 a is rotatable integrally with the first rotation shaft 4.
- each permanent magnet 34a since the permanent magnet 34a is attached to the outer peripheral surface of the fixing portion 34b made of the soft magnetic material as described above, each permanent magnet 34a has the (N) or (N) One pole of S) appears. Further, the polarities of the two permanent magnets 34a adjacent in the circumferential direction are different from each other.
- the B2 rotor 35 has a second soft magnetic material row consisting of six cores 35a (only two are shown). These cores 35 a are arranged at equal intervals in the circumferential direction, and the second soft magnetic material rows are separated between the iron core 33 a of the stator 33 and the magnetic pole rows of the B1 rotor 34 at predetermined intervals, respectively. It is arranged.
- Each core 35a is formed by laminating a soft magnetic material, for example, a plurality of steel plates, and extends in the axial direction. Moreover, the length of the axial direction of the core 35a is set to the same as that of the iron core 33a of the stator 33 similarly to the permanent magnet 34a.
- the core 35a is attached to the outer end portions of the disk-shaped flanges 35b and 35c via cylindrical connecting portions 35d and 35e extending slightly in the axial direction, respectively.
- the flanges 35 b and 35 c are integrally provided on the connecting shaft 6 and the second rotating shaft 7 described above.
- the B2 rotor 35 including the core 35 a is rotatable integrally with the connecting shaft 6 and the second rotation shaft 7.
- the second rotating machine 31 since the second rotating machine 31 is configured in the same manner as the first rotating machine 21, the second rotating machine 31 has the same function as an apparatus combining a planetary gear device and a general one-rotor type rotating machine. That is, during power supply to stator 33 and during power generation, the relationship shown in equation (25) holds between the electrical angular velocity of the second rotating magnetic field and the electrical angular velocity of B1 rotor 34 and B2 rotor 35.
- the ratio of the number of second stator magnetic poles to the number of second magnetic poles to the number of cores 35 a is the ratio of the number of first stator magnetic poles of the first rotary machine 21 to the number of first magnetic poles to the number of cores 25 a.
- it is set to 1: 2.0: (1 + 2.0) / 2.
- the ratio of the number of pole pairs of the second magnetic pole to the number of pole pairs of the second stator pole (hereinafter referred to as "the second number of pole pairs ratio ⁇ ") is set to a value 2.0 .
- the second rotating machine 31 since the second rotating machine 31 is configured in the same manner as the first rotating machine 21, it has the same function as the first rotating machine 21.
- the power supplied to stator 33 is converted to power, and the power is output from B1 rotor 34 and B2 rotor 35, and the power input to B1 rotor 34 or B2 rotor 35 is converted to power and is output from stator 33 .
- the second rotating magnetic field the B1 and B2 rotors 34, 35 rotate while maintaining the collinear relationship regarding the rotational speed as shown in the equation (40).
- the rotational speed of the second rotating magnetic field (hereinafter referred to as “second magnetic field rotational speed VMF2”) and the rotational speeds of the rotors 34 and 35 of B1 and B2 (hereinafter referred to as “B1 rotor rotational speed VRB1” “B2
- VMF2 ( ⁇ + 1)
- VRB2- ⁇ ⁇ VRB1 3 ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ (44)
- the torque equivalent to the electric power supplied to the stator 33 and the second rotating magnetic field is "the second driving equivalent torque TSE2”
- the torque is transmitted to the second driving equivalent torque TSE2 and the rotors 34 and 35 of B1 and B2.
- the following equation (45) is established between the set torques (hereinafter referred to as “B1 rotor transmission torque TRB1” and “B2 rotor transmission torque TRB2”, respectively).
- the second rotating machine 31 has the same function as an apparatus combining a planetary gear device and a general one-rotor type rotating machine.
- the ECU 2 controls the VCU 44 that steps up or down the output voltage of the battery 43 or the charging voltage to the battery 43.
- the control of the VCU 44 by the ECU 2 changes the transformation ratio of the VCU 44 and the like.
- the ECU 2 controls the first PDU 41 to thereby supply the electric power supplied to the stator 23 of the first rotating machine 21 and the first magnetic field rotational speed VMF1 of the first rotating magnetic field generated in the stator 23 along with the supply of the electric power. Control.
- the ECU 2 controls the first PDU 41 to control the electric power generated by the stator 23 and the first magnetic field rotational speed VMF1 of the first rotating magnetic field generated by the stator 23 along with the power generation.
- the ECU 2 controls the second PDU 42 so that the electric power supplied to the stator 33 of the second rotating machine 31 and the second magnetic field rotational speed VMF2 of the second rotating magnetic field generated in the stator 33 along with the supply of the electric power. Control. Furthermore, the ECU 2 controls the second PDU 42 to control the electric power generated by the stator 33 and the second magnetic field rotational speed VMF2 of the second rotating magnetic field generated by the stator 33 along with the power generation.
- the crankshaft 3 a of the engine 3, the A2 rotor 25 of the first rotating machine 21, and the B1 rotor 34 of the second rotating machine 31 mechanically communicate with each other via the first rotating shaft 4.
- the A1 rotor 24 of the first rotating machine 21 and the B2 rotor 35 of the second rotating machine 31 are mechanically connected to each other through the connecting shaft 6, and the B2 rotor 35 and the drive wheels DW and DW They are mechanically connected to each other via a two rotation shaft 7 or the like. That is, the A1 rotor 24 and the B2 rotor 35 are mechanically connected to the drive wheels DW and DW.
- stator 23 of the first rotating machine 21 and the stator 33 of the second rotating machine 31 are electrically connected to each other via the first and second PDUs 41 and 42.
- the battery 43 is electrically connected to the stators 23 and 33 via the VCU 44 and the first and second PDUs 41 and 42, respectively.
- FIG. 19 is a conceptual diagram showing an example of a schematic configuration of the power unit 1 and a transmission state of power.
- the first rotating machine 21 is the “first rotating machine”
- the stator 23 is the “first stator”
- the A1 rotor 24 is the “first rotor”
- the A2 rotor 25 is the “second rotor”
- the second The rotating machine 31 is “second rotating machine”
- the stator 33 is “first stator”
- B1 rotor 34 is “third rotor”
- B2 rotor 35 is “fourth rotor”
- engine 3 is "heat engine”
- drive wheel DW and DW are represented as “driven parts”
- the first PDU 41 is represented as “first controller”
- the second PDU 42 is represented as “second controller”.
- the stator 23 is the “first stator”
- the A1 rotor 24 is the “first rotor”
- the second rotor of the first rotating machine and the third rotor of the second rotating machine are mechanically connected to the output of the heat engine, and the first rotor and second rotation of the first rotating machine
- a fourth rotor of the machine is mechanically connected to the driven part.
- a first controller for controlling power generation / supply power of the first stator is electrically connected to the first stator of the first rotating machine
- a second stator of the second rotating machine is
- a second controller for controlling power generation / supply power is electrically connected
- the first and second stators are electrically connected to each other via these first and second controllers.
- mechanical connections are indicated by solid lines, electrical connections by dashed dotted lines, and magnetic connections by broken lines.
- the flow of power and power is indicated by thick lines with arrows.
- the power of the heat engine is transmitted to the driven portion, for example, as follows. That is, when the power of the heat engine is transmitted to the driven part, power is generated in the first stator of the first rotating machine using a part of the power of the heat engine under the control of the first and second controllers. , The generated electric power is supplied to the second stator of the second rotating machine. At the time of power generation by this first rotating machine, as shown in FIG.
- a part of the power of the heat engine is transmitted to the second rotor connected to the output of the heat engine, and further by the magnetic force by the magnetic lines
- a part of the motive power of the heat engine is transmitted also to the first rotor by the magnetic force of the magnetic field lines. That is, the power of the heat engine transmitted to the second rotor is distributed to the first stator and the first rotor. Furthermore, the power distributed to the first rotor is transmitted to the driven part, while the power distributed to the first stator is supplied to the second stator.
- the electric power generated by the first stator as described above is supplied to the second stator, the electric power is converted to a motive power and is transmitted to the fourth rotor by the magnetic force of the magnetic lines of force.
- the remainder of the power of the heat engine is transmitted to the third rotor, and is further transmitted to the fourth rotor by the magnetic force due to the magnetic field lines.
- the power transmitted to the fourth rotor is transmitted to the driven part. As a result of the above, power having a magnitude equal to that of the heat engine is transmitted to the driven part.
- the first and second rotating machines have the same function as a device combining the planetary gear unit and a general one-rotor type rotating machine, so Unlike the power unit of the present invention, a planetary gear set for distributing / combining and transmitting power is not necessary, and accordingly, the power unit can be miniaturized accordingly. Further, unlike the conventional case described above, since the power of the heat engine is transmitted to the driven portion without recirculation as described above, the power passing through the first and second rotating machines can be reduced. Therefore, miniaturization and cost reduction of the first and second rotating machines can be achieved, whereby further miniaturization and cost reduction of the power plant can be achieved. Furthermore, by using the first and second rotating machines having torque capacities commensurate with the reduced power as described above, it is possible to suppress the loss of power and to enhance the driving efficiency of the power plant.
- the power of the heat engine is determined by the second rotor, the magnetic force by the magnetic field lines and the first transmission path consisting of the first rotor, the second rotor, the magnetic force by the magnetic field lines, the first stator, the first controller, the second controller, the second The divided state through a total of three transmission paths of a second transmission path consisting of two stators, a magnetic force by magnetic lines of force, and a fourth rotor, a third transmission path consisting of a third rotor, a magnetic force by magnetic lines of force and a fourth rotor Is transmitted to the driven part.
- the power (energy) passing through the first and second controllers via the second transmission path can be reduced, so that miniaturization and cost reduction of the first and second controllers can be achieved.
- further miniaturization and cost reduction of the power plant can be achieved.
- the motive power of the heat engine is once converted to electric power and then returned to the motive power, and is transmitted to the driven part by a so-called electrical path, while in the first and second transmission paths Since the motive power is transmitted to the driven part by the so-called magnetic path in a non-contact manner by the magnetic force of the magnetic lines without converting the motive power into the electric power, the transmission efficiency is higher than that of the third transmission path.
- the power of the heat engine is controlled by controlling the rotational speeds of the first and second rotating magnetic fields by the first and second controllers, respectively. It is possible to steplessly shift and transmit to the driven part.
- the first rotating machine as is apparent from the functions described above, the first rotating magnetic field and the first and second rotors are used during energy distribution / combining between the first stator and the first and second rotors. The rotation is performed while maintaining the collinear relationship regarding the rotation speed as shown in equation (25).
- the second rotating magnetic field, the third and fourth rotating magnetic fields are divided during energy distribution and synthesis between the second stator, the third and fourth rotors.
- the rotor rotates while maintaining a collinear relationship with respect to the rotational speed as shown in equation (25).
- the second and third rotors when both the second and third rotors are directly connected to the output portion of the heat engine without a transmission mechanism such as a gear, the second and third rotors are The rotational speeds are all equal to the rotational speed of the output portion of the heat engine (hereinafter referred to as "the number of rotations of the heat engine").
- the rotational speeds of the first and fourth rotors are both equal to the speed of the driven part.
- first to fourth rotor rotational speeds VR1, VR2, VR3, VR4 the rotational speeds of the first and second rotational magnetic fields are respectively It is assumed that “first and second magnetic field rotational speeds VMF1 and VMF2”. From the relationship between the rotational speeds of the various rotating elements described above, the relationship between these rotational speeds VR1 to VR4, VMF1, and VMF2 is shown, for example, as a thick solid line in FIG.
- the first magnetic field rotational speed VMF1 is increased relative to the second and third rotor rotational speeds VR2 and VR3, and the second magnetic field rotational speed VMF2 is set.
- the power of the heat engine can be decelerated steplessly and transmitted to the driven part.
- the first magnetic field rotational speed VMF1 is decreased and the second magnetic field rotational speed VMF2 is increased with respect to the second and third rotor rotational speeds VR2 and VR3.
- the power of the heat engine can be steplessly accelerated and transmitted to the driven part.
- the first magnetic field is generated when the rotational speed of the heat engine is higher than the speed of the driven portion (see the two-dot chain line in FIG. 20).
- the rotational speed VMF1 may be higher than the rotational speed of the heat engine and may be excessive. Therefore, by setting the first pole-log ratio ⁇ to a smaller value, as is apparent from the comparison between the velocity alignment chart shown by a broken line in FIG. 20 and the velocity alignment chart shown by a two-dot chain line, The rotation speed VMF1 can be reduced, and thereby, the reduction of the driving efficiency due to the occurrence of the loss due to the increase of the first magnetic field rotation speed VMF1 can be prevented.
- the second magnetic field rotation is performed.
- the velocity VMF2 may be higher than the velocity of the driven part and may be excessive. Therefore, by setting the second pole-log ratio ⁇ to a smaller value, it is apparent from the comparison between the velocity alignment graph shown by the broken line in FIG. 20 and the velocity alignment graph shown by the one-dot chain line.
- the speed VMF2 can be reduced, which can prevent the reduction of the driving efficiency due to the occurrence of the loss due to the increase of the second magnetic field rotational speed VMF2.
- the electric power is generated by the first stator of the first rotating machine, thereby equivalent torque for the second drive of the second rotating machine described above.
- the heat engine is an internal combustion engine.
- FIG. 21 shows the relationship between the torques of various rotating elements in this case, along with the relationship between the rotational speeds.
- TDHE is a torque transmitted to the output of the heat engine (hereinafter referred to as “heat engine transmission torque")
- TOUT is a torque transmitted to the driven part (hereinafter referred to as “driven part transmission torque” ).
- Tg1 is a first power generation equivalent torque
- Te2 is a second drive equivalent torque.
- the second driving equivalent torque Te2 outputs the output of the driven portion and the heat engine with the first power generation equivalent torque Tg1 as a reaction force. Because the torque is transmitted to both of the units, the torque required for the first rotating machine is greater than otherwise. In this case, the torque required for the first rotating machine, that is, the first power generation equivalent torque Tg1 is expressed by the following equation (47).
- Tg1 ⁇ ⁇ ⁇ TOUT + ( ⁇ + 1) TDHE ⁇ / ( ⁇ + 1 + ⁇ ) (47)
- the first power generation equivalent torque Tg1 is smaller for the driven portion transmission torque TOUT and the heat engine transmission torque TDHE of the same magnitude as the first pole pair number ratio ⁇ is larger. Become. Therefore, by setting the first pole pair number ratio ⁇ to a larger value, further downsizing and cost reduction of the first rotating machine can be achieved.
- the speed of the low speed driven part can be rapidly increased by controlling the heat engine and the first and second rotating machines as follows.
- FIG. 22 shows the relationship between the rotational speeds of the various types of rotary elements at the start of the case where the speed of the driven part is thus rapidly increased, as well as the relationship between the torques of the various types of rotary elements.
- THE is the torque of the heat engine
- Tg2 is the equivalent torque for the second power generation described above.
- the rotational speed of the heat engine is increased to a predetermined rotational speed at which the maximum torque can be obtained. As shown in FIG.
- the direction of rotation of the second rotating magnetic field to be determined is the reverse direction. Power is generated in the second stator in order to apply a positive torque to the driven portion from the second stator that generates such a second rotating magnetic field. Further, the electric power generated by the second stator is supplied to the first stator, and the first rotating magnetic field is rotated forward.
- the torque THE of the heat engine, the first driving equivalent torque Te1, and the second power generation equivalent torque Tg2 are all transmitted to the driven part as positive torques, and as a result, the speed of the driven part is rapidly increased. To rise.
- the torque THE of the heat engine and the first driving equivalent torque Te1 are equivalent to the second power generation equivalent. Since the torque Tg2 is transmitted to the driven part as a reaction force, the torque required of the second rotating machine is larger than in the other cases. In this case, the torque required for the second rotating machine, that is, the second power generation equivalent torque Tg2 is expressed by the following equation (48).
- Tg2 ⁇ ⁇ ⁇ THE + (1 + ⁇ ) TOUT ⁇ / ( ⁇ + ⁇ + 1) (48)
- the second power generation equivalent torque Tg2 is smaller with respect to the driven portion transmission torque TOUT and the heat engine torque THE of the same magnitude as the second pole pair ratio ⁇ is larger. Become. Therefore, by setting the second pole pair number ratio ⁇ to a larger value, it is possible to achieve further downsizing and cost reduction of the second rotating machine.
- the crank angle sensor 51 outputs a detection signal representing a crank angle position of the crankshaft 3 a to the ECU 2.
- the ECU 2 calculates the engine speed NE based on the crank angle position.
- a first rotation angle sensor 52 and a second rotation angle sensor 53 are connected to the ECU 2, and these first and second rotation angle sensors 52, 53 are the rotor rotation angles of A1 and A2 described above.
- Each of ⁇ A1 and ⁇ A2 is detected, and the detection signal thereof is output to the ECU 2.
- the ECU 2 calculates the rotor rotational speeds VRA1 and VRA2 of A1 and A2, respectively, based on the detected rotor rotational angles ⁇ A1 and ⁇ A2 of A1 and A2.
- the third rotation angle sensor 54 is a rotation angle position (hereinafter referred to as “B1 rotor rotation”) of a specific permanent magnet 34 a of the B1 rotor 34 with respect to a specific U-phase coil 33 b (hereinafter referred to as “second reference coil”) of the second rotating machine 31. And detects the angle ⁇ B1), and outputs the detection signal to the ECU 2.
- the ECU 2 calculates the B1 rotor rotational speed VRB1 based on the detected B1 rotor rotational angle ⁇ B1.
- the fourth rotation angle sensor 55 detects the rotation angle position (hereinafter referred to as "B2 rotor rotation angle ⁇ B2") of the specific core 35a of the B2 rotor 35 with respect to the second reference coil, and outputs the detection signal to the ECU 2. .
- the ECU 2 calculates the B2 rotor rotational speed VRB2 based on the detected B2 rotor rotational angle ⁇ B2.
- a detection signal representing the current / voltage value input / output to / from the battery 43 is output to the ECU 2.
- the ECU 2 calculates the charge state of the battery 43 based on the detection signal.
- a detection signal representing an accelerator opening degree AP which is a depression amount of the accelerator pedal (not shown) of the vehicle, is output from the accelerator opening sensor 57 to the ECU 2
- a detection signal representing a vehicle speed VP is output from the vehicle speed sensor 58.
- Ru The vehicle speed VP is the rotational speed of the drive wheels DW, DW.
- the ECU 2 is constituted by a microcomputer including an I / O interface, a CPU, a RAM, a ROM and the like, and the engine 3, the first and the second rotations according to detection signals from the various sensors 51 to 58 described above Control the operation of machines 21 and 31.
- the ECU 2 reads data from the memory 45 that stores various maps and the like that are required when performing the control. Further, the ECU 2 derives the temperature of the battery 43 from the signal detected by the battery temperature sensor 62 attached to the exterior of the battery 43 or its periphery.
- FIG. 23 is a block diagram showing driving force control in the power unit 1 according to the first embodiment.
- FIG. 24 is a velocity collinear diagram of the power unit 1 having a one-collinear four-element mechanism.
- the ECU 2 obtains a detection signal representing the accelerator opening degree AP described above and a detection signal representing the vehicle speed VP.
- the ECU 2 uses the driving force map stored in the memory 45 to derive a driving force (hereinafter referred to as “required driving force”) according to the accelerator opening degree AP and the vehicle speed VP.
- the ECU 2 calculates an output according to the required driving force and the vehicle speed VP (hereinafter referred to as "required output").
- the required output is an output required for the vehicle to travel in accordance with the driver's accelerator pedal operation.
- the ECU 2 acquires information on the remaining capacity (SOC: State of Charge) of the battery 43 from the detection signal representing the current / voltage value input / output to / from the battery 43 described above.
- the ECU 2 determines the ratio of the output of the engine 3 to the required output according to the SOC of the battery 43.
- the ECU 2 uses the ENG operation map stored in the memory 45 to derive an optimum operating point according to the output of the engine 3.
- the ENG operation map is a map based on BSFC (Brake Specific Fuel Consumption) that indicates the fuel consumption rate at each operating point according to the relationship between the shaft rotational speed of the engine 3 and the torque and the output.
- BSFC Brain Specific Fuel Consumption
- the ECU 2 derives the shaft rotational speed of the engine 3 at the optimum operating point (hereinafter referred to as “required ENG shaft rotational speed”). Furthermore, the ECU 2 derives the torque of the engine 3 at the optimal operating point (hereinafter referred to as "ENG required torque").
- the ECU 2 controls the engine 3 to output the ENG required torque.
- the ECU 2 detects the shaft rotational speed of the engine 3.
- the shaft rotation speed of the engine 3 detected at this time is referred to as “the actual ENG shaft rotation speed”.
- the ECU 2 calculates the difference ⁇ rpm between the required ENG axis rotational speed and the actual ENG axis rotational speed.
- the ECU 2 controls the output torque of the first rotating machine 21 such that the difference ⁇ rpm approaches zero.
- the control is performed by regenerative power generation by the stator 23 of the first rotating machine 21.
- the A2 rotor 25 of the first rotating machine 21 (MG1) has a torque T12 shown in the alignment chart of FIG. Is added.
- electric energy (regenerative energy) generated by regenerative power generation in the stator 23 of the first rotating machine 21 is sent to the first PDU 41.
- the regenerative energy generated by the stator 23 of the first rotating machine 21 is indicated by a dotted line A.
- the ECU 2 controls the second PDU 42 such that a torque obtained by subtracting the calculated torque T11 from the previously calculated required driving force is applied to the B2 rotor 35 of the second rotating machine 31.
- torque T22 is applied to the B2 rotor 35 of the second rotating machine 31 (MG2).
- the alignment graph of FIG. 24 shows the case where the electrical energy is supplied to the stator 33 of the second rotating machine 31, and the electrical energy at that time is shown by a dotted line B. At this time, when electric energy is supplied to the second rotating machine 31, regenerative energy obtained by regenerative power generation of the first rotating machine 21 may be used.
- the torque T11 is applied to the A1 rotor 24 of the first rotating machine 21 and the torque T22 is applied to the B2 rotor 35 of the second rotating machine 31. Since the A1 rotor 24 of the first rotating machine 21 is connected to the connecting shaft 6, and the B2 rotor 35 of the second rotating machine 31 is connected to the second rotating shaft 7, torque T11 is applied to the drive wheels DW and DW. And the sum of torque T22.
- the ECU 2 Since the B1 rotor 34 of the second rotating machine 31 is connected to the shaft of the engine 3, the actual ENG shaft rotational speed of the engine 3 is affected by the torque T21. However, even if the actual ENG axis rotation speed changes, the ECU 2 controls the output torque of the first rotating machine 21 so that the difference ⁇ rpm approaches zero. Since the torque T12 changes by the control and the torque T11 generated in the A1 rotor 24 of the first rotating machine 21 also changes, the ECU 2 changes the torque T22 applied to the B2 rotor 35 of the second rotating machine 31. At this time, the torque T21 generated by the changed torque T22 also changes.
- the ECU 2 controls the torque generated on the A2 rotor 25 of the first rotating machine 21 so that the engine 3 operates at the optimum operating point, and the required driving force is applied to the drive wheels DW and DW.
- the torque generated in the B2 rotor 35 of the second rotating machine 31 is controlled so as to be transmitted.
- the vehicle speed VP is used when deriving the required driving force and when deriving the required output, but instead of the vehicle speed VP, information on the number of revolutions of the axle may be used.
- the operation modes of the power unit 1 include EV creep, EV start, ENG start during EV travel, ENG travel, deceleration regeneration, stop ENG start, ENG creep, ENG start, EV reverse start, and ENG reverse start.
- EV creep a diagram showing the transmission state of torque as shown in FIG. 25 and the like, and a velocity collinear diagram showing the relationship between rotational speeds of various rotating elements as shown in FIGS. While, EV creep will be described in order. Before describing this operation mode, these velocity alignment charts will be described.
- the engine rotational speed NE, the A2 rotor rotational speed VRA2 and the B1 rotor rotational speed VRB1 are equal to one another. Further, assuming that A1 rotor rotational speed VRA1 and B2 rotor rotational speed VRB2 are equal to each other, and assuming that there is no shift by differential gear mechanism 9 etc., vehicle speed VP is equal to A1 rotor rotational speed VRA1 and B2 rotor rotational speed VRB2. .
- the engine rotational speed NE the vehicle speed VP, the first magnetic field rotational speed VMF1, the A1 rotor rotational speed VRA1, the A2 rotor rotational speed VRA2, the second magnetic field rotational speed VMF2,
- the relationship between the B1 rotor rotational speed VRB1 and the B2 rotor rotational speed VRB2 is shown by a velocity alignment chart such as in FIGS. 26 (a) and 26 (b).
- the first and second pole-log ratios ⁇ and ⁇ are both 2.0 as described above.
- This EV creep is an operation mode in which the creep operation of the vehicle is performed using the first and second rotating machines 21 and 31 in a state where the engine 3 is stopped. Specifically, electric power is supplied from the battery 43 to the stator 33 of the second rotating machine 31, and the second rotating magnetic field generated by the stator 33 is rotated in the forward direction. Further, the power generated by the stator 23 of the first rotating machine 21 is generated using power transmitted to the A1 rotor 24 of the first rotating machine 21 as described later, and the generated power is further supplied to the stator 33.
- FIG. 25 shows a state of transmission of torque during the above-described EV creep.
- 26 (a) shows an example of the respective velocity alignment charts of the first and second rotating machines 21 and 31 during this EV creep
- FIG. 26 (b) shows FIG. 26 (a).
- combined two speed alignment charts is shown, respectively.
- thick broken or solid lines with arrows indicate the flow of torque.
- the solid arrows indicate the torque acting in the forward direction
- the hollow arrows indicate the torque acting in the reverse direction.
- torque is actually transmitted in the form of electrical energy, but in FIG.
- the second driving equivalent torque TSE2 from the stator 33 causes the B2 rotor 35 to rotate in the forward direction. And, as indicated by arrow A, act to reverse the B1 rotor 34. Further, part of the torque transmitted to the B2 rotor 35 is transmitted to the drive wheels DW and DW via the second rotation shaft 7 and the differential gear mechanism 9 and the like, whereby the drive wheels DW and DW perform forward rotation. Do.
- the rest of the torque transmitted to the B2 rotor 35 is transmitted to the A1 rotor 24 through the connecting shaft 6, and thereafter, the stator 23 is generated according to the power generation in the stator 23 of the first rotating machine 21.
- the first rotating magnetic field generated along with the power generation in the stator 23 is reversed.
- the first power generation equivalent torque TGE1 generated along with the power generation by the stator 23 acts to cause the A2 rotor 25 to rotate in the forward direction.
- the torque transmitted to the A1 rotor 24 is further transmitted to the A2 rotor 25 (shown by an arrow C) so as to balance the first electric power generation equivalent torque TGE1, and acts to rotate the A2 rotor 25 forward.
- the power supplied to the stator 33 and the stator 23 make it possible that the torque for reversing the B1 rotor 34 indicated by the arrow A described above and the torque for rotating the A2 rotor 25 indicated by the arrows B and C balance with each other.
- the A2 rotor 25, the B1 rotor 34 and the crankshaft 3a connected to each other are held stationary.
- the rotor rotational speeds VRA2 and VRB1 of A2 and B1 have the value 0, and the engine speed NE also has the value 0.
- the electric power supplied to the stator 33 of the second rotating machine 31, the electric power generated by the stator 23 of the first rotating machine 21, and the first and second magnetic field rotational speeds VMF1 and VMF2 are respectively
- the rotor rotational speeds VRA1 and VRB2 of A1 and B2 are controlled to be very small (FIG. 26 (a), (B)).
- the creep operation with a very small vehicle speed VP is performed.
- the creep operation can be performed by the driving force of the first and second rotating machines 21 and 31.
- This EV start is an operation mode in which the vehicle is started and traveled using the first and second rotating machines 21 and 31 in a state where the engine 3 is stopped during the above-described EV creep.
- the electric power supplied to the stator 33 of the second rotating machine 31 and the electric power generated by the stator 23 of the first rotating machine 21 are both increased.
- the rotor rotational speeds VRA2 and VRB1 of A2 and B1 that is, engine rotational speed NE, at 0, reverse rotation is performed during EV creep.
- the first magnetic field rotational speed VMF1 of the first rotating magnetic field and the second magnetic field rotational speed VMF2 of the second rotating magnetic field that has been forward rotated are increased in the same rotational direction as before.
- the rotor rotational speeds VRA1 and VRB2 of A1 and B2 ie, the vehicle speed VP rises from the EV creep state shown by the broken line in FIG. Will be launched.
- the state of transmission of torque during the EV start is the same as the state of transmission of torque during the EV creep shown in FIG. 25, as shown in FIG.
- This ENG start during EV travel is an operation mode for starting the engine 3 while the vehicle is traveling with the EV start described above.
- the rotor rotational speeds VRA1 and VRB2 of A1 and B2 ie, the vehicle speed VP at the values at that time
- the first magnetic field of the first rotating magnetic field reverses at EV start as described above
- the rotational speed VMF1 is controlled to a value 0, and the second magnetic field rotational speed VMF2 of the second rotating magnetic field, which has been normally rotated, is controlled to be reduced.
- the first magnetic field rotational speed VMF1 becomes a value 0, in addition to the stator 33 of the second rotating machine 31, power is supplied from the battery 43 to the stator 23 of the first rotating machine 21.
- the first magnetic field rotational speed VMF1 is increased while rotating the generated first rotating magnetic field forward.
- FIG. 29 shows a state of transmission of torque in the state where electric power is supplied to both the stators 23 and 33 as described above at the time of ENG start during EV traveling.
- the second driving equivalent torque TSE2 is transmitted to the B2 rotor 35.
- the torque transmitted to the B1 rotor 34 as described later is transmitted to the B2 rotor 35. That is, the second driving equivalent torque TSE2 and the B1 rotor transmission torque TRB1 transmitted to the B1 rotor 34 are synthesized and transmitted to the B2 rotor 35.
- part of the torque transmitted to the B2 rotor 35 is transmitted to the A1 rotor 24 through the connecting shaft 6, and the remaining part is transmitted to the drive wheels DW and DW through the second rotation shaft 7 or the like.
- the electric power is supplied from the battery 43 to the stator 23 from the function of the first rotating machine 21 described above, so that the first equivalent torque TSE1 for driving is A2.
- the torque transmitted to the A1 rotor 24 as described above is transmitted to the A2 rotor 25. That is, the first driving equivalent torque TSE1 and the A1 rotor transmission torque TRA1 transmitted to the A1 rotor 24 are synthesized and transmitted to the A2 rotor 25.
- crankshaft 3a rotates forward. Furthermore, in this case, the power supplied to both the stators 23 and 33 is controlled such that the power is sufficiently transmitted to the drive wheels DW and DW and the engine 3.
- vehicle speed VP is maintained at the value at the time of ENG start during EV traveling, and rotor rotational speeds VRA2 and VRB1 of A2 and B1 are indicated by the broken line
- the rotational speed of the crankshaft 3a connected to the A2 and B1 rotors 25 and 34 that is, the engine speed NE also increases.
- the engine 3 is started by controlling the ignition operation of the fuel injection valve and the spark plug (neither is shown) of the engine 3. Further, in this case, by controlling the first and second magnetic field rotational speeds VMF1 and VMF2, the engine speed NE is controlled to a relatively small value suitable for starting the engine 3.
- FIG. 31 shows a velocity alignment chart obtained by combining the two velocity alignment charts shown in FIG.
- TDENG is a torque transmitted to the crankshaft 3a of the engine 3 (hereinafter referred to as “engine transmission torque")
- TDDW is a torque transmitted to the drive wheels DW and DW (hereinafter referred to as “drive wheel transmission torque ”)).
- the second driving equivalent torque TSE2 is transmitted to both the driving wheels DW and DW and the crankshaft 3a using the first power generation equivalent torque TGE1 as a reaction force,
- the torque required for one rotating machine 21 is larger than in the other cases.
- TGE 1 ⁇ ⁇ ⁇ TDDW + ( ⁇ + 1) TDENG ⁇ / ( ⁇ + 1 + ⁇ ) (51)
- the first power generation equivalent torque TGE1 decreases with respect to the drive wheel transmission torque TDDW and the engine transmission torque TDENG of the same magnitude as the first pole pair number ratio ⁇ increases.
- the first pole pair number ratio ⁇ is set to the value 2.0, the first power generation equivalent torque TGE1 can be made smaller than when set to the value less than 1.0.
- the ENG traveling is an operation mode in which the vehicle travels using the power of the engine 3.
- the motive power (hereinafter referred to as "engine power”) output to the crankshaft 3a by combustion in the engine 3 during ENG travel is basically the best fuel consumption (hereinafter referred to as “best fuel consumption”) within the range where the required torque can be generated. Control to obtain).
- the required torque is a torque required of the vehicle, and is calculated, for example, by searching a map (not shown) according to the detected vehicle speed VP and accelerator opening degree AP.
- the second rotating machine is used to generate electric power by the stator 23 of the first rotating machine 21 using engine power transmitted to the A2 rotor 25, and without charging the generated electric power to the battery 43.
- the stator 33 of 31 is supplied.
- this operation mode is referred to as "battery input / output zero mode”.
- FIG. 32 shows a state of transmission of torque in this battery input / output zero mode.
- the second drive equivalent torque TSE2 and the B1 rotor transmission torque TRB1 are synthesized and transmitted to the B2 rotor 35 as the B2 rotor transmission torque TRB2, as in the ENG start-up during the EV traveling described above. Therefore, during the battery input / output zero mode, the electric power generated by the stator 23 of the first rotating machine 21 as described above is supplied to the stator 33 of the second rotating machine 31, whereby the second equivalent torque for driving TSE2 is obtained. Is transmitted to the B2 rotor 35, the engine torque transmitted to the B1 rotor 34 as described above is transmitted to the B2 rotor 35. Further, the engine torque distributed to the A1 rotor 24 as described above is further transmitted to the B2 rotor 35 via the connecting shaft 6.
- the first and second rotating machines 21 and 31 function as a continuously variable transmission.
- the rotor rotational speeds VRA2 and VRB1 of A2 and B1 are maintained while maintaining the speed relationship shown in equations (43) and (44). That is, by increasing the first magnetic field rotational speed VMF1 and decreasing the second magnetic field rotational speed VMF2 with respect to the engine rotational speed NE, the rotor rotational speeds VRA1 and VRB2 of the A1 and B2 ie, the vehicle speed VP are made steplessly. It can be slowed down. Conversely, as indicated by the alternate long and short dash lines in FIGS.
- the first magnetic field rotational speed VMF1 is decreased relative to the rotor rotational speeds VRA2 and VRB1 of A2 and B1, and the second magnetic field rotational speed By raising VMF2, the vehicle speed VP can be steplessly accelerated.
- the first and second magnetic field rotational speeds VMF1 and VMF2 are controlled so that the engine rotational speed NE becomes the target rotational speed.
- the target rotational speed is calculated, for example, by searching a map (not shown) in accordance with the vehicle speed VP and the calculated required torque. In this map, the target rotational speed is set to a value such that the best fuel consumption of the engine 3 can be obtained with respect to the vehicle speed VP and the required torque at that time.
- the engine power is temporarily divided, and the B2 rotor 35 is transmitted via the following first to third transmission paths. While being synthesized and transmitted to the drive wheels DW and DW.
- First transmission path A2 rotor 25 ⁇ magnetic force by magnetic line of force ML ⁇ A1 rotor 24 ⁇ connecting shaft 6 ⁇ B2 rotor 35
- Second transmission path B1 rotor 34 ⁇ magnetic force by magnetic line of force ML ⁇ B2 rotor 35
- Third transmission path A2 rotor 25 ⁇ magnetic force by magnetic line of force ML ⁇ stator 23 ⁇ first PDU 41 ⁇ second PDU 42 ⁇ stator 33 ⁇ magnetic force by magnetic line of force ⁇ B2 rotor 35
- engine power is transmitted to the drive wheels DW and DW by so-called magnetic paths by the magnetic force due to the magnetic field lines ML without being converted to electric power. Further, in the above-described third transmission path, the engine power is once converted to electric power, is returned to the power again, and is transmitted to the drive wheels DW and DW by a so-called electric path.
- the electric power generated by the stator 23, and the first and second magnetic field rotational speeds VMF1 and VMF2 are controlled such that the speed relationship shown in equations (43) and (44) is maintained. Be done.
- the second rotating machine 31 assists the engine 3.
- this operation mode is referred to as "assist mode".
- the first predetermined value is calculated by searching a map (not shown) according to the vehicle speed VP, for example. In this map, the first predetermined value is set to a torque value at which the best fuel consumption of the engine 3 can be obtained with respect to the vehicle speed VP at that time.
- the above lower limit value is set to a value that prevents the battery 43 from being overdischarged.
- vehicle required power the power required to drive the vehicle (hereinafter referred to as “vehicle required power”) represented by the vehicle speed VP and the required torque at that time is higher than the engine power that provides the best fuel efficiency. And when the battery 43 has enough power remaining.
- the power generation is performed by the stator 23 using the engine power transmitted to the A2 rotor 25.
- the electric power charged in the battery 43 is supplied to the stator 33, as shown in FIG. Therefore, a second driving equivalent torque TSE2 based on the power supplied from the stator 23 and the battery 43 is transmitted to the B2 rotor 35.
- a torque obtained by combining the second driving equivalent torque TSE2, the engine torque distributed to the A1 rotor 24 with power generation, and the engine torque transmitted to the B1 rotor 34 is , And is transmitted to the drive wheels DW and DW via the B2 rotor 35.
- the power transmitted to the drive wheels DW and DW is equal to the sum of the engine power and the power (energy) supplied from the battery 43.
- the electric power generated by the stator 23, the electric power supplied from the battery 43 to the stator 33, and the first and second magnetic field rotational speeds VMF1 and VMF2 are expressed by the equations (43) and (44). It is controlled to maintain the speed relationship shown in FIG. As a result, the shortage of engine power with respect to the vehicle required power is compensated by supplying power from the battery 43 to the stator 33.
- the example described above is an example in which the shortage of engine power with respect to the vehicle required power is relatively small, in the case of a relatively large amount, the first rotary machine 21 is added to the stator 33 of the second rotary machine 31. Power is also supplied from the battery 43 to the stator 23 of the
- the second predetermined value is calculated by searching a map (not shown) according to the vehicle speed VP, for example. In this map, the second predetermined value is set to a value smaller than the torque value at which the best fuel consumption can be obtained, with respect to the vehicle speed VP at that time. The upper limit value is set to a value that prevents the battery 43 from being overcharged.
- the driving in the drive charging mode is performed when the vehicle required power is smaller than the engine power for obtaining the best fuel efficiency and when the charging state is relatively small.
- the stator 33 of the second rotating machine 31 receives the electric power generated by the stator 23 of the first rotating machine 21.
- the electric power of the magnitude obtained by subtracting the electric power to be charged is supplied, and the second driving equivalent torque TSE2 based on this electric power is transmitted to the B2 rotor 35.
- a torque obtained by combining the second driving equivalent torque TSE2 the engine torque distributed to the A1 rotor 24 with power generation, and the engine torque transmitted to the B1 rotor 34 is , And is transmitted to the drive wheels DW and DW via the B2 rotor 35.
- the power transmitted to the drive wheels DW and DW is obtained by subtracting the power (energy) charged in the battery 43 from the engine power. It becomes a size.
- the power generated by the stator 23, the power charged to the battery 43, and the first and second magnetic field rotational speeds VMF1 and VMF2 are expressed by the equations (43) and (44). It is controlled to maintain the indicated speed relationship. As a result, the surplus of the engine power with respect to the vehicle required power is converted to electric power in the stator 23 of the first rotating machine 21, and the battery 43 is charged.
- the electric power generated by the stator 23 of the first rotating machine 21 is controlled such that the first power generation equivalent torque TGE1 is 1/3 of the engine torque
- the engine 3 to the drive wheels DW and DW The transmission of power can be done only by the magnetic path. In this case, a torque having a magnitude of 2/3 times the engine torque is transmitted to the drive wheels DW and DW.
- the engine 3 When the vehicle speed VP in the low speed state is rapidly increased during ENG traveling (hereinafter, such operation is referred to as "rapid acceleration operation during ENG traveling"), the engine 3, the first and second rotating machines 21, 31 is controlled as follows.
- 36 (a) shows an example of the respective velocity alignment charts of the first and second rotating machines 21 and 31 at the start of the sudden acceleration operation during this ENG traveling, and FIG. The velocity alignment chart which synthesize
- TENG is engine 3 torque.
- the engine speed NE is increased to a predetermined speed at which the maximum torque can be obtained. As shown in FIGS.
- the engine speed NE becomes higher than the vehicle speed VP, and the difference between the two increases.
- the direction of rotation of the second rotating magnetic field to be determined is the reverse direction. Therefore, in order to apply a positive torque to the drive wheels DW and DW from the stator 33 of the second rotating machine 31 that generates such a second rotating magnetic field, the stator 33 generates power. Further, the electric power generated by the stator 33 is supplied to the stator 23 of the first rotating machine 21 and the first rotating magnetic field is rotated forward.
- the second power generation equivalent torque TGE2 decreases with respect to the drive wheel transmission torque TDDW and the engine torque TENG having the same magnitude as the second pole pair logarithmic ratio ⁇ increases.
- the second pole-log ratio ⁇ is set to the value 2.0, the second drive equivalent torque TSE2 can be made smaller than when set to the value less than 1.0.
- Deceleration regeneration This deceleration regeneration is performed on the first rotating machine 21 or the second rotating machine 31 using the inertia energy of the drive wheels DW and DW while the vehicle is decelerating traveling, that is, when the vehicle is traveling with inertia. This is an operation mode for generating power and charging the generated power to the battery 43.
- deceleration regeneration when the ratio of the torque of the drive wheels DW, DW transmitted to the engine 3 to the torque of the drive wheels DW, DW (torque due to inertia) is small, a part of the power of the drive wheels DW, DW is used The two stators 23 and 33 generate electric power, and the generated electric power is charged to the battery 43.
- this power generation is performed using the power transmitted to the A2 rotor 25 as described later in the stator 23 of the first rotating machine 21, and in the stator 33 of the second rotating machine 31, the B2 rotor 35 is generated. It is performed using the power transmitted as will be described later.
- FIG. 37 shows a state of transmission of torque during the above-described deceleration regeneration.
- FIG. 38 (a) shows an example of the respective velocity alignment charts of the first and second rotating machines 21 and 31 during this deceleration regeneration
- FIG. 38 (b) shows FIG. 38 (a).
- combined two speed alignment charts is shown, respectively.
- a combined torque obtained by combining all of the torque of the drive wheels DW and DW with the torque distributed as described later to the A1 rotor 24 in the B2 rotor 35 along with the power generation in the stator 33 Is transmitted. Further, from the function of the second rotating machine 31 described above, the combined torque transmitted to the B2 rotor 35 is distributed to the stator 33 and the B1 rotor 34.
- Stop ENG Start This stop ENG start is an operation mode for starting the engine 3 while the vehicle is stopped. At the time of ENG start while stopped, electric power is supplied from the battery 43 to the stator 23 of the first rotating machine 21 and the first rotating magnetic field generated by the stator 23 is made to forward rotate accordingly and the B1 rotor 34 is described later. The generated power is generated by the stator 33 using the transmitted power, and the generated power is further supplied to the stator 23.
- FIG. 39 shows a state of transmission of torque at the time of ENG start while the vehicle is stopped.
- FIG. 40 (a) shows an example of the respective velocity alignment charts of the first and second rotating machines 21 and 31 at the time of ENG start while the vehicle is stopped
- FIG. 40 (b) shows FIG. 40 (a).
- combined two shown velocity alignment charts is shown, respectively.
- the first driving equivalent torque TSE1 from stator 23 acts to rotate A2 rotor 25 forward.
- it acts to reverse the A1 rotor 24.
- part of the torque transmitted to the A2 rotor 25 is transmitted to the crankshaft 3a, whereby the crankshaft 3a performs normal rotation.
- the rest of the torque transmitted to the A2 rotor 25 is transmitted to the B1 rotor 34, and thereafter, as the stator 33 of the second rotating machine 31 generates electricity, the stator 33 is used as electric energy It is transmitted.
- the second rotating magnetic field generated as a result of power generation in the stator 33 is reversed.
- the second power generation equivalent torque TGE2 generated along with the power generation by the stator 33 acts to cause the B2 rotor 35 to rotate in the forward direction.
- the torque transmitted to the B1 rotor 34 is further transmitted to the B2 rotor 35 (shown by an arrow F) so as to balance the second electric power generation equivalent torque TGE2, and acts to rotate the B2 rotor 35 forward.
- the torque is supplied to the stator 23 of the first rotating machine 21 so that the torque for reverse rotating the A1 rotor 24 indicated by the arrow D and the torque for normal rotating the B2 rotor 35 indicated by arrows E and F are balanced.
- the A1 rotor 24, the B2 rotor 35, and the drive wheels DW and DW connected to each other are held stationary.
- the rotor rotational speeds VRA1 and VRB2 of A1 and B2 become the value 0, and the vehicle speed VP also becomes the value 0.
- the power relationship supplied to stator 23, the power generated by stator 33, and the first and second magnetic field rotational speeds VMF1 and VMF2 maintain the speed relationship shown in the equations (43) and (44).
- the rotor rotational speeds VRA2 and VRB1 of A2 and B1 are controlled to be relatively small values (see FIGS. 40 (a) and 40 (b)).
- the engine speed NE is controlled to a relatively small value suitable for starting the engine 3 while keeping the vehicle speed VP at the value 0.
- the engine 3 is started by controlling the ignition operation of the fuel injection valve and the spark plug of the engine 3 according to the crank angle position.
- ENG creep This ENG creep is an operation mode for performing a creep operation of a vehicle using engine power.
- the power generated by the stator 23 is generated using the engine power transmitted to the A2 rotor 25, and the power generated by the stator 33 is generated using the engine power transmitted to the B1 rotor 34. Further, the battery 43 is charged with the power generated by the two stators 23 and 33 as described above.
- FIG. 41 shows a state of transmission of torque during the ENG creep described above.
- FIG. 42 (a) shows an example of the respective velocity alignment charts of the first and second rotating machines 21 and 31 during this ENG creep, and
- FIG. 42 (b) shows FIG. 42 (a).
- combined two speed alignment charts is shown, respectively.
- a part of the engine torque TENG is transmitted to the A2 rotor 25 along with the power generation in the stator 23 as in the case of the battery input / output zero mode described above.
- the engine torque TENG transmitted to the A2 rotor 25 is distributed to the stator 23 and the A1 rotor 24. Also, as shown in FIGS.
- the engine torque TENG distributed to the A1 rotor 24, the second power generation equivalent torque TGE2, and the engine torque TENG transmitted to the B1 rotor 34 are synthesized in the B2 rotor 35.
- the combined torque is transmitted. Further, this combined torque is transmitted to the drive wheels DW, DW to cause the drive wheels DW, DW to rotate in the forward direction.
- the electric power generated by the stators 23 and 33, and the first and second magnetic field rotational speeds VMF1 and VMF2 are controlled such that the rotor rotational speeds VRA1 and VRB2 of A1 and B2, ie, the vehicle speed VP become very small (see FIG. 42 (a), (b)), whereby the creep operation is performed.
- engine torque TENG distributed to A1 rotor 24 along with power generation by stator 23, and B2 rotor via B1 rotor 34 along with power generation by stator 33.
- the engine torque TENG transmitted to 35 is transmitted to the drive wheels DW and DW. That is, since a part of the engine torque TENG can be transmitted to the drive wheels DW, DW, a large reaction force can be prevented from acting on the engine 3 from the drive wheels DW, DW. Therefore, creep operation does not occur. It can be performed.
- the above-mentioned driving by ENG creep is mainly performed when the state of charge is small or when the vehicle is climbing.
- FIG. 43 shows a state of transmission of torque at the time of ENG start.
- the second magnetic field rotational speed VMF2 of the second rotating magnetic field which was reversed during ENG creep, is controlled to be a value 0, and the first magnetic field rotational speed VMF1 of the first rotating magnetic field that has been forward rotated. And increase engine power.
- the operation in the above-described battery input / output zero mode is performed.
- the rotor rotational speeds VRA1 and VRB2 of A1 and B2 that is, the vehicle speed VP increase from the ENG creep state shown by the broken line in FIG. Take off.
- FIG. 45 shows a state of transmission of torque during the EV reverse start.
- FIG. 46 (a) shows an example of the respective velocity alignment charts of the first and second rotating machines 21 and 31 during the EV reverse start
- FIG. 46 (b) shows it in FIG. 46 (a). The velocity alignment chart which synthesize
- the second driving equivalent torque TSE2 from the stator 33 acts to reverse the B2 rotor 35, and at the same time, the B1 rotor 24 becomes positive. Acts to roll.
- the rotor rotational speeds VRA1 and VRB2 of A1 and B2 ie, the vehicle speed VP increase in the negative direction from the stopped state shown by the broken line in FIG. And the vehicle starts moving backward.
- FIG. 47 shows a state of transmission of torque during the ENG backward start.
- the second magnetic field rotational speed VMF2 of the second rotating field reversed during ENG creep is controlled so as to further increase in the negative direction, and the first rotating field is rotated in the normal direction While increasing the magnetic field rotational speed VMF1, the engine power is increased.
- the vehicle speed VP rises in the negative direction from the ENG creep state shown by the broken line in the figure, and the vehicle starts to move backward.
- the first and second rotating machines 21 and 31 have the same function as a device combining the planetary gear device and a general one-rotor type rotating machine, Unlike a conventional power plant, a planetary gear set for distributing / combining and transmitting power is not necessary, and accordingly, the power plant 1 can be miniaturized accordingly. Also, unlike the conventional case described above, as described with reference to FIG. 32, the engine power is transmitted to the drive wheels DW and DW without recirculation, so the first and second rotating machines 21 and 31 The power to pass through can be reduced. Therefore, downsizing and cost reduction of the first and second rotating machines 21 and 31 can be achieved, whereby further downsizing and cost reduction of the power plant 1 can be achieved. Furthermore, by using the first and second rotating machines 21 and 31 having torque capacities commensurate with the reduced power as described above, the loss of power can be suppressed and the driving efficiency of the power unit 1 can be enhanced. it can.
- the engine power is obtained by the first transmission path (A2 rotor 25, magnetic force by magnetic line of force ML, A1 rotor 24, connecting shaft 6, B2 rotor 35) and second transmission path (B1 rotor 34, magnetic force by magnetic line of force ML) B2 rotor 35), through a total of three paths of the third transmission path (A2 rotor 25, magnetic force by magnetic field line ML, stator 23, first PDU 41, second PDU 42, stator 33, magnetic force by magnetic field line ML, B2 rotor 35)
- the divided wheels are transmitted to the drive wheels DW and DW.
- the power (energy) passing through the first and second PDUs 41 and 42 via the third transmission path can be reduced, and therefore, downsizing and cost reduction of the first and second PDUs 41 and 42 can be achieved.
- further miniaturization and cost reduction of the power plant 1 can be achieved.
- engine power is transmitted to the drive wheels DW and DW by electrical paths
- power is transmitted to the drive wheels DW and DW by magnetic paths.
- the transmission efficiency is higher than the third transmission path.
- the engine power is continuously shifted, and the drive wheels DW, It is transmitted to DW. Furthermore, in this case, since the first and second magnetic field rotational speeds VMF1 and VMF2 are controlled such that the engine rotational speed NE becomes the target rotational speed set so as to obtain the best fuel consumption, the best fuel consumption is obtained.
- the drive wheels DW and DW can be driven while controlling the engine power as described above. Therefore, the drive efficiency of the power plant 1 can be further enhanced.
- the first pole pair number ratio ⁇ of the first rotating machine 21 is set to the value 2.0, the above-mentioned equation (when starting ENG during EV traveling in which the torque required for the first rotating machine 21 becomes particularly large) As described using 51), the first power generation equivalent torque TGE1 can be made smaller than when the first pole pair number ratio ⁇ is set to a value less than 1.0, and therefore, the first rotary machine 21 Further miniaturization and cost reduction can be achieved.
- the second pole pair ratio ⁇ of the second rotating machine 31 is set to the value 2.0, the time of the start of the rapid acceleration operation during ENG traveling where the torque required for the second rotating machine 31 becomes particularly large
- the second drive equivalent torque TSE2 can be made smaller than when the second pole logarithm ratio ⁇ is set to a value less than 1.0, and therefore the second Further downsizing and cost reduction of the rotating machine 31 can be achieved.
- the driving in the drive charging mode is performed when the required vehicle power is smaller than the engine power for obtaining the best fuel efficiency, and during the driving charge mode, the engine power is controlled to obtain the best fuel efficiency.
- the surplus of the engine power with respect to the vehicle required power is charged to the battery 43 as electric power.
- the operation in the assist mode is performed when the required vehicle power is larger than the engine power for obtaining the best fuel efficiency, and during the assist mode, the engine power is controlled to obtain the best fuel efficiency, and The shortage of engine power for the engine is compensated by the supply of power from the battery 43. Therefore, regardless of the size of the load of the drive wheels DW, DW, the drive efficiency of the power plant 1 can be further enhanced.
- the power is supplied from the battery 43 to the first rotating machine 21 and / or the second rotating machine 31, and the first rotating machine 21 and The power generated by the second rotating machine 31 is charged to the battery 43. Further, as described above, the ECU 2 calculates the state of charge of the battery 43 based on the detection signal from the current / voltage sensor 56.
- the battery 43 is configured by a secondary battery such as a nickel hydrogen battery or a lithium ion battery.
- a secondary battery such as a nickel hydrogen battery or a lithium ion battery.
- SOC State of Charge
- the ECU 2 of the present embodiment performs control in accordance with the SOC of the battery 43 (hereinafter referred to as "battery SOC").
- FIG. 49 is a diagram showing the range of the battery SOC in which charge and discharge are repeated. As shown in FIG. 49, the ECU 2 controls the operations of the engine 3 and the first and second rotating machines 21 and 31 so that the battery SOC falls within the range from the lower limit SOC to the upper limit SOC.
- the operation device 1 continues the ENG start operation, and as indicated by thick solid lines in FIGS. 44 (a) and 44 (b), the rotation direction of the second rotating magnetic field in the stator 33 of the second rotating machine 31 is positive.
- the stator 33 In the turning direction, the stator 33 is in a power running state, and consumes electrical energy.
- the regenerative energy obtained by the regenerative power generation of the first rotating machine 21 is used.
- the battery 43 is charged by the surplus regenerative energy.
- the battery 43 is charged by the regenerative energy.
- the battery SOC may exceed the upper limit SOC. Therefore, when the battery SOC is equal to or higher than the first threshold value lower than the upper limit SOC shown in FIG. 49, the ECU 2 performs the control described below.
- FIGS. 50 (a) and 50 (b) show (a) a speed alignment chart when the battery SOC is less than the first threshold when the operation mode of the operation apparatus 1 is "ENG start", and (b) the battery The velocity alignment chart when SOC is more than a 1st threshold value is shown. As shown in FIG.
- the first magnetic field rotational speed VMF1 of the first rotating magnetic field in the stator 23 of the first rotating machine 21 is as shown in FIG. It is controlled to be lower than the first magnetic field rotational speed VMF1 shown in FIG.
- the regenerative energy generated by the first rotating machine 21 in the case shown in FIG. 50 (b) is lower than the regenerative energy in the case shown in FIG. 50 (a).
- the rotation direction of the second rotating magnetic field in the stator 33 of the second rotating machine 31 is the reverse direction, the regenerative energy generated by the second rotating machine 31 in the case shown in FIG. It is lower than the regenerative energy in the case shown in).
- the rotation direction of the second rotating magnetic field in the stator 33 of the second rotating machine 31 is the normal direction, the energy consumed by the second rotating machine 31 in the case shown in FIG. It is higher than the energy consumption shown in a).
- the ECU 2 controls the engine 3 to operate at the shaft rotation speed lower than the required ENG shaft rotation speed and without changing the output torque. As a result, the charge amount to the battery 43 is reduced. Therefore, when the battery SOC is equal to or higher than the first threshold value close to the upper limit SOC, the ECU 2 can perform the control to prevent the battery 43 from being overcharged. However, as a result of the control, the output of the engine 3 is reduced. However, as shown in FIG. 50 (b), since the torque from the second rotating machine 31 is applied, the output torque transmitted to the drive wheels DW, DW does not change.
- the torque that the ECU 2 requests the engine 3 at the time of the control described above may be less than the ENG required torque described with reference to FIG.
- the ECU 2 controls the engine 3 to output a torque according to the shaft rotational speed at the time of the above control.
- the torque at the optimum operating point when the shaft rotation speed of the engine 3 is low is approximately proportional to the shaft rotation speed, so the torque at this time is smaller than the ENG required torque. With such control, the output of the engine 3 is further reduced, but the engine 3 can be operated at the optimum operating point.
- the engine 3 is controlled to operate at a shaft rotation number lower than the required ENG shaft rotation number of the engine 3.
- the regenerative energy per unit time generated in the stator 23 of the first rotating machine 21 with respect to the torque required for the engine 3 exceeds the specified value, it is lower than the ENG required torque described with reference to FIG.
- the engine 3 may be controlled to output a torque.
- the shaft rotational speed of the engine 3 may be equal to or less than the required ENG shaft rotational speed described with reference to FIG.
- the battery 43 is discharged when the operation mode of the operation device 1 is "EV travel".
- the battery SOC may fall below the lower limit SOC. Therefore, when the battery SOC is equal to or lower than the second threshold value higher than the lower limit SOC shown in FIG. 49, the ECU 2 performs the control described below.
- FIGS. 51 (a) and 51 (b) show (a) a speed alignment chart when the battery SOC is higher than the second threshold when the operation mode of the operation apparatus 1 is "EV travel", and (b) the battery The velocity alignment chart when SOC is below a 2nd threshold value is shown.
- the second magnetic field rotational speed VMF2 of the second rotating magnetic field in the stator 33 of the second rotating machine 31 is the second magnetic field rotation shown in FIG. 51 (a). It is controlled to be lower than the speed VMF2.
- the upper limit of the number of shaft revolutions of the engine 3 during the control is the number of revolutions until the first magnetic field rotational speed VMF1 of the first rotating magnetic field in the stator 23 of the first rotating machine 21 is controlled to zero.
- the discharge amount of the battery 43 is reduced by controlling the engine 3 to operate. Therefore, when the battery SOC is equal to or lower than the second threshold value close to the lower limit SOC, the ECU 2 can perform the control to prevent the overdischarge of the battery 43.
- the second threshold is variable.
- the energy required when the first rotating machine 21 starts the engine 3 varies depending on the vehicle speed VP, and the energy required is larger when the vehicle speed VP is higher. Therefore, the ECU 2 sets a second threshold according to the vehicle speed VP. That is, the ECU 2 sets the second threshold value higher as the vehicle speed VP is higher.
- the battery 43 is discharged when the operation mode of the operation device 1 is “ENG backward start”. However, when the battery 43 is discharged in a state where the battery SOC is close to the lower limit SOC, the battery SOC may fall below the lower limit SOC. Therefore, when the battery SOC is equal to or lower than the second threshold value higher than the lower limit SOC shown in FIG. 49, the ECU 2 performs the control described below.
- FIGS. 52 (a) and 52 (b) are (a) velocity alignment charts when the battery SOC is higher than the second threshold when the operation mode of the operating device 1 is "ENG backward start", and (b) FIG. 17 shows a velocity alignment chart when the battery SOC is less than or equal to a second threshold value. As shown in FIG.
- the absolute value of the second magnetic field rotational speed VMF2 of the second rotating magnetic field in the stator 33 of the second rotating machine 31 is as shown in FIG. It is controlled to be lower than the absolute value of the second magnetic field rotational speed VMF2 shown in (a). As a result, the energy consumed by the second rotating machine 31 is reduced.
- the ECU 2 controls the engine 3 to operate at the shaft rotation speed lower than the required ENG shaft rotation speed and without changing the output torque. As a result, the amount of discharge of the battery 43 is reduced. Therefore, when the battery SOC is equal to or lower than the second threshold value close to the lower limit SOC, the ECU 2 can perform the control to prevent the overdischarge of the battery 43. However, as a result of the control, the output of the engine 3 is reduced. However, since the output torque of the engine 3 does not change, the output torque transmitted to the drive wheels DW and DW does not change.
- the torque that the ECU 2 requests the engine 3 at the time of the control described above may be less than the ENG required torque described with reference to FIG.
- the ECU 2 controls the engine 3 to output a torque according to the shaft rotational speed at the time of the above control.
- the torque at the optimum operating point when the shaft rotation speed of the engine 3 is low is approximately proportional to the shaft rotation speed, so the torque at this time is smaller than the ENG required torque. With such control, the output of the engine 3 is further reduced, but the engine 3 can be operated at the optimum operating point.
- the engine 3 is controlled to operate at a shaft rotation number lower than the required ENG shaft rotation number of the engine 3.
- the energy per unit time consumed by the stator 33 of the second rotating machine 31 for the torque required for the engine 3 exceeds the specified value, it is lower than the ENG required torque described with reference to FIG.
- the engine 3 may be controlled to output a torque.
- the shaft rotational speed of the engine 3 may be equal to or less than the required ENG shaft rotational speed described with reference to FIG.
- FIG. These power units 1A to 1D are mainly different from the first embodiment in that they further include transmissions 61, 71, 81 and 91, and any of the second to fifth embodiments.
- the connection between the engine 3, the first and second rotating machines 21 and 31, and the drive wheels DW and DW is the same as that in the first embodiment. That is, the A2 and B1 rotors 25 and 34 are mechanically connected to the crankshaft 3a of the engine 3, and the A1 and B2 rotors 24 and 35 are mechanically connected to the drive wheels DW and DW.
- FIG. 53 to FIG. 56 the same components as in the first embodiment are indicated using the same reference numerals. The same applies to the drawings for explaining the other embodiments described later. Hereinafter, the differences from the first embodiment will be mainly described in order from the power unit 1A of the second embodiment.
- the transmission 61 is provided in place of the aforementioned gear 7b and the first gear 8b.
- the transmission 61 is a belt-type continuously variable transmission, and is provided on the input shaft connected to the second rotation shaft 7 described above, the output shaft connected to the idler shaft 8, and the input shaft and the output shaft. And a metal belt (not shown) wound around the pulleys.
- the transmission 61 outputs the power input to the input shaft to the output shaft in a shifted state by changing the effective diameters of the pulleys. Further, the transmission ratio of the transmission 61 (rotation speed of input shaft / rotation speed of output shaft) is controlled by the ECU 2.
- the transmission 61 is provided between the A1 and B2 rotors 24 and 35 and the driving wheels DW and DW, and the power transmitted to the A1 and B2 rotors 24 and 35 is the transmission It is shifted by 61 and transmitted to the drive wheels DW and DW.
- the transmission ratio is controlled to a predetermined value on the deceleration side larger than the value 1.0.
- the torques transmitted to the A1 and B2 rotors 24 and 35 are increased in the transmission 61 and then transmitted to the drive wheels DW and DW.
- the electric power generated by the first rotating machine 21 and the electric power supplied to the second rotating machine 31 the generated electric power so that the torque transmitted to the rotors 24 and 35 of A1 and B2 decreases.
- the maximum value of the torque required for the first and second rotating machines 21 and 31 can be reduced, and the further downsizing of the first and second rotating machines 21 and 31 can be achieved. And reduce costs.
- the transmission gear ratio of the transmission 61 is smaller than the value 1.0 Controlled by value.
- the rotor rotational speeds VRA1 and VRB2 of A1 and B2 can be reduced with respect to the vehicle speed VP. Therefore, in the first and second rotating machines 21 and 31 due to the excess of both rotor rotational speeds VRA1 and VRB2. Failure can be prevented.
- the A1 rotor 24 is made of a magnet, and the magnet is lower in strength than the soft magnetic body, and is thus particularly effective because the above-mentioned problems are likely to occur.
- the transmission gear ratio of the transmission 61 is set so that the first and second magnetic field rotational speeds VMF1 and VMF2 become predetermined first and second target values, respectively. It is controlled.
- These first and second target values are calculated by searching the map according to the vehicle speed VP when only the first and second rotating machines 21 and 31 are used as a power source, and the engine 3 and the first When the second rotating machine 21 or 31 is used as a power source, it is calculated by searching another map other than the above according to the engine speed NE and the vehicle speed VP.
- the first and second target values can obtain high efficiencies of the first and second rotating machines 21 and 31 with respect to the vehicle speed VP (and the engine speed NE) at that time. It is set to a similar value. Further, in parallel with the control of the transmission 61, the first and second magnetic field rotational speeds VMF1 and VMF2 are controlled to the first and second target values, respectively. As described above, according to the present embodiment, high efficiency of the first and second rotating machines 21 and 31 can be obtained while the vehicle is traveling.
- the engine power can be continuously changed by the first and second rotating machines 21 and 31 and transmitted to the drive wheels DW and DW. Therefore, the frequency of the shift operation of the transmission 61 can be lowered. Therefore, the heat loss due to the speed change operation can be suppressed, whereby the high drive efficiency of the power plant 1A can be secured. Besides, according to the present embodiment, the effect of the first embodiment can be obtained similarly.
- the transmission 61 is a belt-type continuously variable transmission, but may be a toroidal-type continuously variable transmission or a gear-type stepped transmission.
- the transmission 71 is a gear type stepped transmission, and has a plurality of gears whose gear ratios are different from the input shaft 72 and the output shaft (not shown). It has a clutch (none of which is shown) for connecting and disconnecting between the trains and the plurality of gear trains, the input shaft 72 and the output shaft for each gear train.
- the transmission 71 outputs the power input to the input shaft 72 to the output shaft in a state of being shifted by one of the plurality of gear trains.
- a total of four gear stages are set, each of which comprises 1.0) and the third speed (gear ratio ⁇ 1.0), and one gear stage for reverse, and the change is controlled by the ECU 2.
- the gear 7b is not provided on the second rotating shaft 7, and the rotors 24 and 35 of A1 and B2 are connected to the drive wheels DW and DW as follows. It is connected. That is, the A1 rotor 24 is directly connected to the input shaft 72 of the transmission 71, and the output shaft of the transmission 71 is directly connected to the connecting shaft 6 described above.
- a gear 6b is integrally provided on the connecting shaft 6, and the gear 6b meshes with the first gear 8b described above.
- the A1 rotor 24 includes the drive wheels DW and DW via the transmission 71, the gear 6b, the first gear 8b, the idler shaft 8, the second gear 8c, the gear 9a, the differential gear mechanism 9, and the like.
- Mechanically connected to The power transmitted to the A1 rotor 24 is shifted by the transmission 71 and transmitted to the drive wheels DW and DW.
- the B2 rotor 35 is mechanically connected to the drive wheels DW and DW without the transmission 71 via the connection shaft 6, the gear 6b, the first gear 8b, and the like.
- the transmission gear of the transmission 71 has the first speed (gear ratio> It is controlled to 1.0).
- the torque transmitted to the A1 rotor 24 is transmitted to the drive wheels DW and DW after being increased in the transmission 71.
- the electric power generated by the first rotating machine 21 is controlled such that the torque transmitted to the A1 rotor 24 is reduced.
- the maximum value of the torque required for the first rotating machine 21 can be reduced, and further downsizing and cost reduction of the first rotating machine 21 can be achieved.
- the shift position of the transmission 71 is controlled to the third speed (gear ratio ⁇ 1.0).
- the A1 rotor rotational speed VRA1 can be reduced with respect to the vehicle speed VP, it is possible to prevent the failure of the first rotating machine 21 due to the excessive A1 rotor rotational speed VRA1. it can.
- the A1 rotor 24 is made of a magnet, and the magnet is lower in strength than the soft magnetic body, and the above-mentioned problems are likely to occur.
- the shift position of the transmission 71 is controlled such that the first magnetic field rotational speed VMF1 becomes a predetermined target value.
- This target value is calculated by searching the map according to the vehicle speed VP when only the first and second rotary machines 21 and 31 are used as a power source, and the engine 3 and the first and second rotary machines 21 are calculated. 31 is used as a power source, it is calculated by searching another map other than the above according to the engine speed NE and the vehicle speed VP. Further, in these maps, the target value is set to a value at which high efficiency of the first rotating machine 21 can be obtained with respect to the vehicle speed VP (and the engine speed NE) at that time. Further, in parallel with the control of the transmission 71, the first magnetic field rotational speed VMF1 is controlled to the above-mentioned target value. Thus, according to the present embodiment, high efficiency of the first rotating machine 21 can be obtained while the vehicle is traveling.
- the first and second rotating machines 21 and 31 are controlled as follows. That is, during the shifting operation of the transmission 71, the connection between the A1 rotor 24 and the drive wheels DW and DW is interrupted by the interruption between the gear train in the transmission 71 and the input shaft 72 and the output shaft. Since the loads of the drive wheels DW, DW do not act on the rotor 24, power generation is not performed in the first rotating machine 21, and power is supplied to the stator 33 of the second rotating machine 31 from the battery 43.
- the second driving equivalent torque TSE2 from the stator 33 and a part of the engine torque TENG transmitted to the B1 rotor 34 are synthesized, and the B2 rotor is produced. Since the torque is transmitted to the drive wheels DW and 35 via 35, it is possible to suppress the shift shock due to the engine torque TENG not being transmitted to the drive wheels DW and DW via the transmission 71, thus enhancing the productability. be able to. Besides, according to the present embodiment, the effect of the first embodiment can be obtained similarly.
- the gear 7b is not provided on the second rotating shaft 7, and the first gear 8b described above is integrated with the connecting shaft 6. It meshes with the provided gear 6b.
- the A1 rotor 24 does not intervene through the transmission 81 via the connecting shaft 6, the gear 6b, the first gear 8b, the idler shaft 8, the second gear 8c, the gear 9a, the differential gear mechanism 9, and the like.
- the driving wheels DW and DW are connected to each other.
- the transmission 81 is a gear-type stepped transmission having the first to third speeds, which is configured similarly to the transmission 71 of the third embodiment, and is directly connected to the B2 rotor 35.
- the input shaft 82 and the output shaft (not shown) directly connected to the connecting shaft 6 are provided, and the power input to the input shaft 82 is changed in speed and output to the output shaft. Further, the change of the gear position of the transmission 81 is controlled by the ECU 2.
- the B2 rotor 35 is mechanically coupled to the drive wheels DW and DW via the transmission 81, the gear 6b, the second gear 8c, and the like.
- the power transmitted to the B2 rotor 35 is shifted by the transmission 81 and transmitted to the drive wheels DW and DW.
- the gear position of the transmission 81 is the first speed It is controlled to (gear ratio> 1.0).
- the torque transmitted to the B2 rotor 35 is increased in the transmission 81 and then transmitted to the drive wheels DW and DW.
- the power supplied to the second rotating machine 31 is controlled such that the torque transmitted to the B2 rotor 35 is reduced.
- the maximum value of the torque required for the second rotating machine 31 can be reduced, and further downsizing and cost reduction of the second rotating machine 31 can be achieved.
- the torque from the stator 33 and a part of the engine torque TENG transmitted to the B1 rotor 34 are synthesized and transmitted to the drive wheels DW and DW via the B2 rotor 35. Since the torque larger than that of the A1 rotor 24 acts on the B2 rotor 35, it is particularly effective.
- the shift position of the transmission 81 is controlled to the third speed (gear ratio ⁇ 1.0).
- the B2 rotor rotational speed VRB2 can be reduced relative to the vehicle speed VP, so that the failure of the second rotating machine 31 due to the excessive increase of the B2 rotor rotational speed VRB2 can be prevented. it can.
- the shift position of the transmission 81 is controlled such that the second magnetic field rotational speed VMF2 becomes a predetermined target value.
- This target value is calculated by searching the map according to the vehicle speed VP when only the first and second rotary machines 21 and 31 are used as a power source, and the engine 3 and the first and second rotary machines 21 are calculated. 31 is used as a power source, it is calculated by searching another map other than the above according to the engine speed NE and the vehicle speed VP. Further, in these maps, the target value is set to a value such that high efficiency of the second rotating machine 31 can be obtained with respect to the vehicle speed VP (and the engine speed NE) at that time. Further, in parallel with the control of the transmission 81, the second magnetic field rotational speed VMF2 is controlled to the above-mentioned target value. Thereby, according to the present embodiment, high efficiency of the second rotating machine 31 can be obtained while the vehicle is traveling.
- an input shaft 92 of the transmission 91 is directly connected to the flywheel 5 and an output shaft (not shown) thereof is directly connected to the first rotation shaft 4 described above.
- the transmission 91 is provided between the crankshaft 3 a and the rotors 25 and 34 of A 2 and B 1 to shift the engine power and transmit it to the A 2 rotor 25 and the B 1 rotor 34.
- the number of teeth of the gear 9a of the differential gear mechanism 9 described above is larger than the number of teeth of the second gear 8c of the idler shaft 8, whereby the power transmitted to the idler shaft 8 is reduced. In the state, it is transmitted to the drive wheels DW and DW.
- the gear position of the transmission 91 is the second speed It is controlled to (gear ratio ⁇ 1.0).
- the engine torque TENG input to the rotors 25 and 34 of A2 and B1 decreases.
- the electric power generated by the first rotating machine 21 and the electric power supplied to the second rotating machine 31 are generated such that the engine torque TENG transmitted to the rotors 24 and 35 of A1 and B2 decreases. Power) is controlled.
- the engine torque TENG transmitted to the A1 and B2 rotors 24 and 35 is transmitted to the drive wheels DW and DW in a state increased by deceleration by the second gear 8c and the gear 9a.
- the maximum value of the torque required for the first and second rotating machines 21 and 31 can be reduced, and the sizes of the first and second rotating machines 21 and 31 can be further reduced. And cost can be reduced.
- the rotor rotational speeds VRA2 and VRB1 of A2 and B1 can be reduced as compared with the case of the second gear, so both rotor rotational speeds VRA2 and VRB1 are excessive. It is possible to prevent the failure of the first and second rotating machines 21 and 31 due to Since the B1 rotor 34 is made of a magnet, the above-mentioned problems are likely to occur, which is particularly effective.
- the transmission gear position of transmission 91 has first and second magnetic field rotational speeds VMF1 and VMF2 corresponding to first and second rotating machines 21 and 31, respectively, according to engine speed NE and vehicle speed VP.
- the value is changed so that high efficiency of can be obtained.
- the first and second magnetic field rotational speeds VMF1 and VMF2 are the engine rotational speed NE, the vehicle speed VP, the gear position of the transmission 91, It is controlled to a value determined by the equations (43) and (44).
- shift shock control In addition, in order to suppress a shift shock, during ENG traveling and during a shift operation of the transmission 91, that is, when the transmission 91 blocks between the engine 3 and the rotors 25 and 34 of A2 and B1.
- the first and second rotating machines 21 and 31 are controlled as follows. Hereinafter, such control of the first and second rotating machines 21 and 31 is referred to as "shift shock control".
- the first and second rotating magnetic fields respectively generated in the stators 23 and 33 are caused to rotate in the normal direction.
- the first driving equivalent torque TSE1 from the stator 23 and the torque transmitted to the A1 rotor 24 as described later are synthesized, and this synthesized torque is transmitted to the A2 rotor 25.
- the torque transmitted to the A2 rotor 25 is not transmitted to the crankshaft 3a due to the interruption by the transmission 91 described above, is transmitted to the B1 rotor 34, and is further combined with the second drive equivalent torque TSE2 from the stator 33. After that, it is transmitted to the B2 rotor 35. Part of the torque transmitted to the B2 rotor 35 is transmitted to the A1 rotor 24, and the remaining part is transmitted to the drive wheels DW and DW.
- the present embodiment it is possible to suppress the shift shock due to the fact that the engine torque TENG is not transmitted to the drive wheels DW and DW during the shift operation, and to improve the commercial property. Note that this shift shock control is performed only during the shift operation of the transmission 91. Besides, according to the present embodiment, the effect of the first embodiment can be obtained similarly.
- the transmissions 71, 81, and 91 are gear-type stepped transmissions, but may be belt-type or toroidal-type continuously variable transmissions.
- a power plant 1E according to a sixth embodiment will be described with reference to FIG. As shown to the same figure, this power plant 1E adds the brake mechanism BL to the power plant 1 of 1st Embodiment.
- this power plant 1E adds the brake mechanism BL to the power plant 1 of 1st Embodiment.
- differences from the first embodiment will be mainly described.
- the brake mechanism BL has a one-way clutch OC connected to the aforementioned first rotary shaft 4 and the case CA.
- the one-way clutch OC connects between the first rotating shaft 4 and the case CA configured to be non-rotatable when power is applied to reversely rotate the crankshaft 3a to which the first rotating shaft 4 is connected. When power for causing normal rotation is applied, the first rotation shaft 4 and the case CA are shut off.
- the brake mechanism BL configured by the one-way clutch OC and the case CA, the rotation of the first rotating shaft 4 is permitted only when forward rotating with the crankshaft 3a, the A2 rotor 25 and the B1 rotor 34, It is blocked when the single rotation shaft 4 reverses with the crankshaft 3a or the like.
- the reverse rotation of the A2 rotor 25 is blocked by the brake mechanism BL with respect to the first rotating magnetic field of the stator 23 that reverses as described above, so it is apparent from the function of the first rotating machine 21 described above.
- all the power supplied to the stator 23 is transmitted as power to the A1 rotor 24, whereby the A1 rotor 24 rotates forward.
- the reverse rotation of the B1 rotor 34 is blocked by the brake mechanism BL with respect to the second rotating magnetic field of the stator 33 rotating normally as described above, as apparent from the function of the second rotating machine 31 described above
- the power supplied to the stator 33 is all transmitted to the B2 rotor 35 as motive power, whereby the B2 rotor 35 rotates forward.
- the power transmitted to the A1 and B2 rotors 24 and 35 is transmitted to the drive wheels DW and DW, and as a result, the drive wheels DW and DW perform forward rotation.
- the first and second drive equivalent torques TSE1 and TSE2 act to reverse the rotors 25 and 34 of A2 and B1, respectively, which are prevented from reversing by the brake mechanism BL.
- the rotors 25 and 34 of the crankshafts 3a, A2 and B1 are not only reversed but also held stationary.
- the drive wheels DW and DW can be driven by the first and second rotating machines 21 and 31 without using engine power. Further, during this driving, the crankshaft 3a is not only reversed but also kept stationary so that the engine 3 will not be dragged.
- the first and second pole-log ratios ⁇ and ⁇ are both set to the value 2.0, but the first and second poles When the logarithmic ratios ⁇ and ⁇ are set smaller than the value 1.0, the following effects can be obtained.
- the engine speed NE is When the vehicle speed is higher than the vehicle speed VP (see the two-dot chain line in FIGS. 33A and 33B), the first magnetic field rotational speed VMF1 may be higher than the engine speed NE and may be excessive.
- the second pole-log ratio ⁇ is set to a relatively large value
- the second The magnetic field rotational speed VMF2 may be higher than the vehicle speed VP and may be excessive.
- the second pole-log ratio ⁇ is set to be smaller than the value 1.0, the velocity alignment graph shown by broken lines in FIGS.
- the A2 rotor 25 and the B1 rotor 34 are connected to each other, and the A1 rotor 24 and the B2 rotor 35 are connected to each other.
- the A2 rotor 25 and the B1 rotor 34 may not be connected to each other as long as they are connected to 3a, and may not be connected to each other as long as they are connected to the drive wheels DW and DW.
- the transmission 61 of the second embodiment is configured by two transmissions, and one of the two transmissions is driven between the A1 rotor 24 and the drive wheels DW and DW, and the other is driven by the B2 rotor 35 and It may be respectively provided between the rings DW and DW.
- the transmission 91 of the fifth embodiment is configured of two transmissions, and one of the two transmissions is between the A2 rotor 25 and the crankshaft 3a, and the other is the B1 rotor 34 and the crankshaft 3a. May be provided respectively.
- a brake mechanism BL may be provided to prevent reverse rotation of the crankshaft 3a.
- the brake mechanism BL is configured by the one-way clutch OC and the case CA, it may be configured by another mechanism, such as a band brake, as long as the reverse rotation of the crankshaft 3a can be prevented.
- a power plant 1F according to a seventh embodiment will be described with reference to FIG.
- the power plant 1F is different from the power plant 1 according to the first embodiment in that the second rotary machine 31 is a general single pinion type first planetary gear unit PS1 and a general single rotor type rotary machine 101.
- the second rotary machine 31 is a general single pinion type first planetary gear unit PS1 and a general single rotor type rotary machine 101.
- the same components as in the first embodiment are indicated using the same reference numerals. The same applies to the other embodiments described later.
- differences from the first embodiment will be mainly described.
- the first planetary gear unit PS1 includes a first sun gear S1, a first ring gear R1 provided on the outer periphery of the first sun gear S1, and a plurality (for example, three) meshing with both gears S1 and R1.
- a first planetary gear P1 (only two are shown), and a first carrier C1 rotatably supporting the first planetary gear P1.
- first planetary gear ratio r1 The ratio of the number of teeth of the first sun gear S1 to the number of teeth of the first ring gear R1 (number of teeth of the first sun gear S1 / number of teeth of the first ring gear R1, hereinafter referred to as “first planetary gear ratio r1”) is 1
- the value is set to a predetermined value slightly smaller than .0, and is set to a relatively large value that can be taken by a general planetary gear device.
- the first sun gear S1 described above is mechanically coupled directly to the A2 rotor 25 via the first rotation shaft 4 and mechanically coupled directly to the crankshaft 3a via the first rotation shaft 4 and the flywheel 5.
- the first carrier C1 is mechanically directly connected to the A1 rotor 24 through the connecting shaft 6, and the second rotating shaft 7, the gear 7b, the first gear 8b, the idler shaft 8, and the second gear 8c, It is mechanically coupled to the drive wheels DW and DW via the gear 9a, the differential gear mechanism 9 and the like. That is, the A1 rotor 24 and the first carrier C1 are mechanically connected to the drive wheels DW and DW.
- the first planetary gear unit PS1 has the same known function as a general planetary gear unit due to its configuration. That is, the function of distributing the power input to the first carrier C1 to the first sun gear S1 and the first ring gear R1 when the rotational directions of the first sun gear S1, the first ring gear R1 and the first carrier C1 are the same. And the function of combining the power input to the first sun gear S1 and the first ring gear R1 and outputting the combined power to the first carrier C1. In addition, during such power distribution / synthesis, the first sun gear S1, the first ring gear R1 and the first carrier C1 rotate while maintaining a collinear relationship with respect to the rotational speed.
- the rotating machine 101 is a three-phase brushless DC motor, and has a stator 102 composed of a plurality of coils and the like, and a rotor 103 composed of magnets and the like.
- the rotating machine 101 also has a function of converting the power supplied to the stator 102 into motive power and outputting the power to the rotor 103 and a function of converting the power input to the rotor 103 into power and outputting the power to the stator ing.
- the rotor 103 is provided integrally with the first ring gear R1 and is rotatable with the first ring gear R1.
- the stator 102 is electrically connected to the battery 43 via the second PDU 42. That is, the stator 23 of the first rotating machine 21 and the stator 102 of the rotating machine 101 are electrically connected to each other via the first and second PDUs 41 and 42.
- FIG. 59 is a conceptual diagram showing an example of a schematic configuration of a power plant 1F and a transmission state of power.
- the first rotating machine 21 is the “first rotating machine”
- the stator 23 is the “first stator”
- the A1 rotor 24 is the “first rotor”
- the A2 rotor 25 is the “second rotor”
- the planetary gear unit PS1 is “differential”
- the first sun gear S1 is “first element”
- the first carrier C1 is “second element”
- the first ring gear R1 is “third element”
- the rotating machine 101 is “first
- the engine 3 is represented as a “heat engine”, the drive wheels DW, DW as a “driven part”, the first PDU 41 as a “first controller”, and the second PDU 42 as a “second controller” .
- the differential has the same function as the planetary gear. Furthermore, the first rotor and the second element of the differential are mechanically coupled to the driven portion, and the second rotor and the first element of the differential are mechanically coupled to the first output of the heat engine. Also, the third element of the differential is mechanically coupled to the second output of the second rotating machine, and the stator and the second rotating machine are electrically connected to each other via the first and second controllers. It is connected to the.
- the power of the heat engine is transmitted to the driven portion, for example, as follows.
- a power unit in which the second rotor and the first element are connected to the first output portion of the heat engine and the first rotor and the second element are connected to the driven portion is referred to as "first power device”.
- a power plant in which the first rotor and the second element are connected to the first output of the heat engine and the second rotor and the first element are connected to the driven part is referred to as a "second power plant”.
- transmission of power from the heat engine to the driven part in these first and second power plants will be described in order from the first power plant.
- FIG. 59 as in FIG.
- the mechanical connection is indicated by a solid line
- the electrical connection is indicated by an alternate long and short dashed line
- the magnetic connection is indicated by a broken line.
- the flow of power and power is indicated by thick lines with arrows.
- the first and second controllers control the power of the heat engine using part of the power of the heat engine to generate power, and 2 Supply to the rotating machine.
- a part of the motive power of the heat engine is transmitted to the second rotor connected to the first output portion of the heat engine, and further, The magnetic force is distributed to the first rotor and the stator.
- the stator a portion of the power transmitted to the second rotor is converted to electric power and distributed.
- the power distributed to the first rotor as described above is transmitted to the driven part, while the power distributed to the stator is supplied to the second rotating machine.
- the electric power generated by the first rotating machine as described above is supplied to the second rotating machine, the electric power is converted to a power and then transmitted to the third element. Also, the remainder of the power of the heat engine is transmitted to the first element, combined with the power transmitted to the third element as described above, and then transmitted to the driven part via the second element. As a result of the above, power having a magnitude equal to that of the heat engine is transmitted to the driven part.
- the first power unit 1F of this embodiment as in the power unit 1 of the first embodiment, a device in which the first rotating machine is a combination of a planetary gear unit and a general one-rotor type rotating machine Because it has the same function, only one differential for the same purpose is required, unlike the conventional power unit described above, which required two planetary gear units to distribute, combine and transmit power. Therefore, the first power unit can be miniaturized accordingly. The same applies to the second power unit described above. Further, in the first power unit, unlike the conventional case described above, since the power of the heat engine is transmitted to the driven portion without recirculation as described above, the first rotating machine, the differential and the second The power passing through the rotating machine can be reduced.
- the power of the heat engine is a second rotor, a magnetic force by magnetic lines and a first transmission path consisting of the first rotor, a second rotor, a magnetic force by magnetic lines, a stator, a first controller, a second controller, a second rotation To the driven part in a divided state via a total of three transmission paths of the second transmission path consisting of the third element and the second element and the third transmission path consisting of the first and second elements It is transmitted.
- the power (energy) passing through the first and second controllers via the second transmission path can be reduced, so that miniaturization and cost reduction of the first and second controllers can be achieved. Thereby, further miniaturization and cost reduction of the first power plant can be achieved.
- the first and second controllers control the rotational speed of the rotating magnetic field of the stator and the rotational speed of the second output of the second rotating machine, respectively.
- the power of the heat engine can be steplessly shifted and transmitted to the driven part.
- the rotating magnetic field and the first and second rotors are given by the equation (25) during energy distribution and combination between the stator and the first and second rotors. It rotates, maintaining the collinear relationship regarding the rotational speed as shown in 2.).
- the first to third elements rotate while maintaining a collinear relationship regarding the rotational speed. Furthermore, in the connection relationship described above, when the second rotor and the first element are directly connected to the first output of the heat engine, the rotational speeds of both the second rotor and the first element are the same as those of the heat engine Equal to the rotational speed of one output. In addition, when the first rotor and the second element are directly connected to the driven part, the rotational speeds of the first rotor and the second element are both equal to the speed of the driven part. Furthermore, when the second output of the second rotating machine and the third element are directly connected to each other, the rotational speeds of the second rotating machine and the third element are equal to each other.
- the rotational speed of the first output portion of the heat engine is referred to as “the rotational speed of the heat engine”
- the rotational speed of the second output portion of the second rotating machine is referred to as the “rotational speed of the second rotating machine”.
- the rotational speed of the rotating magnetic field is “magnetic field rotational speed VF”
- the rotational speeds of the first and second rotors are “first and second rotor rotational speeds VR1, VR2”, respectively.
- Let the rotational speeds of the elements be “first to third element rotational speeds V1 to V3”, respectively.
- the magnetic field rotational speed VF is increased with respect to the second rotor rotational speed VR2 and the first element rotational speed V1, and the rotational speed of the second rotating machine is increased.
- the power of the heat engine can be decelerated steplessly and transmitted to the driven part.
- the magnetic field rotational speed VF is decreased with respect to the second rotor rotational speed VR2 and the first element rotational speed V1, and the rotational speed of the second rotating machine is increased.
- the power of the heat engine can be steplessly accelerated and transmitted to the driven part.
- the magnetic field rotational speed VF is The speed may be higher than the speed of the heat engine and may be excessive. Therefore, by setting the pole-to-log ratio ⁇ of the first rotating machine to a smaller value, as apparent from the comparison between the velocity alignment graph shown by a broken line in FIG. 60 and the velocity alignment graph shown by a two-dot chain line, The magnetic field rotational speed VF can be reduced, thereby preventing the reduction of the driving efficiency due to the occurrence of the loss due to the increase of the magnetic field rotational speed VF.
- the collinear relationship regarding the rotational speeds of the first to third elements in the differential device can be determined by the difference between the rotational speeds of the first and second elements and the rotational speeds of the second and third elements.
- the rotational speed of the second rotating machine may be higher than the speed of the driven part and may be excessive. Therefore, by setting the above value X to a smaller value, the rotation of the second rotating machine is apparent as apparent from the comparison between the velocity alignment chart shown by the broken line in FIG. 60 and the velocity alignment chart shown by the one-dot chain line. The speed can be reduced, which can prevent the reduction of the driving efficiency due to the occurrence of the loss due to the increase of the rotational speed of the second rotating machine.
- torque is output to the second output portion of the second rotating machine by supplying electric power to the second rotating machine and generating electric power by the first stator (hereinafter referred to as “second rotating machine torque Can be transmitted to the driven unit in a state where the first output unit of the heat engine is stopped with the equivalent torque for power generation of the first rotating machine described above as a reaction force, thereby driving the driven unit.
- second rotating machine torque Can be transmitted to the driven unit in a state where the first output unit of the heat engine is stopped with the equivalent torque for power generation of the first rotating machine described above as a reaction force, thereby driving the driven unit.
- the heat engine is an internal combustion engine.
- FIG. 61 shows the relationship between the torques of various rotating elements in this case, as well as the relationship between the rotational speeds.
- TOUT is the driven portion transmission torque as in the first aspect
- TDHE, Tg and TM2 are torques transmitted to the first output portion of the heat engine (hereinafter referred to as "heat engine transmission torque” ), Power generation equivalent torque and second rotating machine torque.
- the second rotary machine torque TM2 uses the equivalent torque Tg for power generation of the first rotary machine as a reaction force to be driven and the heat engine
- Tg the torque required of the first rotating machine
- the power generation equivalent torque Tg is expressed by the following equation (54).
- Tg ⁇ ⁇ X ⁇ TOUT + (X + 1) TDHE ⁇ / ( ⁇ + 1 + X) (54)
- the equivalent torque Tg for power generation is smaller for the driven part transmission torque TOUT and the heat engine transmission torque TDHE of the same magnitude. It becomes smaller. Therefore, by setting the pole-to-log ratio ⁇ to a larger value, it is possible to achieve further downsizing and cost reduction of the first rotating machine.
- the speed of the low speed driven part can be rapidly increased by controlling the heat engine and the first and second rotating machines as follows.
- FIG. 62 shows the relationship between the rotational speeds of the various types of rotary elements at the start of the case where the speed of the driven part is thus rapidly increased, as well as the relationship between the torques of the various types of rotary elements.
- TEE is the torque of the heat engine
- Te is the equivalent torque for driving the first rotating machine described above.
- the rotational speed of the heat engine is increased to a predetermined rotational speed at which the maximum torque can be obtained. As shown in FIG.
- the rotational speed of the heat engine becomes higher than the speed of the driven part, and the difference between the two becomes large.
- the second output of is reversed.
- power is generated in the second rotating machine in order to apply a positive torque to the driven portion from the second output portion of the second rotating machine which reverses in such a manner.
- the electric power generated by the second rotating machine is supplied to the stator of the first rotating machine, and the rotating magnetic field generated by the stator is rotated forward.
- the torque THE of the heat engine, the equivalent torque Te for driving, and the second rotating machine torque TM2 are all transmitted to the driven portion as positive torque, and as a result, the speed of the driven portion is rapidly increased.
- the torque THE of the heat engine and the equivalent torque Te for driving the second rotary machine torque TM2 Since the torque is transmitted to the driven part as a reaction force, the torque required of the second rotating machine is larger than in the other cases.
- the torque required for the second rotating machine, that is, the second rotating machine torque TM2 is expressed by the following equation (55).
- TM2 - ⁇ ⁇ THE + (1 + ⁇ ) TOUT ⁇ / (X + 1 + ⁇ ) (55)
- the second rotary machine torque TM2 decreases with respect to the driven portion transmission torque TOUT and the heat engine torque THE of the same magnitude as the value X increases. Therefore, by setting the value X to a larger value, the second rotary machine can be further miniaturized and the cost can be reduced.
- FIG. 63 schematically shows an example of a transmission state of power from the heat engine to the driven portion in the second power unit described above.
- the method of description of the connection relation of the various rotation elements in the same figure, etc. is the same as FIG.
- the power of the heat engine is transmitted to the driven portion, for example, as follows. That is, under the control of the first and second controllers, power is generated by the second rotating machine using a part of the power of the heat engine, and the generated power is supplied to the stator of the first rotating machine. At the time of power generation by this second rotating machine, as shown in FIG.
- a part of the power of the heat engine is transmitted to the second element connected to the first output of the heat engine, and the first and third Distributed to the elements.
- the power distributed to the first element is transmitted to the driven part, while the power distributed to the third element is transmitted to the second rotating machine and converted to electric power and then supplied to the stator .
- the second power unit since the power of the heat engine is transmitted to the driven portion without recirculation similarly to the first power unit described above, the first rotating machine, the differential unit, and the second power unit The power passing through the two-rotating machine can be reduced. Therefore, it is possible to reduce the size and cost of the first rotating machine, the differential gear and the second rotating machine as well as the first power unit, thereby further reducing the size and cost of the second power unit. Can be achieved, and the driving efficiency of the second power unit can be enhanced. In addition, in the second power unit, the power distribution and combination in the first rotary machine and the differential unit are simply reversed between the first power unit and the second power unit.
- the power of the heat engine is transmitted to the driven portion in a divided state via a total of three transmission paths of the first to third transmission paths described above. Therefore, as with the first power unit, it is possible to miniaturize and reduce the cost of the first and second controllers, thereby achieving further miniaturization and cost reduction of the second power unit. it can.
- the first and second controllers control the magnetic field rotational speed VF and the second rotary machine.
- the power of the heat engine can be continuously transmitted to the driven parts by shifting the power continuously.
- the rotational speed of the heat engine, the speed of the driven portion, the magnetic field rotational speed VF, the first and second rotor rotational speeds VR1 and VR2, and the first to third rotational speeds are indicated, for example, as a thick solid line in FIG.
- the rotational speed of the second rotating machine is increased with respect to the second element rotational speed V2 and the first rotor rotational speed VR1, and the magnetic field rotational speed VF is decreased.
- the power of the heat engine can be decelerated steplessly and transmitted to the driven part.
- the rotational speed of the second rotating machine is decreased with respect to the second element rotational speed V2 and the first rotor rotational speed VR1, and the magnetic field rotational speed VF is increased.
- the power of the heat engine can be steplessly accelerated and transmitted to the driven part.
- the magnetic field rotational speed VF is It may be higher than the speed of the driven part and may be excessive. Therefore, by setting the pole-log ratio ⁇ to a smaller value, as is apparent from the comparison between the velocity alignment chart shown by the broken line in FIG. 64 and the velocity alignment chart shown by the one-dot chain line, It is possible to reduce the drive efficiency by the occurrence of the loss due to the excessive increase of the magnetic field rotational speed VF.
- the rotational speed of the heat engine is higher than the speed of the driven part (see the two-dot chain line in FIG. 64) when the value X defining the collinear relationship regarding the rotational speed in the differential gear described above is relatively large.
- the rotational speed of the second rotating machine may be higher than the rotational speed of the heat engine and may be excessive. Therefore, by setting this value X to a smaller value, it is apparent from the comparison between the velocity alignment chart shown by a broken line in FIG. 64 and the velocity alignment chart shown by a two-dot chain line, the rotation of the second rotating machine.
- the speed can be reduced, which can prevent the reduction of the driving efficiency due to the occurrence of the loss due to the increase of the rotational speed of the second rotating machine.
- the electric power is supplied to the stator of the first rotating machine, and power generation is performed by the second rotating machine to generate the equivalent torque Te for driving the first rotating machine, and the second rotating machine torque TM2.
- the heat engine is an internal combustion engine, it is possible, like the first power plant, to start the internal combustion engine.
- FIG. 65 shows the relationship between the torques of various rotating elements in this case, along with the relationship between the rotational speeds.
- the driving equivalent torque Te takes the second rotary machine torque TM2 as a reaction force, and both of the driven part and the output part of the heat engine Therefore, the torque required for the second rotating machine is larger than in the other cases.
- the torque required for the second rotating machine that is, the second rotating machine torque TM2 is expressed by the following equation (56).
- TM2 - ⁇ ⁇ TOUT + (1 + ⁇ ) TDHE ⁇ / (X + ⁇ + 1) (56)
- the second rotary machine torque TM2 decreases with respect to the driven portion transmission torque TOUT and the heat engine transmission torque TDHE of the same magnitude as the value X is larger. Therefore, by setting the value X to a larger value, the second rotary machine can be further miniaturized and the cost can be reduced.
- FIG. 66 shows the relationship between the rotational speeds of the various types of rotary elements at the start of the case where the speed of the driven part is thus rapidly increased, as well as the relationship between the torques of the various types of rotary elements.
- the rotational speed of the heat engine is increased to a predetermined rotational speed at which the maximum torque can be obtained.
- the rotational speed of the heat engine becomes higher than the speed of the driven part, and the difference between the two becomes larger.
- the direction of rotation of the rotating magnetic field determined by is the reverse direction. For this reason, in order to apply a positive torque from the stator of the first rotating machine that generates such a rotating magnetic field to the driven portion, power is generated in the stator. Furthermore, the electric power generated by the stator is supplied to the second rotating machine, and the second output portion is rotated forward.
- the torque THE of the heat engine, the second rotary machine torque TM2, and the power generation equivalent torque Tg are all transmitted to the driven part as positive torques, and as a result, the speed of the driven part is rapidly increased. .
- the speed of the driven part in the low speed state is rapidly increased as described above, it is apparent from FIG. 66 that the torque THE of the heat engine and the second rotary machine torque TM2 of the first rotary machine Since the electric power generation equivalent torque Tg is transmitted to the driven part as a reaction force, the torque required of the first rotating machine is larger than in the other cases.
- the torque required for the first rotating machine, that is, the power generation equivalent torque Tg is expressed by the following equation (57).
- Tg - ⁇ X ⁇ THE + (1 + X) TOUT ⁇ / ( ⁇ + 1 + X) ... (57)
- the larger the pole pair ratio ⁇ the smaller the power generation equivalent torque Tg with respect to the driven part transmission torque TOUT having the same magnitude and the torque THE of the heat engine. Therefore, by setting the pole-to-log ratio ⁇ to a larger value, it is possible to achieve further downsizing and cost reduction of the first rotating machine.
- the rotation angle sensor 59 is connected to the ECU 2, and the rotation angle sensor 59 detects the rotation angle position of the rotor 103 of the rotating machine 101, and sends the detected signal to the ECU 2. Output.
- the ECU 2 calculates the rotational speed of the rotor 103 (hereinafter referred to as "rotor rotational speed") based on the detection signal. Further, the ECU 2 controls the second PDU 42 based on the detected rotational angle position of the rotor 103 to control the power supplied to the stator 102 of the rotary machine 101, the power generated by the stator 102, and the rotor rotational speed. Do.
- the ECU 2 reads data from the memory 45 that stores various maps and the like that are required when performing the control. Further, the ECU 2 derives the temperature of the battery 43 from the signal detected by the battery temperature sensor 62 attached to the exterior of the battery 43 or its periphery.
- FIG. 68 is a block diagram showing driving force control in a power plant 1F according to a seventh embodiment. Further, FIG. 69 is a velocity alignment chart of a power unit 1F having a 1-collinear 4-element mechanism.
- the ECU 2 acquires a detection signal indicating the accelerator opening degree AP described above and a detection signal indicating the vehicle speed VP.
- the ECU 2 uses the driving force map stored in the memory 45 to derive a driving force (hereinafter referred to as “required driving force”) according to the accelerator opening degree AP and the vehicle speed VP.
- the ECU 2 calculates an output according to the required driving force and the vehicle speed VP (hereinafter referred to as "required output").
- the required output is an output required for the vehicle to travel in accordance with the driver's accelerator pedal operation.
- the ECU 2 acquires information on the remaining capacity (SOC: State of Charge) of the battery 43 from the detection signal representing the current / voltage value input / output to / from the battery 43 described above.
- the ECU 2 determines the ratio of the output of the engine 3 to the required output according to the SOC of the battery 43.
- the ECU 2 uses the ENG operation map stored in the memory 45 to derive an optimum operating point according to the output of the engine 3.
- the ENG operation map is a map based on BSFC (Brake Specific Fuel Consumption) that indicates the fuel consumption rate at each operating point according to the relationship between the shaft rotational speed of the engine 3 and the torque and the output.
- BSFC Brain Specific Fuel Consumption
- the ECU 2 derives the shaft rotational speed of the engine 3 at the optimum operating point (hereinafter referred to as “required ENG shaft rotational speed”). Furthermore, the ECU 2 derives the torque of the engine 3 at the optimal operating point (hereinafter referred to as "ENG required torque").
- the ECU 2 controls the engine 3 to output the ENG required torque.
- the ECU 2 detects the shaft rotational speed of the engine 3.
- the shaft rotation speed of the engine 3 detected at this time is referred to as “the actual ENG shaft rotation speed”.
- the ECU 2 calculates the difference ⁇ rpm between the required ENG axis rotational speed and the actual ENG axis rotational speed.
- the ECU 2 controls the output torque of the first rotating machine 21 such that the difference ⁇ rpm approaches zero.
- the control is performed by regenerative power generation by the stator 23 of the first rotating machine 21.
- the A2 rotor 25 of the first rotating machine 21 receives the torque T12 shown in the alignment chart of FIG. Is added.
- electric energy (regenerative energy) generated by regenerative power generation in the stator 23 of the first rotating machine 21 is sent to the first PDU 41.
- the regenerative energy generated by the stator 23 of the first rotating machine 21 is indicated by a dotted line A.
- the ECU 2 controls the second PDU 42 so that a torque T22 obtained by subtracting the calculated torque T11 from the previously calculated required driving force is added to the first carrier C1 of the first planetary gear apparatus PS1.
- torque is applied to the rotor 103 of the rotating machine 101 (MG2) and is transmitted to the first carrier C1 of the first planetary gear device PS1.
- the alignment chart of FIG. 69 shows the case where the electrical energy is supplied to the stator 102 of the rotating machine 101, and the electrical energy at that time is shown by the dotted line B. At this time, when supplying electrical energy to the rotating machine 101, regenerative energy obtained by regenerative power generation of the first rotating machine 21 may be used.
- the torque T11 is applied to the A1 rotor 24 of the first rotating machine 21, and the torque T22 is applied to the first carrier C1 of the first planetary gear apparatus PS1.
- the A1 rotor 24 of the first rotating machine 21 is connected to the first carrier C1 of the first planetary gear unit PS1 via the connecting shaft 6, and the first carrier C1 of the first planetary gear unit PS1 is the second rotating shaft 7
- the sum of the torque T11 and the torque T22 is added to the drive wheels DW and DW.
- the ECU 2 Since the first sun gear S1 of the first planetary gear unit PS1 is connected to the shaft of the engine 3, the actual ENG shaft rotational speed of the engine 3 is affected by the torque T21. However, even if the actual ENG axis rotation speed changes, the ECU 2 controls the output torque of the first rotating machine 21 so that the difference ⁇ rpm approaches zero. Since the torque T12 changes by the control and the torque T11 generated in the A1 rotor 24 of the first rotating machine 21 also changes, the ECU 2 changes the torque applied to the rotor 103 of the rotating machine 101. At this time, the torque T21 generated by the changed torque also changes.
- the ECU 2 controls the torque generated on the A2 rotor 25 of the first rotating machine 21 so that the engine 3 operates at the optimum operating point, and the required driving force is applied to the drive wheels DW and DW.
- the torque generated in the rotor 103 of the rotating machine 101 is controlled so as to be transmitted.
- the vehicle speed VP is used when deriving the required driving force and when deriving the required output, but instead of the vehicle speed VP, information on the number of revolutions of the axle may be used.
- the power plant 1F only replaces the second rotating machine 31 with the first planetary gear apparatus PS1 and the rotating machine 101, as compared to the power plant 1 of the first embodiment, It has exactly the same function as this power unit 1. Further, in the power plant 1F, the operation in various operation modes such as the EV creep described in the first embodiment is performed in the same manner. In this case, the operation in these operation modes is performed by replacing various parameters (such as the second magnetic field rotational speed VMF2) related to the second rotating machine 31 with various parameters of the corresponding rotating machine 101.
- various parameters such as the second magnetic field rotational speed VMF2
- EV Creep During EV creep, power is supplied from the battery 43 to the stator 102 of the rotating machine 101, and the rotor 103 is rotated forward. Further, the power generated by the stator 23 is generated using power transmitted to the A1 rotor 24 of the first rotating machine 21 as described later, and the generated power is further supplied to the stator 102. Along with this, the torque (hereinafter referred to as "rotating machine torque") output to the rotor 103 of the rotating machine 101 acts to cause the first carrier C1 to rotate normally and acts to reverse the first sun gear S1. Do. Further, part of the torque transmitted to the first carrier C1 is transmitted to the drive wheels DW and DW via the second rotation shaft 7 and the like, whereby the drive wheels DW and DW perform forward rotation.
- rotating machine torque part of the torque transmitted to the first carrier C1 is transmitted to the drive wheels DW and DW via the second rotation shaft 7 and the like, whereby the drive wheels DW and DW perform forward rotation.
- the remainder of the torque transmitted to the first carrier C1 is transmitted to the A1 rotor 24 through the connecting shaft 6, and then, along with the power generation in the stator 23 of the first rotating machine 21, The electric energy is transmitted to E.23.
- the first power-generating equivalent torque TGE1 acts to cause the A2 rotor 25 to rotate in the forward direction.
- the torque transmitted to the A1 rotor 24 is further transmitted to the A2 rotor 25 so as to balance the first power-generating equivalent torque TGE1, and acts to cause the A2 rotor 25 to rotate in the forward direction.
- the electric power supplied to the stator 102 and the electric power generated by the stator 23 are controlled so that the torque for reversing the first sun gear S1 and the torque for rotating the A2 rotor 25 are balanced.
- the coupled A2 rotor 25, the first sun gear S1 and the crankshaft 3a are held stationary.
- the A2 rotor rotational speed VRA2 and the first sun gear rotational speed VSU1 have the value 0, and the engine rotational speed NE also has the value 0.
- the power supplied to stator 102, the power generated by stator 23, the first magnetic field rotational speed VMF1 and the rotor rotational speed are speeds as shown in the above equations (43) and (53), respectively.
- the first carrier rotational speed VCA1 and the A1 rotor rotational speed VRA1 are controlled to be very small so that the relationship is maintained.
- the creep operation with a very small vehicle speed VP is performed.
- the creep operation can be performed by the first rotating machine 21 and the rotating machine 101 while the engine 3 is stopped.
- the first magnetic field rotational speed VMF1 of the first rotational field reversed as described above at the time of EV start Control is performed so as to be 0, and control is performed so as to reduce the rotor rotational speed of the rotor 103 that has been normally rotated. Then, after the first magnetic field rotational speed VMF1 becomes the value 0, power is supplied from the battery 43 to the stator 23 of the first rotating machine 21 in addition to the stator 102 of the rotating machine 101, and is generated by the stator 23. While rotating the first rotating magnetic field forward, the first magnetic field rotational speed VMF1 is increased.
- the electric power is supplied to the stator 102, whereby the torque of the rotating machine 101 is transmitted to the first carrier C1 via the first ring gear R1, and the first sun gear S1 will be described later.
- the torque thus transmitted is transmitted to the first carrier C1. That is, the rotating machine torque and the torque transmitted to the first sun gear S1 are combined and transmitted to the first carrier C1. Further, a part of the torque transmitted to the first carrier C1 is transmitted to the A1 rotor 24 via the connecting shaft 6, and the rest is transmitted to the drive wheels DW and DW via the second rotation shaft 7 or the like. .
- the first drive equivalent torque TSE1 is transmitted to the A2 rotor 25 by supplying electric power from the battery 43 to the stator 23.
- the torque transmitted as described above to the A1 rotor 24 is transmitted to the A2 rotor 25.
- a part of the torque transmitted to the A2 rotor 25 is transmitted to the first sun gear S1 via the first rotation shaft 4, and the rest is transmitted to the crankshaft 3a via the first rotation shaft 4 or the like.
- the crankshaft 3a rotates forward.
- the power supplied to both the stators 102 and 23 is controlled such that the power is sufficiently transmitted to the drive wheels DW and DW and the engine 3.
- the vehicle speed VP is maintained at the value at that time, and the engine speed NE is increased.
- the engine 3 is started by controlling the ignition operation of the fuel injection valve and the spark plug of the engine 3 according to the crank angle position, as in the first embodiment. Further, by controlling the first magnetic field rotational speed VMF1 and the rotor rotational speed, the engine rotational speed NE is controlled to a relatively small value suitable for starting the engine 3.
- FIG. 70 shows an example of the relationship between rotational speeds and torques of various types of rotary elements at the start of ENG start during EV travel.
- VRO and TMOT are respectively the rotor rotational speed and the rotating machine torque of the rotating machine 101.
- the first embodiment since the rotating machine torque TMOT is transmitted to both the drive wheels DW and DW and the crankshaft 3a using the first electric power-generating equivalent torque TGE1 as a reaction force, the first embodiment Similarly, the torque required of the first rotating machine 21 is larger than in the other cases.
- the torque required for the first rotating machine 21, that is, the first power generation equivalent torque TGE1 is expressed by the following equation (60).
- TGE1 ⁇ ⁇ r1 ⁇ TDDW + (1 + r1) TDENG ⁇ / ( ⁇ + 1 + r1) (60)
- the first power generation equivalent torque TGE1 decreases with respect to the drive wheel transmission torque TDDW and the engine transmission torque TDENG having the same magnitude as the first pole pair number ratio ⁇ increases.
- the first power generation equivalent torque TGE1 is smaller than when set to the value less than 1.0. can do.
- ENG traveling operation is performed in the battery input / output zero mode, the assist mode, and the drive charging mode according to the execution conditions described in the first embodiment.
- the power generated by the stator 23 of the first rotating machine 21 is generated using the engine power transmitted to the A2 rotor 25, and the generated power is not charged to the battery 43.
- the stator 102 of 101 is supplied.
- a part of the engine torque TENG is distributed to the stator 23 and the A1 rotor 24 via the A2 rotor 25. Further, the remainder of the engine torque TENG is transmitted to the first sun gear S1 via the first rotation shaft 4.
- the rotating machine torque TMOT and the torque transmitted as described above to the first sun gear S1 are combined and transmitted to the first carrier C1. Further, the engine torque TENG distributed to the A1 rotor 24 as described above is further transmitted to the first carrier C1 via the connecting shaft 6.
- the A2 rotor rotational speed VRA2 and the first sun gear rotational speed VSU1, ie, the engine rotation, are maintained while maintaining the speed relationship shown in the equations (43) and (53).
- the A1 rotor rotational speed VRA1 and the first carrier rotational speed VCA1, that is, the vehicle speed VP is continuously reduced steplessly by increasing the first magnetic field rotational speed VMF1 and decreasing the rotor rotational speed VRO with respect to the number NE. Can.
- the first magnetic field rotational speed VMF1 is decreased with respect to the engine rotational speed NE, and the rotor rotational speed VRO is increased to increase the vehicle speed VP steplessly. can do. Furthermore, in this case, the first magnetic field rotational speed VMF1 and the rotor rotational speed VRO are controlled such that the engine rotational speed NE becomes the target rotational speed.
- First transmission path A2 rotor 25 ⁇ magnetic force by magnetic line of force ML ⁇ A1 rotor 24 ⁇ connecting shaft 6 ⁇ first carrier C1
- Second transmission path first sun gear S1 ⁇ first planetary gear P1 ⁇ first carrier C1
- Third transmission path A2 rotor 25 ⁇ magnetic force by magnetic line of force ML ⁇ stator 23 ⁇ first PDU 41 ⁇ second PDU 42 ⁇ rotating machine 101 ⁇ first ring gear R1 ⁇ first planetary gear P1 ⁇ first carrier C1
- engine power is transmitted to the drive wheels DW and DW by a magnetic path and a so-called mechanical path by meshing of gears without being converted to electric power.
- the electric power generated by the stator 23, the first magnetic field rotational speed VMF1 and the rotor rotational speed VRO are controlled such that the speed relationship shown in the equations (43) and (53) is maintained. Be done.
- the power generated by the stator 23 is generated using the engine motive power transmitted to the A2 rotor 25, and the electric power stored in the battery 43 is added to the generated electric power.
- the stator 102 is supplied. Therefore, the rotating machine torque TMOT based on the power supplied from the stator 23 and the battery 43 to the stator 102 is transmitted to the first carrier C1. Furthermore, as in the battery input / output zero mode described above, this rotating machine torque TMOT, the engine torque TENG distributed to the A1 rotor 24 with the power generation by the stator 23, and the engine torque TENG transmitted to the first sun gear S1. And the torque obtained by combining the above is transmitted to the drive wheels DW and DW via the first carrier C1. As a result of the above, assuming that there is no transmission loss due to each gear in the assist mode, the power transmitted to the drive wheels DW and DW is the engine power and the electric power supplied from the battery 43 as in the first embodiment. Equal to the energy).
- the electric power generated by the stator 23, the electric power supplied from the battery 43 to the stator 102, and the first magnetic field rotational speed VMF1 and the rotor rotational speed VRO are expressed by Equations (43) and (53). It is controlled to maintain the indicated speed relationship.
- the shortage of the engine power with respect to the vehicle required power is compensated by supplying power from the battery 43 to the stator 102.
- power is also supplied from the battery 43 to the stator 23 of the first rotary machine 21 when the shortage of engine power with respect to the vehicle required power is relatively large.
- the stator 102 of the rotating machine 101 is supplied with electric power of a size obtained by subtracting the electric power charged to the battery 43 from the electric power generated by the stator 23 of the first rotating machine 21
- the rotary machine torque TMOT based on is transmitted to the first carrier C1.
- the rotating machine torque TMOT, the engine torque TENG distributed to the A1 rotor 24 along with the power generation by the stator 23, and the engine torque TENG transmitted to the first sun gear S1 The combined torque is transmitted to the drive wheels DW and DW via the first carrier C1.
- the electric power generated by the stator 23, the electric power charged to the battery 43, the first magnetic field rotational speed VMF1 and the rotor rotational speed VRO are expressed by equations (43) and (53).
- the speed relationship is controlled to be maintained.
- the surplus of the engine power with respect to the vehicle required power is converted to electric power in the stator 23 of the first rotating machine 21 and the battery 43 is charged.
- FIG. 72 shows an example of the relationship between rotational speeds and torques of various types of rotary elements at the start of a sudden acceleration operation during ENG travel.
- the engine rotational speed NE is increased to a predetermined rotational speed at which the maximum torque can be obtained.
- the engine speed NE becomes higher than the vehicle speed VP, and the difference between the both increases, so the rotor 103 of the rotating machine 101 reverses. .
- Power is generated in the stator 102 in order to apply positive torque to the drive wheels DW and DW from the rotor 103 that reverses in such a manner. Furthermore, the electric power generated by the stator 102 is supplied to the stator 23 of the first rotating machine 21 to rotate the first rotating magnetic field forward.
- the rotary machine torque TMOT decreases with respect to the drive wheel transmission torque TDDW and the engine torque TENG of the same magnitude as the first planetary gear ratio r1 increases.
- the rotating machine torque TMOT is more than that set to a small value. It can be made smaller.
- stop ENG During stop ENG, the power is supplied from the battery 43 to the stator 23 of the first rotating machine 21 and the first rotating magnetic field generated by the stator 23 is made to forward rotate accordingly, and the rotating machine 101 Is generated by the stator 102, and the generated power is further supplied to the stator 23.
- the first driving equivalent torque TSE1 from the stator 23 acts to cause the A2 rotor 25 to rotate in the normal direction, and the A1 rotor Act to reverse 24. Further, part of the torque transmitted to the A2 rotor 25 is transmitted to the crankshaft 3a, whereby the crankshaft 3a performs normal rotation.
- the remaining torque transmitted to the A2 rotor 25 is transmitted to the first sun gear S1, and thereafter, along with the power generation in the stator 102 of the rotary machine 101, the first planetary gear P1, the first Electric energy is transmitted to the stator 102 through the ring gear R1 and the rotor 103.
- the crankshaft 3a is normally rotated as described above, so the rotor 103 is reversely rotated.
- the rotating machine torque TMOT generated along with the power generation in the stator 102 is transmitted to the first carrier C1 via the first ring gear R1, and acts to cause the first carrier C1 to rotate normally.
- the torque transmitted to the first sun gear S1 is further transmitted to the first carrier C1 so as to balance the rotating machine torque TMOT, and acts to rotate the first carrier C1 forward.
- the A1 rotor 24, the first carrier C1 and the drive wheels DW and DW connected to each other are held stationary.
- the A1 rotor rotational speed VRA1 and the first carrier rotational speed VCA1 have the value 0, and the vehicle speed VP also has the value 0.
- the speed relationship shown in equations (43) and (53) is maintained such that the power supplied to stator 23, the power generated by stator 102, first magnetic field rotational speed VMF1 and rotor rotational speed VRO And the A2 rotor rotational speed VRA2 and the first sun gear rotational speed VSU1 are controlled to be relatively small values.
- the engine speed NE is controlled to a relatively small value suitable for starting the engine 3 while keeping the vehicle speed VP at 0 as in the first embodiment.
- the engine 3 is started by controlling the ignition operation of the fuel injection valve and the spark plug of the engine 3 according to the crank angle position.
- the stators 23 and 102 generate power. Further, the battery 43 is charged with the power generated by the two stators 23 and 102 as described above. As in the case of the battery input / output zero mode described above, a part of the engine torque TENG is transmitted to the A2 rotor 25 and the engine torque TENG transmitted to the A2 rotor 25 is associated with the power generation by the stator 23 described above , And the stator 23 and the A1 rotor 24. Further, while the vehicle speed VP is substantially 0, since the crankshaft 3a is normally rotated, the rotor 103 of the rotating machine 101 is reversely rotated.
- the rotating machine torque TMOT generated along with the above-described power generation by the stator 102 acts to cause the first carrier C1 to rotate normally, as in the case of the ENG start during stop described above. Further, the engine torque TENG transmitted to the first sun gear S1 is further transmitted to the first carrier C1 so as to balance the rotating machine torque TMOT, and acts to rotate the first carrier C1 forward. Further, the engine torque TENG distributed to the A1 rotor 24 as described above is transmitted to the first carrier C1.
- the first carrier C1 is synthesized by combining the engine torque TENG distributed to the A1 rotor 24, the rotating machine torque TMOT, and the engine torque TENG transmitted to the first sun gear S1. Torque is transmitted. The combined torque is transmitted to the drive wheels DW and DW to cause the drive wheels DW and DW to rotate forward. Further, the electric power generated by the stators 23 and 102, the first magnetic field rotational speed VMF1 and the rotor rotational speed VRO are controlled such that the A1 rotor rotational speed VRA1 and the first carrier rotational speed VCA1, ie, the vehicle speed VP become very small. Thus, the creep operation is performed.
- engine torque TENG distributed to A1 rotor 24 along with power generation by stator 23, and the first sun gear S1 along with power generation by stator 102.
- the engine torque TENG transmitted to the carrier C1 is transmitted to the drive wheels DW and DW.
- a part of the engine torque TENG can be transmitted to the drive wheels DW and DW, so creep operation can be performed without causing engine stall.
- the rotor rotational speed VRO of the rotor 103 reversely rotated during ENG creep is controlled to be 0, and the first magnetic field rotational speed VMF1 of the first rotational magnetic field rotated forward is While raising it, increase engine power. Then, after the rotor rotational speed VRO reaches the value 0, the operation in the above-described battery input / output zero mode is performed. Thus, the vehicle speed VP is increased and the vehicle is started.
- EV Reverse Start At the time of EV reverse start, power is supplied from the battery 43 to both the stator 102 of the rotating machine 101 and the stator 23 of the first rotating machine 21. As a result, the first rotating magnetic field generated by the stator 23 is rotated forward, and the second rotating magnetic field generated by the stator 102 is rotated forward. While the electric power is supplied to the stator 23 of the first rotating machine 21 during the EV reverse start, the first driving equivalent torque from the stator 23 acts to cause the A2 rotor 25 to rotate normally, and the A1 rotor Act to reverse 24.
- the second driving equivalent torque TSE2 from the stator 102 acts to reverse the first carrier C1 of the first planetary gear device PS1.
- the first sun gear S1 of the first planetary gear unit PS1 is rotated in the forward direction.
- the vehicle speed VP increases in the negative direction, and the vehicle starts to move backward.
- the first rotating machine 21 has the same function as a device combining the planetary gear device and a general one-rotor type rotating machine, unlike the conventional power unit described above
- the engine power is transmitted to the drive wheels DW and DW without recirculation, unlike the conventional case described above.
- the power passing through the rotating machine 21, the first planetary gear device PS1 and the rotating machine 101 can be reduced.
- the first rotating machine 21 the first planetary gear unit PS1, and the rotating machine 101 can be achieved, thereby achieving further downsizing and cost reduction of the power plant 1F. it can. Furthermore, by using the first rotating machine 21, the first planetary gear unit PS1 and the rotating machine 101 having torque capacities commensurate with the reduced power as described above, the loss of power is suppressed, and the driving of the power unit 1F Efficiency can be improved.
- engine power is obtained from the first transmission path (A2 rotor 25, magnetic force by magnetic line of force ML, A1 rotor 24, connecting shaft 6, first carrier C1) and the second transmission path (first sun gear S1, first planetary gear P1, The first carrier C1) and the third transmission path (A2 rotor 25, magnetic force by magnetic line of force ML, stator 23, first PDU 41, second PDU 42, rotating machine 101, first ring gear R1, first planetary gear P1, first carrier C1) It is transmitted to the drive wheels DW and DW in a divided state via a total of three transmission paths.
- the power (energy) passing through the first and second PDUs 41 and 42 via the third transmission path can be reduced, and therefore, downsizing and cost reduction of the first and second PDUs 41 and 42 can be achieved.
- further downsizing and cost reduction of the power plant 1F can be achieved.
- the drive wheels DW and DW can be driven while controlling the engine power. Therefore, the driving efficiency of the power plant 1F can be further enhanced.
- the first pole-log ratio ⁇ of the first rotating machine 21 is set to the value 2.0.
- the first pole pair ratio ⁇ has a value of 1.2.
- the first power generation equivalent torque TGE1 can be made smaller than when it is set to less than 0, and therefore, further downsizing and cost reduction of the first rotating machine 21 can be achieved.
- the first planetary gear ratio r1 of the first planetary gear set PS1 is set to a relatively large value that can be taken by a general planetary gear set.
- the first planetary gear ratio r1 is small.
- the rotary machine torque TMOT can be made smaller than when it is set to the value, and therefore, the rotary machine 101 can be further miniaturized and the cost can be reduced.
- the effect of the first embodiment can be obtained similarly.
- the power plant 1F of this embodiment performs the same control as "control according to the battery SOC" performed by the power plant 1 of the first embodiment.
- the second rotating machine 31 of the first embodiment is replaced with the first planetary gear device PS1 and the rotating machine 101 of one rotor type. Therefore, the second rotating machine 31 is replaced with the rotating machine 101, the stator 33 of the second rotating machine 31 is replaced with the stator 102 of the rotating machine 101, and the B2 rotor 35 is replaced with the first carrier C1 of the first planetary gear unit PS1. .
- power plants 1G, 1H, 1I, 1J, and 1K according to eighth to twelfth embodiments will be described with reference to FIGS. 73 to 77.
- These power units 1G to 1K are mainly different from the seventh embodiment in that they further include transmissions 111, 121, 131, 141, and 151, and the eighth to twelfth embodiments are different from the seventh embodiment.
- the connection between the engine 3, the first rotating machine 21, the first planetary gear unit PS1, the rotating machine 101, and the drive wheels DW and DW is the same as that in the seventh embodiment.
- the A2 rotor 25 and the first sun gear S1 are mechanically coupled to the crankshaft 3a of the engine 3, and the A1 rotor 24 and the first carrier C1 are mechanically coupled to the drive wheels DW and DW. Further, the rotor 103 of the rotating machine 101 is mechanically coupled to the first ring gear R1. Further, in FIG. 73 to FIG. 77, the same components as in the seventh embodiment are indicated using the same reference numerals. The same applies to the drawings for explaining the other embodiments described later. Hereinafter, the differences from the seventh embodiment will be mainly described in order from the power plant 1G of the eighth embodiment.
- the transmission 111 is provided instead of the gear 7b and the first gear 8b meshing with each other.
- the transmission 111 is a belt-type continuously variable transmission, and is provided on the input shaft connected to the second rotation shaft 7 described above, the output shaft connected to the idler shaft 8, and the input shaft and the output shaft. And a metal belt (not shown) wound around the pulleys.
- the transmission 111 changes the effective diameter of these pulleys to output the power input to the input shaft to the output shaft in a state of being shifted. Further, the transmission ratio of the transmission 111 (the number of rotations of the input shaft / the number of rotations of the output shaft) is controlled by the ECU 2.
- the transmission 111 is provided between the A1 rotor 24 and the first carrier C1 and the drive wheels DW and DW, and the power transmitted to the A1 rotor 24 and the first carrier C1 is It is shifted by the transmission 111 and transmitted to the drive wheels DW and DW.
- the transmission ratio is controlled to a predetermined value on the deceleration side larger than the value 1.0.
- the torque transmitted to the A1 rotor 24 and the first carrier C1 is transmitted to the drive wheels DW and DW after being increased in the transmission 111.
- the electric power generated by the first rotating machine 21 and the electric power supplied to the rotating machine 101 are controlled such that the torque transmitted to the A1 rotor 24 and the first carrier C1 decreases. Be done.
- the maximum value of the torque required for the first rotating machine 21 and the rotating machine 101 can be reduced, so the further miniaturization and cost of the first rotating machine 21 and the rotating machine 101 can be achieved. Can be reduced.
- the maximum value of the torque transmitted to the first carrier C1 via the first sun gear S1 and the first ring gear R1 can be reduced, the further miniaturization and cost reduction of the first planetary gear device PS1 can be achieved. Can be
- the transmission gear ratio of the transmission 111 is smaller than the value 1.0 when the A1 rotor rotational speed VRA1 becomes excessive. It is controlled to a predetermined value on the speed increasing side.
- the A1 rotor rotational speed VRA1 can be reduced with respect to the vehicle speed VP, it is possible to prevent the failure of the first rotating machine 21 due to the excessive A1 rotor rotational speed VRA1. it can.
- the A1 rotor 24 is made of a magnet, and the magnet is lower in strength than the soft magnetic body, and is thus particularly effective because the above-mentioned problems are likely to occur.
- the transmission gear ratio of the transmission 111 is a value 1 It is controlled to a predetermined value on the speed increasing side smaller than 0.
- the transmission gear ratio of the transmission 111 is controlled such that the first magnetic field rotational speed VMF1 and the rotor rotational speed VRO become predetermined first and second target values, respectively.
- These first and second target values are calculated by searching a map according to the vehicle speed VP when only the first rotating machine 21 and the rotating machine 101 are used as a power source, and the engine 3 and the first rotating machine are calculated.
- calculation is performed by searching another map than the above according to the engine speed NE and the vehicle speed VP.
- the first and second target values are such that high efficiency of the first rotating machine 21 and the rotating machine 101 can be obtained with respect to the vehicle speed VP (and the engine speed NE) at that time. It is set to a value. Furthermore, in parallel with such control of the transmission 111, the first magnetic field rotational speed VMF1 and the rotor rotational speed VRO are controlled to the first and second target values, respectively. As described above, according to the present embodiment, high efficiency of the first rotating machine 21 and the rotating machine 101 can be obtained while the vehicle is traveling.
- the engine power is continuously shifted by the first rotating machine 21, the first planetary gear unit PS1, and the rotating machine 101 to drive the drive wheels DW, Since it can be transmitted to the DW, the frequency of the shift operation of the transmission 111 can be reduced. Therefore, the heat loss due to the speed change operation can be suppressed, whereby the high drive efficiency of the power plant 1G can be secured.
- the effects of the seventh embodiment can be obtained similarly.
- the transmission 111 is a belt-type continuously variable transmission, it goes without saying that it may be a toroidal or hydraulic-type continuously variable transmission or a gear-type stepped transmission. .
- the number of teeth of the gear 9a of the differential gear mechanism 9 described above is larger than the number of teeth of the second gear 8c of the idler shaft 8, whereby the power transmitted to the idler shaft 8 is reduced. In the state, it is transmitted to the drive wheels DW and DW.
- the engine torque TENG transmitted to the A1 rotor 24 and the first carrier C1 is transmitted to the drive wheels DW and DW in a state increased by deceleration by the second gear 8c and the gear 9a.
- the maximum value of the torque required of the first rotating machine 21 and the rotating machine 101 can be reduced, and the size and cost of the first rotating machine 21 and the rotating machine 101 can be further reduced. It is possible to reduce.
- the maximum value of the torque transmitted to the first carrier C1 via the first sun gear S1 and the first ring gear R1 can be reduced, the further miniaturization and cost reduction of the first planetary gear device PS1 can be achieved. Can be
- the A2 rotor rotational speed VRA2 can be made smaller than when the shift position is the second speed, the failure of the first rotating machine 21 due to the excessive A2 rotor rotational speed VRA2 It can be prevented.
- the shift position of the transmission 121 is controlled to the second speed.
- the rotor rotational speed VRO can be reduced. It is possible to prevent the failure of the rotating machine 101 due to the excessive increase of the rotational speed VRO.
- the speed position of the transmission 121 is such that the first magnetic field rotational speed VMF1 and the rotor rotational speed VRO are respectively high efficiency of the first rotating machine 21 and the rotating machine 101 according to the engine speed NE and the vehicle speed VP. It is changed to become a value that can be obtained. Further, in parallel with the change of the gear position of the transmission 121, the first magnetic field rotational speed VMF1 and the rotor rotational speed VRO are the engine rotational speed NE, the vehicle speed VP, the gear position of the transmission 121, It is controlled to a value determined by equations (43) and (53). Thereby, according to the present embodiment, high efficiency of the first rotating machine 21 and the rotating machine 101 can be obtained while the vehicle is traveling.
- shift shock control In addition, in order to suppress a shift shock, during ENG traveling and during the shift operation of the transmission 121, that is, when the transmission 121 disconnects between the engine 3 and the A2 rotor 25 and the first sun gear S1.
- the first rotating machine 21 and the rotating machine 101 are controlled as follows. Hereinafter, such control of the first rotating machine 21 and the rotating machine 101 is referred to as "shift shock control”.
- the present embodiment it is possible to suppress the shift shock due to the fact that the engine torque TENG is not transmitted to the drive wheels DW and DW during the shift operation, and to improve the commercial property. Note that this shift shock control is performed only during the shift operation of the transmission 121. In addition, according to the present embodiment, the effects of the seventh embodiment can be obtained similarly.
- the transmission 131 is a gear type stepped transmission, and has a plurality of gears whose gear ratios are different from the input shaft 132 and the output shaft (not shown). It has a clutch (all not shown) for connecting and disconnecting between the trains and the plurality of gear trains and the input shaft 132 and the output shaft for each gear train.
- the transmission 131 outputs the power input to the input shaft 132 to the output shaft in a state of being shifted by one of the plurality of gear trains.
- a total of four gear stages are set, each of which comprises 1.0) and the third speed (gear ratio ⁇ 1.0), and one gear stage for reverse, and the change is controlled by the ECU 2.
- the second rotating shaft 7 is not provided, and the A1 rotor 24 is directly connected to the input shaft 132 of the transmission 131, and the output shaft of the transmission 131 Is directly connected to the connecting shaft 6 described above.
- a gear 6b is integrally provided on the connecting shaft 6, and the gear 6b meshes with the first gear 8b described above.
- the A1 rotor 24 is driven via the transmission 131, the connecting shaft 6, the gear 6b, the first gear 8b, the idler shaft 8, the second gear 8c, the gear 9a, the differential gear mechanism 9, and the like. It is mechanically connected to the wheels DW, DW.
- the power transmitted to the A1 rotor 24 is shifted by the transmission 131 and transmitted to the drive wheels DW and DW.
- the first carrier C1 is mechanically connected to the drive wheels DW and DW without the transmission 131 via the connection shaft 6, the gear 6b, the first gear 8b, and the like.
- the rotor 103 of the rotating machine 101 is integrally provided on the rotating shaft 103a, and the rotating shaft 103a is directly connected to the first ring gear R1 via a flange.
- the rotor 103 is mechanically directly connected to the first ring gear R1, and is rotatable integrally with the first ring gear R1.
- the transmission gear of the transmission 131 has the first speed (gear ratio> It is controlled to 1.0).
- the torque transmitted to the A1 rotor 24 is transmitted to the drive wheels DW and DW after being increased in the transmission 131.
- the electric power generated by the first rotating machine 21 is controlled such that the torque transmitted to the A1 rotor 24 is reduced.
- the maximum value of the torque required for the first rotating machine 21 can be reduced, and further downsizing and cost reduction of the first rotating machine 21 can be achieved.
- the shift position of the transmission 131 is controlled to the third speed (gear ratio ⁇ 1.0).
- the A1 rotor rotational speed VRA1 can be reduced with respect to the vehicle speed VP, it is possible to prevent the failure of the first rotating machine 21 due to the excessive A1 rotor rotational speed VRA1. it can.
- the A1 rotor 24 is made of a magnet, and the magnet is lower in strength than the soft magnetic body, and the above-mentioned problems are likely to occur.
- the shift position of the transmission 131 is controlled such that the first magnetic field rotational speed VMF1 becomes a predetermined target value.
- This target value is calculated by searching the map according to the vehicle speed VP when only the first rotating machine 21 and the rotating machine 101 are used as a power source, and the engine 3, the first rotating machine 21 and the rotating machine 101 are powered. When used as a source, it is calculated by searching another map than the above according to the engine speed NE and the vehicle speed VP. Further, in these maps, the target value is set to a value at which high efficiency of the first rotating machine 21 can be obtained with respect to the vehicle speed VP (and the engine speed NE) at that time. Further, in parallel with the control of the transmission 131, the first magnetic field rotational speed VMF1 is controlled to the above-described target value. Thus, according to the present embodiment, high efficiency of the first rotating machine 21 can be obtained while the vehicle is traveling.
- the first rotating machine 21 and the rotating machine 101 are controlled as follows. That is, during the shifting operation of the transmission 131, the A1 rotor 24 is disconnected from the drive wheels DW and DW by the disconnection between the gear train in the transmission 131 and the input shaft 132 and the output shaft, thereby causing the A1 to The load of the drive wheels DW, DW does not act on the rotor 24. For this reason, power generation is not performed in the first rotating machine 21, and power is supplied to the stator 102 of the rotating machine 101 from the battery 43.
- the rotating machine torque TMOT transmitted to the first ring gear R1 and the engine torque TENG transmitted to the first sun gear S1 are synthesized during the gear shift operation of the transmission 131, and the first carrier is generated.
- the first carrier is generated.
- it is transmitted to the drive wheels DW and DW via C1 it is possible to suppress a shift shock due to the fact that the engine torque TENG is not transmitted to the drive wheels DW and DW, and therefore, it is possible to improve the merchantability.
- the engine power can be continuously transmitted to the drive wheels DW and DW by the first rotating machine 21, the first planetary gear unit PS1 and the rotating machine 101, the frequency of the shifting operation of the transmission 131 is reduced.
- the driving efficiency of the power plant 1I can be enhanced.
- the effects of the seventh embodiment can be obtained similarly.
- the second rotating shaft 7 is not provided, and the first gear 8b is integral with the connecting shaft 6. It meshes with a gear 6b provided on the As a result, the A1 rotor 24 and the first carrier C1 transmit the transmission through the connecting shaft 6, the gear 6b, the first gear 8b, the idler shaft 8, the second gear 8c, the gear 9a, the differential gear mechanism 9, and the like. It is mechanically connected to the drive wheels DW and DW without passing through 141.
- the transmission 141 is a gear-type stepped transmission having the first to third speeds, which is configured similarly to the transmission 131 of the tenth embodiment.
- an output shaft 142 directly connected to the first ring gear R1 via the rotary shaft 103a, and the power input to the input shaft is shifted to change the output shaft 142.
- the change of the shift position of the transmission 141 is controlled by the ECU 2.
- the rotor 103 is mechanically coupled to the first ring gear R1 via the transmission 141, and the power of the rotor 103 is shifted by the transmission 141 and transmitted to the first ring gear R1. .
- the gear of the transmission 141 is the first speed (1st It is controlled to gear ratio> 1.0).
- the rotary machine torque TMOT is increased in the transmission 141 and then transmitted to the drive wheels DW and DW via the first ring gear R1 and the first carrier C1.
- the power supplied to the rotating machine 101 is controlled such that the rotating machine torque TMOT is reduced.
- the maximum value of the torque required of the rotating machine 101 can be reduced, and the size reduction and cost reduction of the rotating machine 101 can be achieved.
- the shift position of the transmission 141 is set to the third speed (gear ratio ⁇ 1.0). It is controlled.
- the rotor rotation speed VRO can be reduced relative to the first ring gear rotation speed VRI1 determined by the relationship between the vehicle speed VP and the engine rotation speed NE at that time. It is possible to prevent the failure of the rotating machine 101 due to the excessive
- the shift position of the transmission 141 is controlled such that the rotor rotational speed VRO becomes a predetermined target value.
- This target value is calculated by searching the map according to the vehicle speed VP when only the first rotating machine 21 and the rotating machine 101 are used as a power source, and the engine 3, the first rotating machine 21 and the rotating machine 101 are powered. When used as a source, it is calculated by searching another map than the above according to the engine speed NE and the vehicle speed VP. Further, in these maps, the target value is set to a value such that high efficiency of the rotary machine 101 can be obtained with respect to the vehicle speed VP (and the engine speed NE) at that time. Furthermore, in parallel with such control of the transmission 141, the rotor rotational speed VRO is controlled to the above-mentioned target value. Thereby, according to the present embodiment, high efficiency of the rotating machine 101 can be obtained while the vehicle is traveling.
- the engine power can be transmitted steplessly to the drive wheels DW and DW by the first rotating machine 21, the first planetary gear unit PS1 and the rotating machine 101, the frequency of the shifting operation of the transmission 141 is reduced.
- the driving efficiency of the power plant 1J can be enhanced.
- the effects of the seventh embodiment can be obtained similarly.
- the second rotating shaft 7 is not provided, and the first gear 8b is connected. It meshes with a gear 6 b integrally provided on the shaft 6.
- the transmission 151 is a gear type stepped transmission having the first to third shift speeds, which is configured similarly to the transmission 131 of the tenth embodiment, and is directly connected to the first carrier C1.
- the input shaft 152 and the output shaft (not shown) directly connected to the connecting shaft 6 are provided, and the power input to the input shaft 152 is changed in speed and output to the output shaft. Further, the change of the shift position of the transmission 151 is controlled by the ECU 2.
- the first carrier C1 is mechanically connected to the drive wheels DW and DW via the transmission 151, the connecting shaft 6, the gear 6b, the first gear 8b, etc.
- the power transmitted to the carrier C1 is shifted by the transmission 151 and transmitted to the drive wheels DW and DW.
- the A1 rotor 24 is mechanically connected to the drive wheels DW and DW without the transmission 151 via the connection shaft 6, the gear 6b, the first gear 8b, and the like.
- the rotor 103 is directly connected to the first ring gear R1 via the rotation shaft 103a, and is rotatable in unison with the first ring gear R1.
- the gear position of the transmission 151 is the first It is controlled to the speed (gear ratio> 1.0).
- the torque transmitted to the first carrier C1 is transmitted to the drive wheels DW and DW after being increased in the transmission 151.
- the power supplied to the rotating machine 101 is controlled such that the rotating machine torque TMOT is reduced.
- the maximum value of the torque required of the rotating machine 101 and the maximum value of the torque transmitted to the first carrier C1 can be reduced, and the rotating machine 101 and the first planetary gear Further downsizing and cost reduction of the device PS1 can be achieved.
- the shift position of the transmission 151 is set to the third speed (gear ratio ⁇ 1.0). It is controlled.
- the rotor rotational speed VRO can be reduced, so that the rotor rotation can be achieved. It is possible to prevent the failure of the rotating machine 101 due to the increase of the speed VRO.
- the shift position of the transmission 151 is controlled such that the rotor rotational speed VRO becomes a predetermined target value.
- This target value is calculated by searching the map according to the vehicle speed VP when only the first rotating machine 21 and the rotating machine 101 are used as a power source, and the engine 3, the first rotating machine 21 and the rotating machine 101 are powered. When used as a source, it is calculated by searching another map than the above according to the engine speed NE and the vehicle speed VP. Further, in these maps, the target value is set to a value such that high efficiency of the rotary machine 101 can be obtained with respect to the vehicle speed VP (and the engine speed NE) at that time. Further, in parallel with such control of the transmission 151, the rotor rotational speed VRO is controlled to the above-mentioned target value. Thereby, according to the present embodiment, high efficiency of the rotating machine 101 can be obtained while the vehicle is traveling.
- the seventh embodiment has been described in the seventh embodiment when the ENG travel is in progress and the transmission 151 is operating to shift, that is, when the first transmission C1 and the drive wheels DW and DW are disconnected by the transmission 151.
- a part of the engine torque TENG is transmitted to the drive wheels DW and DW via the A1 rotor 24.
- the engine power can be transmitted steplessly to the drive wheels DW and DW by the first rotating machine 21, the first planetary gear unit PS1 and the rotating machine 101, the frequency of the shifting operation of the transmission 151 is reduced.
- the driving efficiency of the power plant 1K can be enhanced.
- the effects of the seventh embodiment can be obtained similarly.
- the transmissions 121 to 151 are gear-type stepped transmissions, but it goes without saying that belt-type, toroidal-type or hydraulic-type continuously variable transmissions may be used. .
- This power unit 1L mainly includes a transmission that changes the ratio of the speed difference between the rotor rotational speed VRO and the vehicle speed VP to the speed difference between the vehicle speed VP and the engine speed NE compared to the seventh embodiment. It is different.
- differences from the seventh embodiment will be mainly described.
- the second rotating shaft 7 is not provided, and the first gear 8b is mounted on the gear 6b integrally provided on the connecting shaft 6.
- the A1 rotor 24 and the first carrier C1 are engaged via the connecting shaft 6, the gear 6b, the first gear 8b, the differential gear mechanism 9 and the like without using the above-described transmission. It is mechanically connected to the wheels DW, DW. Further, the rotor 103 is rotatable integrally with the rotating shaft 103a, as in the tenth embodiment.
- the above transmission includes the second planetary gear unit PS2, a first clutch CL1, and a second clutch CL2.
- the second planetary gear unit PS2 is configured in the same manner as the first planetary gear unit PS1, and includes a second sun gear S2, a second ring gear R2, and a plurality of (for example, three) second gears engaged with both gears S2 and R2.
- a second carrier C2 rotatably supporting the planetary gear P2 (only two shown) is provided.
- the second sun gear S2 is mechanically directly connected to the first carrier C1 via the rotation shaft, and is thereby rotatable integrally with the first carrier C1.
- the second carrier C2 is mechanically directly coupled to the first ring gear R1 via a hollow shaft or a flange, and is thereby rotatable integrally with the first ring gear R1.
- the rotational speeds of the second sun gear S2, the second ring gear R2 and the second carrier C2 will be referred to as “second sun gear rotational speed VSU2", “second ring gear rotational speed VRI2” and “second carrier rotational speed VCA2".
- the first clutch CL1 is, for example, a friction type multiple disc clutch, and is provided between the second carrier C2 and the rotating shaft 103a. That is, the second carrier C2 is mechanically directly coupled to the rotor 103 via the first clutch CL1. Further, the first clutch CL1 connects and disconnects between the second carrier C2 and the rotary shaft 103a, that is, between the second carrier C2 and the rotor 103, as the degree of engagement is controlled by the ECU 2.
- the above-described second clutch CL2 is configured by a friction type multiple disc clutch, and is provided between the second ring gear R2 and the rotation shaft 103a. That is, the second ring gear R2 is mechanically directly coupled to the rotor 103 via the second clutch CL2. Further, the second clutch CL2 is connected and disconnected between the second ring gear R2 and the rotary shaft 103a, that is, between the second ring gear R2 and the rotor 103, as the degree of engagement is controlled by the ECU 2.
- the rotor 103 of the rotating machine 101 is mechanically coupled to the first ring gear R1 via the first clutch CL1 and the second carrier C2, and the second clutch CL2, the second It is mechanically connected to the first ring gear R1 via the 2 ring gear gear R2, the second planetary gear P2 and the second carrier C2.
- FIG. 79 (a) is a velocity collinear chart showing an example of the relationship between the first sun gear rotation speed VSU1, the first carrier rotation speed VCA1, and the first ring gear rotation speed VRI1, the second sun gear rotation speed VSU2, the second carrier rotation It is shown with a velocity alignment chart showing an example of the relationship between the velocity VCA2 and the second ring gear rotational velocity VRI2.
- r2 is the ratio of the number of teeth of the second sun gear S2 to the number of teeth of the second ring gear R2 (number of teeth of the second sun gear S2 / number of teeth of the second ring gear R2, hereinafter "second planetary gear ratio" ).
- the two velocity alignment charts concerning the first and second planetary gear sets PS1, PS2 in FIG. 79 (a) are represented by one velocity alignment chart as shown in FIG. 79 (b).
- FIG. 79 (b) As shown in the figure, by connecting various rotating elements of the first and second planetary gear units PS1 and PS2 as described above, four rotating elements whose rotational speeds are collinear with each other are formed. .
- FIG. 80 (a) is a velocity collinear chart showing an example of the relationship between the rotational speeds of the four rotating elements described above, in the relationship between the rotor rotational speeds VRA1 and VRA2 of the first magnetic field rotational speeds VMF1, A1 and A2. It has shown with the velocity alignment chart which shows an example. As described above, since the first carrier C1 and the A1 rotor 24 are directly connected to each other, the second carrier rotation speed VCA2 and the A1 rotor rotation speed VRA1 are equal to each other. Further, since the first sun gear S1 and the A2 rotor 25 are directly connected to each other, the first sun gear rotational speed VSU1 and the A2 rotor rotational speed VRA2 are equal to each other. Therefore, the two velocity alignment charts of FIG. 80 (a) are shown as one velocity alignment chart as shown in FIG. 80 (b).
- the crankshaft 3a, the A2 rotor 25 and the first sun gear S1 are directly connected to each other, the engine rotational speed NE, the A2 rotor rotational speed VRA2 and the first sun gear rotational speed VSU1 are equal to each other.
- the drive wheels DW and DW, the A1 rotor 24, the first carrier C1 and the second sun gear S2 are connected to one another, the vehicle speed VP and the A1 rotor rotation are assumed if there is no gear change by the differential gear mechanism 9.
- the speed VRA1, the first carrier rotation speed VCA1, and the second sun gear rotation speed VSU2 are equal to one another.
- the rotor 103 is connected to the second carrier C2 and the second ring gear R2 via the first and second clutches CL1 and CL2, respectively, the first clutch CL1 is connected, and the second clutch CL2 is connected. Is interrupted (hereinafter, such a clutch engagement / disengagement state is referred to as "first transmission mode"), the rotor rotational speed VRO and the second carrier rotational speed VCA2 are equal to each other. Furthermore, when the first clutch CL1 is disconnected and the second clutch CL2 is connected (hereinafter, such a connected / disconnected state of the clutch is referred to as “second shift mode”), the rotor rotational speed VRO and The second ring gear rotational speeds VRI2 are equal to one another.
- the first magnetic field rotational speed VMF1, the engine rotational speed NE, the vehicle speed VP, and the rotor rotational speed VRO become collinear as shown in, for example, FIG. 81 (a) during the first shift mode.
- the second speed change mode for example, a collinear relationship as shown in FIG. 81 (b) is obtained.
- the distance between the vertical line representing the vehicle speed VP and the vertical line representing the rotor rotational speed VRO in the velocity nomograph is the first shift described above. Since the mode is smaller than the second transmission mode, the ratio of the rotational difference DN2 between the rotor rotational speed VRO and the vehicle speed VP to the rotational difference DN1 between the vehicle speed VP and the engine rotational speed NE (hereinafter referred to as "rotational ratio DN2 / DN1”) is smaller in the first shift mode.
- the rotor rotational speed VRO when the rotor rotational speed VRO becomes excessive, such as during high-speed operation where the vehicle speed VP is higher than the engine rotational speed NE or when the vehicle speed VP is high during EV traveling described above
- the first shift mode is used.
- the rotor rotation speed VRO can be made smaller than in the case where the second transmission mode is used. It is possible to prevent the failure of the rotating machine 101 due to the excessive VRO.
- the first and second shift modes are used at the start of a sudden acceleration operation during ENG traveling, that is, when the torque required of the rotating machine 101 becomes large, the rotational speeds of various rotating elements and The relationship between the torques is represented by FIG. 82 (a) and FIG. 82 (b), respectively.
- the torque required of the rotating machine 101 that is, the rotating machine torque TMOT is expressed by the above equation (61).
- the rotating machine torque TMOT is expressed by the following equation (62).
- TMOT - ⁇ TENG + (1 + ⁇ ) TDD W ⁇ / (R1 ⁇ r2 + r1 + 1 + ⁇ ) (62)
- the rotating machine torque TMOT is smaller in the second shift mode than the drive wheel transmission torque TDDW and the engine torque TENG having the same magnitude. .
- the second shift mode is used during a sudden acceleration operation during ENG traveling.
- the rotating machine 101 since the second shift mode is used as described above and the electric power generated by the rotating machine 101 is controlled based on the above-mentioned equation (62), the rotating machine 101 is required.
- the maximum value of the torque can be reduced, which can further reduce the size and cost of the rotating machine 101.
- the vehicle speed VP and the engine rotation during the operation of the engine 3 according to the vehicle speed VP during the stop of the engine 3 among the first and second shift modes.
- a transmission mode is selected, which allows higher efficiency of the rotating machine 101.
- the rotor rotational speed VRO can be controlled to an appropriate height, so that high efficiency of the rotating machine 101 can be obtained.
- switching between the first and second shift modes is performed when the second carrier rotational speed VCA2 and the second ring gear rotational speed VRI2 are equal to each other.
- the switching of the first and second shift modes can be smoothly performed while maintaining the rotation of the drive wheels DW and DW and the engine 3, and good drivability is ensured. be able to.
- the seventh embodiment is described.
- part of the engine torque TENG can be transmitted to the drive wheels DW and DW via the rotors 25 and 24 of A2 and A1. Therefore, since it is possible to suppress a shift shock such as a rapid decrease in torque, it is possible to improve the commercial property.
- the effects of the seventh embodiment can be obtained similarly.
- the second sun gear S2 is coupled to the first carrier C1, and the second ring gear R2 is coupled to the rotor 103 via the second clutch CL2.
- the coupling relationship between them is reversed. That is, the second ring gear R2 may be connected to the first carrier C1, and the second sun gear S2 may be connected to the rotor 103 via the second clutch CL2.
- 1st and 2nd clutch CL1 and CL2 are comprised with the friction type multiple disc clutch, you may comprise with an electromagnetic clutch etc., for example.
- FIGS. 83 (a) and 83 (b) show an example of the relationship between the rotational speeds of various types of rotary elements in the power unit 1L in (a) the first shift mode and (b) the second shift mode. It is a velocity alignment chart.
- the rotating machine 21 is “first rotating machine”
- the rotating machine 101 is “second rotating machine”
- the second sun gear S2 is "one gear” or "first gear”.
- the second ring gear R2 is "the other gear” or “the second gear”
- the second carrier C2 is the “carrier”
- the second output portion is the “rotation shaft 103a”
- the first clutch is the "first clutch CL1”
- the second clutch is represented as “first clutch CL2”
- the engine 3 is represented as “heat engine”
- the drive wheels DW and DW are represented as “driven parts”.
- the rotational speed of one gear of the second planetary gear unit PS2 is "first gear rotational speed VG1”
- the rotational speed of the other gear of the second planetary gear unit PS2 is “second gear rotational speed VG2”.
- the rotational speed of the carrier of the second planetary gear unit PS2 is referred to as "carrier rotational speed VC”.
- the rotary element is directly connected in various ways, and the second output of the second rotary machine is connected to the carrier by connection of the first clutch, and the second output is connected by disconnection of the second clutch.
- the rotational speed of the heat engine and the driven speed of the heat engine are reduced when the motor and the other gear are disconnected (hereinafter, such a connected / disconnected state of the first and second clutches is referred to as "first transmission mode").
- the relationship such as the speed of the part is shown, for example, as shown in FIG. 83 (a).
- the distance from the vertical line representing the first gear rotational speed VG1 to the vertical line representing the carrier rotational speed VC is Y
- the vertical line representing the carrier rotational speed VC is the second gear
- Z be the distance to the vertical line representing the rotational speed VG2.
- the second shift mode is more than the second shift mode. Since the rotational speed of the rotating machine can be reduced, it is possible to prevent the failure of the second rotating machine due to an excessive increase in the rotational speed of the second rotating machine.
- the torque TM2 of the second rotating machine is the second for the driven portion transmission torque TOUT of the same magnitude and the torque THE of the heat engine.
- the shift mode is smaller. Therefore, for example, when the torque required for the second rotating machine is increased as described above, the second rotating machine torque TM2 can be reduced by using the second shift mode, and hence, Further downsizing and cost reduction of the second rotating machine can be achieved.
- the rotational speed of the second rotating machine can be controlled to an appropriate size, thereby , High efficiency of the second rotating machine can be obtained. Furthermore, by switching between the first and second shift modes when the carrier rotational speed VC and the second gear rotational speed VG2 are equal to each other as shown in FIG. 85, the rotation of the driven part or the heat engine is maintained. While, it can be done smoothly and good drivability can be secured.
- the first rotor to the driven part without the aid of a gear-type stepped transmission, so that, at the time of the transition between the first and second transmission modes, Even if the second rotary machine and the driven part are shut off due to both the first and second clutches being shut off, as is clear from FIG. , And can be transmitted to the driven part via the second and first rotors. Therefore, at the time of transition between the first and second shift modes, it is possible to suppress the shift shock, so that the product property can be enhanced.
- a power plant 1M according to a fourteenth embodiment will be described with reference to FIG.
- This power unit 1M is obtained by adding the brake mechanism BL described in the sixth embodiment to the power unit 1F of the seventh embodiment.
- differences from the seventh embodiment will be mainly described.
- the rotation of the first rotary shaft 4 is allowed only by the brake mechanism BL configured of the one-way clutch OC and the case CA, only in the case of normal rotation with the crankshaft 3a, the A2 rotor 25 and the first sun gear S1. And is prevented in the case of reverse rotation with the crankshaft 3a or the like.
- the above-described EV creep operation and operation by EV start are performed as follows. That is, power is supplied to the stator 23 of the first rotating machine 21 and the stator 102 of the rotating machine 101, and the first rotating magnetic field generated by the stator 23 is reversed accordingly, and the rotor 103 is rotated forward together with the first ring gear R1.
- the first magnetic field rotational speed VMF1 and the rotor rotational speed VRO are controlled such that (1 + r1)) VMF1
- the power supplied to the stators 23 and 102 is controlled such that torque is sufficiently transmitted to the drive wheels DW and DW.
- all the power supplied to the stator 23 is transmitted as power to the A1 rotor 24, whereby the A1 rotor 24 rotates forward.
- all the power from the rotating machine 101 is the first ring gear R1 and the first planetary gear P1.
- the power transmitted to the A1 rotor 24 and the first carrier C1 is transmitted to the drive wheels DW and DW, and as a result, the drive wheels DW and DW perform forward rotation.
- the A2 rotor 25 and the first sun gear S1 which are prevented from being reversely rotated by the brake mechanism BL, are respectively controlled from the stator 23 and the rotor 103 by the control of the first rotating machine 21 and the rotating machine 101 described above.
- a torque acts to reverse the torque.
- the crankshaft 3a, the A2 rotor 25 and the first sun gear S1 are not only reversed but also held stationary.
- the drive wheels DW and DW can be driven by the first rotating machine 21 and the rotating machine 101 without using engine power. Further, during this driving, the crankshaft 3a is not only reversed but also kept stationary so that the engine 3 will not be dragged. In addition, the effect by 7th Embodiment can be acquired similarly.
- the first pole-log ratio ⁇ of the first rotating machine 21 is set to the value 2.0 as in the first embodiment.
- the drive efficiency is lowered due to the occurrence of the loss due to the excess of the first magnetic field rotational speed VMF1 Can be prevented.
- the first planetary gear ratio r1 of the first planetary gear unit PS1 is set to a relatively large value, but setting the value to a smaller value provides the following effect. can get.
- the rotor rotational speed VRO is The vehicle speed may be higher than the vehicle speed VP and may be excessive.
- the first planetary gear ratio r1 is set to a relatively large value, when the vehicle speed VP is higher than the engine rotational speed NE (see the alternate long and short dash line in FIG. 71), the rotor rotational speed VRO is The vehicle speed may be higher than the vehicle speed VP and may be excessive.
- the first planetary gear ratio r1 by setting the first planetary gear ratio r1 to a smaller value, as is apparent from the comparison between the velocity alignment chart shown by a broken line in FIG. 71 and the velocity alignment chart shown by a one-dot chain line, The rotational speed VRO can be reduced, and therefore, the reduction of the driving efficiency due to the occurrence of the loss due to the increase of the rotor rotational speed VRO can be prevented.
- the A2 rotor 25 and the first sun gear S1 are directly connected to each other, and the A1 rotor 24 and the first carrier C1 are directly connected to each other.
- the A2 rotor 25 and the first sun gear S1 are Is not required to be directly connected to each other as long as it is connected to the crankshaft 3a, and the A1 rotor 24 and the first carrier C1 are not connected to each other as long as they are connected to the drive wheels DW and DW.
- the transmissions 111 and 121 according to the eighth and ninth embodiments may be two transmissions, respectively, and may be provided as follows.
- one of the two transmissions constituting the transmission 111 may be provided between the A1 rotor 24 and the drive wheels DW and DW, and the other may be provided between the first carrier C1 and the drive wheels DW and DW.
- one of the two transmissions constituting the transmission 121 may be provided between the A2 rotor 25 and the crankshaft 3a, and the other may be provided between the first sun gear S1 and the crankshaft 3a.
- the first sun gear S1 and the first ring gear R1 are connected to the engine 3 and the rotating machine 101, respectively, but the connection relationship between them is reversed, that is, the first ring gear R1 and the first sun gear S1 may be coupled to the engine 3 and the rotating machine 101, respectively.
- the rotating machine torque TMOT is expressed by the following equation (65) during a rapid acceleration operation during ENG traveling in which the torque required of the rotating machine 101 becomes particularly large.
- r1 ' is a ratio of the number of teeth of the first ring gear R1 to the number of teeth of the first sun gear S1 (number of teeth of the first ring gear / number of teeth of the first sun gear S1) Greater than .0.
- the fact that the first planetary gear ratio r1 is the number of teeth of the first sun gear S1 / the number of teeth of the first ring gear R1 as described above, and is smaller than 1.0, and the above equation (61)
- the rotary machine torque TMOT can be made smaller, and therefore, the rotary machine 101 can be further miniaturized and the cost can be reduced.
- a power plant 1N according to a fifteenth embodiment will be described with reference to FIG.
- the power plant 1N is provided with the first planetary gear unit PS1 and the rotary machine 101 described in the seventh embodiment in place of the first rotary machine 21 in comparison with the power plant 1 of the first embodiment. Only the point is different.
- differences from the first embodiment will be mainly described.
- the first carrier C1 of the first planetary gear unit PS1 and the B1 rotor 34 of the second rotating machine 31 are mechanically connected directly to each other via the first rotation shaft 4, and the first rotation It is mechanically directly connected to the crankshaft 3 a via the shaft 4 and the flywheel 5.
- the B2 rotor 35 of the second rotating machine 31 is mechanically directly connected to the first sun gear S1 of the first planetary gear unit PS1 via the connecting shaft 6, and the second rotating shaft 7, the gear 7b, and the It is mechanically connected to the drive wheels DW and DW via the 1 gear 8b, the idler shaft 8, the second gear 8c, the gear 9a, the differential gear mechanism 9 and the like.
- the first sun gears S1 and B2 rotors 35 are mechanically connected to the drive wheels DW and DW.
- the stator 102 is electrically connected to the battery 43 via the first PDU 41. That is, the stator 102 of the rotating machine 101 and the stator 33 of the second rotating machine 31 are electrically connected to each other via the first and second PDUs 41 and 42.
- the rotational angle position of the rotor 103 of the rotating machine 101 is detected by the aforementioned rotational angle sensor 59 as in the seventh embodiment. Further, the ECU 2 calculates the rotor rotational speed VRO based on the detected rotational angle position of the rotor 103, and controls the first PDU 41 to control the power supplied to the stator 102 of the rotating machine 101 or the stator 102. It controls the power to be generated and the rotor rotational speed VRO.
- the power plant 1N only replaces the first rotating machine 21 with the first planetary gear apparatus PS1 and the rotating machine 101, as compared with the power plant 1 of the first embodiment. It has exactly the same function as this power unit 1. Further, in the power unit 1N, operations in various operation modes such as EV creep described in the first embodiment are performed in the same manner. In this case, the operation in these operation modes is performed by replacing various parameters (such as the first magnetic field rotational speed VMF1) related to the first rotating machine 21 with various parameters of the corresponding rotating machine 101.
- various parameters such as the first magnetic field rotational speed VMF1
- the second driving equivalent torque TSE2 from the stator 33 acts to cause the B2 rotor 35 to rotate in the normal direction, and acts to reverse the B1 rotor 34.
- a part of the torque transmitted to the B2 rotor 35 is transmitted to the drive wheels DW and DW via the second rotation shaft 7 and the like, whereby the drive wheels DW and DW perform forward rotation.
- the remainder of the torque transmitted to B2 rotor 35 is transmitted to first sun gear S1 via connecting shaft 6, and thereafter, along with the power generation in stator 102 of rotating machine 101, the first planetary gear Electrical energy is transmitted to the stator 102 through P 1, the first ring gear R 1 and the rotor 103.
- the rotating machine torque TMOT generated along with the power generation in the stator 102 is transmitted to the first carrier C1 via the first ring gear R1 and the first planetary gear P1, 1) Act to rotate the carrier C1 forward.
- the torque transmitted to the first sun gear S1 is further transmitted to the first carrier C1 via the first planetary gear P1 so as to balance the rotating machine torque TMOT, and causes the first carrier C1 to rotate in the forward direction.
- the electric power supplied to the stator 33 and the electric power generated by the stator 102 are controlled so that the torque for reversing the B1 rotor 34 and the torque for rotating the first carrier C1 balance each other.
- the connected B1 rotor 34, the first carrier C1 and the crankshaft 3a are held stationary.
- the B1 rotor rotational speed VRB1 and the first carrier rotational speed VCA1 have the value 0, and the engine rotational speed NE also has the value 0.
- the power supplied to stator 33, the power generated by stator 102, the second magnetic field rotational speed VMF2 and the rotor rotational speed VRO are as shown in the above formulas (44) and (53), respectively.
- the speed relationship is maintained, and the B2 rotor rotational speed VRB2 and the first sun gear rotational speed VSU1 are controlled to be very small.
- the creep operation with a very small vehicle speed VP is performed.
- the creep operation can be performed by the rotating machine 101 and the second rotating machine 31 in a state where the engine 3 is stopped.
- the rotor rotational speed VRO of the rotor 103 which was reverse as described above during EV start, becomes the value 0 while maintaining the vehicle speed VP at the value at that time.
- the second magnetic field rotational speed VMF2 of the second rotating magnetic field which has been normally rotated, is controlled to decrease.
- power is supplied from the battery 43 to the stator 102 of the rotating machine 101 to rotate the rotor 103 forward. , Increase the rotor rotational speed VRO.
- the second driving equivalent torque TSE2 and the torque transmitted to the B1 rotor 34 as described later are combined.
- B2 rotor 35 part of the torque transmitted to the B2 rotor 35 is transmitted to the first sun gear S1 via the connecting shaft 6, and the rest is transmitted to the drive wheels DW and DW via the second rotating shaft 7 or the like. .
- the vehicle speed VP is maintained at the value at that time, and the engine speed NE is increased.
- the engine 3 is started by controlling the ignition operation of the fuel injection valve and the spark plug of the engine 3 according to the crank angle position, as in the first embodiment. Further, by controlling the rotor rotational speed VRO and the second magnetic field rotational speed VMF 2, the engine speed NE is controlled to a relatively small value suitable for starting the engine 3.
- FIG. 88 shows an example of the relationship between rotational speeds and torques of various types of rotary elements at the start of ENG start during EV travel.
- the first carrier rotational speed VCA1, B1 rotor rotational speed VRB1 and engine rotational speed NE are equal to each other, and the first sun gear rotational speed VSU1 and B2 rotor rotational speed VRB2 are mutually Equally, the first ring gear rotational speed VRI1 and the rotor rotational speed VRO are equal to each other.
- the vehicle speed VP, the first sun gear rotational speed VSU1 and the B2 rotor rotational speed VRB2 are equal to one another.
- the relationship between the rotational speeds VCA1, VRB1, NE, VSU1, VRB2, VP, VRI1, and VRO, and the second magnetic field rotational speed VMF2 is shown in FIG. As indicated.
- the second driving equivalent torque TSE2 is transmitted to both the drive wheels DW and DW and the crankshaft 3a using the rotating machine torque TMOT as a reaction force.
- the required torque will be greater than otherwise.
- the torque required for the rotating machine 101 that is, the rotating machine torque TMOT is expressed by the following equation (66).
- the rotary machine torque TMOT decreases with respect to the drive wheel transmission torque TDDW and the engine transmission torque TDENG of the same magnitude as the first planetary gear ratio r1 increases.
- the first planetary gear ratio r1 is set to a relatively large value among values that can be taken by a general planetary gear device, downsizing of the rotating machine 101 and cost reduction can be achieved. .
- ENG traveling operation is performed in the battery input / output zero mode, the assist mode, and the drive charging mode according to the execution conditions described in the first embodiment.
- the second motive power machine 31 generates electric power by the stator 102 of the rotary machine 101 using engine power transmitted to the rotor 103 and does not charge the battery 43 with the generated electric power.
- Supply to the stator 33 of the In this case a part of the engine torque TENG is transmitted to the rotor 103 through the first carrier C1, the first planetary gear P1 and the first ring gear R1 by the power generation by the stator 102, and thus the first sun gear.
- a part of engine torque TENG is also transmitted to S1 via the first carrier C1 and the first planetary gear P1. That is, a part of engine torque TENG is distributed to first sun gear S1 and first ring gear R1.
- the remainder of the engine torque TENG is transmitted to the B1 rotor 34 via the first rotation shaft 4.
- the second drive equivalent torque TSE2 and the torque transmitted to the B1 rotor 34 as described above are synthesized and transmitted to the B2 rotor 35, as in the ENG start-up during the EV traveling described above.
- the engine torque TENG distributed to the first sun gear S1 as described above is further transmitted to the B2 rotor 35 via the connecting shaft 6.
- the B2 rotor 35 has a combined torque that combines the engine torque TENG distributed to the first sun gear S1, the second driving equivalent torque TSE2, and the engine torque TENG transmitted to the B1 rotor 34. It is transmitted. Further, this combined torque is transmitted to the drive wheels DW and DW via the second rotation shaft 7 and the like. As a result of the above, in the battery input / output zero mode, assuming that there is no transmission loss due to each gear, power of the same magnitude as the engine power is transmitted to the drive wheels DW and DW as in the first embodiment. .
- the first carrier rotational speed VCA1 and the B1 rotor rotational speed VRB1 that is, the engine rotation, while maintaining the speed relationship shown in the equations (53) and (44).
- the first sun gear rotation speed VSU1 and the B2 rotor rotation speed VRB2 that is, the vehicle speed VP is continuously reduced steplessly by raising the rotor rotation speed VRO and decreasing the second magnetic field rotation speed VMF2 with respect to the number NE. Can.
- the vehicle speed VP is increased steplessly by decreasing the rotor rotational speed VRO with respect to the engine rotational speed NE and increasing the second magnetic field rotational speed VMF2. can do. Further, in this case, the rotor rotational speed VRO and the second magnetic field rotational speed VMF2 are controlled such that the engine rotational speed NE becomes the target rotational speed.
- the engine power is temporarily divided, and the following first to third transmission paths are The torque is transmitted to the B2 rotor 35 and is transmitted to the drive wheels DW and DW in a combined state.
- First transmission path first carrier C1 ⁇ first planetary gear P1 ⁇ first sun gear S1 ⁇ connecting shaft 6 ⁇ B2 rotor 35
- Second transmission path B1 rotor 34 ⁇ magnetic force by magnetic line of force ⁇ B2 rotor 35
- Third transmission path first carrier C1 ⁇ first planetary gear P1 ⁇ first ring gear R1 ⁇ rotor 103 ⁇ stator 102 ⁇ first PDU 41 ⁇ second PDU 42 ⁇ stator 33 ⁇ magnetic force due to magnetic field lines ⁇ B2 rotor 35
- engine power is transmitted to the drive wheels DW and DW by a magnetic path or a mechanical path without being converted to electric power.
- the engine power is transmitted to the drive wheels DW and DW by the electrical path.
- stator 102 the power generated by stator 102, rotor rotational speed VRO and second magnetic field rotational speed VMF2 are controlled such that the speed relationship shown in equations (53) and (44) is maintained. Ru.
- the assist mode power is generated by the stator 102 of the rotary machine 101, and the power charged in the battery 43 is supplied to the stator 33 of the second rotary machine 31 in addition to the generated power. Therefore, the second driving equivalent torque TSE2 based on the power supplied from the stator 102 and the battery 43 to the stator 33 is transmitted to the B2 rotor 35. Furthermore, similarly to the above-described battery input / output zero mode, the second drive equivalent torque TSE2, the engine torque TENG distributed to the first sun gear S1 along with the power generation by the stator 102, and the B1 rotor 34 are transmitted. The torque obtained by combining the engine torque TENG is transmitted to the drive wheels DW and DW via the B2 rotor 35. As a result of the above, assuming that there is no transmission loss due to each gear in the assist mode, the power transmitted to the drive wheels DW and DW is the engine power and the electric power supplied from the battery 43 as in the first embodiment. Equal to the energy).
- the electric power generated by the stator 102, the electric power supplied from the battery 43 to the stator 33, and the rotor rotational speed VRO and the second magnetic field rotational speed VMF2 are expressed by the above equations (53) and (44). It is controlled to maintain the speed relationship shown in FIG.
- the shortage of the engine power with respect to the vehicle required power is compensated by supplying power from the battery 43 to the stator 33 of the second rotating machine 31.
- power is also supplied from the battery 43 to the stator 102 of the rotating machine 101 when the shortage of engine power with respect to the vehicle required power is relatively large.
- the stator 33 of the second rotating machine 31 is supplied with electric power of a size obtained by subtracting the electric power charged to the battery 43 from the electric power generated by the stator 102 of the rotating machine 101
- the second drive equivalent torque TSE2 based on the above is transmitted to the B2 rotor 35.
- the second driving equivalent torque TSE2 similarly to the battery input / output zero mode, the second driving equivalent torque TSE2, the engine torque TENG distributed to the first sun gear S1 with the power generation by the stator 102, and the engine torque transmitted to the B1 rotor 34
- the torque combined with TENG is transmitted to the drive wheels DW and DW via the B2 rotor 35.
- the power generated by the stator 102, the power charged to the battery 43, the rotor rotational speed VRO and the second magnetic field rotational speed VMF2 are expressed by the equations (53) and (44).
- the speed relationship is controlled to be maintained.
- the surplus of the engine power with respect to the vehicle required power is converted to electric power in the stator 102 of the rotary machine 101 and the battery 43 is charged.
- the driving wheels DW and DW from the engine 3 Transmission of power to can be done by magnetic path only.
- a torque of r1 / (1 + r1) times the engine torque TENG is transmitted to the drive wheels DW and DW.
- FIG. 90 shows an example of the relationship between rotational speeds and torques of various types of rotary elements at the start of a sudden acceleration operation during ENG travel.
- the engine rotational speed NE is increased to a predetermined rotational speed at which the maximum torque can be obtained.
- the engine rotational speed NE becomes higher than the vehicle speed VP, and the difference between the two becomes larger.
- the direction of rotation is the reverse direction.
- stator 33 In order to apply a positive torque to the drive wheels DW and DW from the stator 33 that generates such a second rotating magnetic field, the stator 33 generates power. Furthermore, the electric power generated by the stator 33 is supplied to the stator 102 of the rotating machine 101 to cause the rotor 103 to rotate normally.
- the rotary machine torque TMOT decreases with respect to the drive wheel transmission torque TDDW and the engine torque TENG of the same magnitude as the second pole pair logarithmic ratio ⁇ increases.
- the second pole pair ratio ⁇ is set to the value 2.0, the second rotary machine 31 can be miniaturized and the cost can be reduced as in the first embodiment.
- Deceleration regeneration During deceleration regeneration, when the ratio of the torque of the drive wheels DW, DW transmitted to the engine 3 to the torque of the drive wheels DW, DW (torque due to inertia) is small, part of the power of the drive wheels DW, DW
- the power is generated by the two stators 102 and 33 using the above, and the generated power is charged to the battery 43.
- the stator 33 With the power generation by the stator 33, a combined torque obtained by combining all of the torque of the drive wheels DW and DW and the torque distributed to the first sun gear S1 as described later is transmitted to the B2 rotor 35. Further, the combined torque transmitted to the B2 rotor 35 is distributed to the stator 33 and the B1 rotor 34.
- the rest of the torque transmitted to the first carrier C1 is transmitted to the B1 rotor 34, and thereafter, along with the power generation in the stator 33 of the second rotating machine 31, electric energy is transmitted to the stator 33 It is transmitted as Also, in this case, as described in the first embodiment, the second rotating magnetic field is reversed. For this reason, the second power-generating equivalent torque TGE2 generated along with the power generation in the stator 33 acts to cause the B2 rotor 35 to rotate in the forward direction. Further, the torque transmitted to the B1 rotor 34 is further transmitted to the B2 rotor 35 so as to balance the second power-generating equivalent torque TGE2, and acts to cause the B2 rotor 35 to rotate in the forward direction.
- the first sun gears S1 and B2 rotor 35 and the drive wheels DW and DW connected to each other are held stationary.
- the first sun gear rotational speed VSU1 and the B2 rotor rotational speed VRB2 have the value 0, and the vehicle speed VP also has the value 0.
- the speed relationship shown in equations (53) and (44) is maintained such that the power supplied to stator 102, the power generated by stator 33, rotor rotational speed VRO and second magnetic field rotational speed VMF2 And the first carrier rotational speed VCA1 and the B1 rotor rotational speed VRB1 are controlled to be relatively small values.
- the engine speed NE is controlled to a relatively small value suitable for starting the engine 3 while keeping the vehicle speed VP at 0 as in the first embodiment.
- the engine 3 is started by controlling the ignition operation of the fuel injection valve and the spark plug of the engine 3 according to the crank angle position.
- ENG creep During ENG creep, the stators 102 and 33 generate power. Also, the battery 43 is charged with the power generated by the two stators 102 and 33 as described above. As in the case of the battery input / output zero mode described above, a part of the engine torque TENG is transmitted to the first carrier C1 and the engine torque transmitted to the first carrier C1 along with the power generation in the stator 102 described above. TENG is distributed to stator 102 and first sun gear S1. Further, as in the first embodiment, the second rotating magnetic field generated as a result of the above-described power generation by the stator 33 is reversed.
- the second electric power-generating equivalent torque TGE2 generated along with the electric power generation by the stator 33 acts to cause the B2 rotor 35 to rotate in the forward direction.
- the engine torque TENG transmitted to the B1 rotor 34 is further transmitted to the B2 rotor 35 so as to balance the second power-generating equivalent torque TGE2, and causes the B2 rotor 35 to rotate in the forward direction.
- the engine torque TENG distributed to the first sun gear S1 as described above is transmitted to the B2 rotor 35.
- the B2 rotor 35 combines the engine torque TENG distributed to the first sun gear S1, the second power generation equivalent torque TGE2, and the engine torque TENG transmitted to the B1 rotor 34. Combined torque is transmitted. The combined torque is transmitted to the drive wheels DW and DW to cause the drive wheels DW and DW to rotate forward. Further, the electric power generated by the stators 102 and 33, the rotor rotational speed VRO and the second magnetic field rotational speed VMF2 are controlled such that the first sun gear rotational speed VSU1 and B2 rotor rotational speed VRB2, that is, the vehicle speed VP becomes very small. Thus, the creep operation is performed.
- engine torque TENG distributed to first sun gear S1 with power generation by stator 102 and B2 rotor via B1 rotor 34 with power generation by stator 33.
- the engine torque TENG transmitted to 35 is transmitted to the drive wheels DW and DW.
- a part of the engine torque TENG can be transmitted to the drive wheels DW and DW, so creep operation can be performed without causing engine stall.
- the second rotating machine 31 since the second rotating machine 31 has the same function as a device combining the planetary gear device and a general one-rotor type rotating machine, unlike the conventional power unit described above There is no need for two planetary gear sets for distributing, combining and transmitting power, and only one first planetary gear set PS1 is sufficient. Therefore, the power plant 1N can be miniaturized accordingly. Further, in the power unit 1N, as described in the description of the operation in the battery input / output zero mode, the engine power is transmitted to the drive wheels DW and DW without recirculation, unlike the conventional case described above. The power passing through the planetary gear set PS1, the rotating machine 101 and the second rotating machine 31 can be reduced.
- the rotating machine 101 and the second rotating machine 31 can be achieved, thereby achieving further downsizing and cost reduction of the power plant 1N. it can. Furthermore, by using the first planetary gear unit PS1, the rotating machine 101 and the second rotating machine 31 having the torque capacity corresponding to the reduced power as described above, the loss of the power is suppressed, and the driving of the power unit 1N Efficiency can be improved.
- engine power is obtained from the first transmission path (the first carrier C1, the first planetary gear P1, the first sun gear S1, the connecting shaft 6, the B2 rotor 35) and the second transmission path (B1 rotor 34, magnetic force by magnetic lines of force, B2
- the total of the rotor 35) and the third transmission path (the first carrier C1, the first planetary gear P1, the first ring gear R1, the rotor 103, the stator 102, the first PDU 41, the second PDU 42, the stator 33, the magnetic force due to magnetic lines, the B2 rotor 35)
- the three divided transmission paths are transmitted to the drive wheels DW and DW via the three transmission paths.
- the power (energy) passing through the first and second PDUs 41 and 42 via the third transmission path can be reduced, and therefore, downsizing and cost reduction of the first and second PDUs 41 and 42 can be achieved.
- further miniaturization and cost reduction of the power plant 1N can be achieved.
- the first planetary gear ratio r1 of the first planetary gear device PS1 is set to a relatively large value among values that can be taken by a general planetary gear device.
- the first planetary gear ratio r1 is set to a small value
- the rotary machine torque TMOT can be made smaller than in the case, and therefore, the rotary machine 101 can be further miniaturized and the cost can be reduced.
- the second pole-log ratio ⁇ of the second rotating machine 31 is set to the value 2.0.
- the second pole logarithm ratio ⁇ is a value
- the rotary machine torque TMOT can be made smaller than when set to less than 1.0, and therefore, the second rotary machine 31 can be further miniaturized and the cost can be reduced.
- the effect of the first embodiment can be obtained similarly.
- the power plant 1N of the present embodiment performs the same control as "control according to the battery SOC" performed by the power plant 1 of the first embodiment.
- the first rotating machine 21 of the first embodiment is replaced with the first planetary gear device PS1 and the rotating machine 101 of one rotor type. Therefore, the first rotating machine 21 is replaced with the rotating machine 101, the stator 23 of the first rotating machine 21 is replaced with the stator 102 of the rotating machine 101, and the A2 rotor 25 is replaced with the first carrier C1 of the first planetary gear unit PS1. .
- FIG. 10 to 1R are mainly different from the fifteenth embodiment in that they further include transmissions 161, 171, 181, and 191, and any of the sixteenth to nineteenth embodiments. Also, the connection between the engine 3, the rotating machine 101, the first planetary gear unit PS1, the second rotating machine 31, and the drive wheels DW and DW is the same as that in the fifteenth embodiment.
- the first carriers C1 and B1 rotor 34 are mechanically coupled to the crankshaft 3a of the engine 3, and the first sun gears S1 and B2 rotor 35 are mechanically coupled to the drive wheels DW and DW. Further, the rotor 103 of the rotating machine 101 is mechanically coupled to the first ring gear R1. Further, in FIG. 91 to FIG. 94, the same components as in the fifteenth embodiment are indicated using the same reference numerals. The same applies to the drawings for explaining the other embodiments described later. The differences from the fifteenth embodiment will be mainly described in order from the power plant 1O according to the sixteenth embodiment.
- the transmission 161 is provided instead of the gear 7b and the first gear 8b which mesh with each other.
- the transmission 161 is a belt-type continuously variable transmission, and has an input shaft connected to the second rotation shaft 7 and an output connected to the idler shaft 8. It has a shaft, pulleys respectively provided on the input shaft and the output shaft, and a metal belt (not shown) wound around these pulleys.
- the transmission 161 outputs the power input to the input shaft to the output shaft in a shifted state by changing the effective diameters of these pulleys. Further, the transmission ratio of the transmission 161 (rotation speed of input shaft / rotation speed of output shaft) is controlled by the ECU 2.
- the transmission 161 is provided between the first sun gears S1 and B2 rotor 35 and the drive wheels DW and DW, and the power transmitted to the first sun gears S1 and B2 rotor 35 is The gear is changed by the transmission 161 and transmitted to the drive wheels DW and DW.
- the gear ratio of the transmission 161 Is controlled to a predetermined value on the deceleration side larger than the value 1.0.
- the torque transmitted to the first sun gear S1 and the B2 rotor 35 is transmitted to the drive wheels DW and DW after being increased in the transmission 161.
- the electric power generated by the rotary machine 101 and the electric power supplied to the second rotary machine 31 are controlled such that the torque transmitted to the first sun gear S1 and the B2 rotor 35 becomes smaller. Be done.
- the maximum value of the torque required for the rotating machine 101 and the second rotating machine 31 can be reduced, the size reduction and cost of the rotating machine 101 and the second rotating machine 31 can be further reduced. It is possible to reduce. Further, the torque distributed to the first sun gear S1 and the first ring gear R1 through the first carrier C1 can be reduced by the control of the transmission 161 and the rotating machine 101 described above, and the torque is transmitted to the first carrier C1. Since the maximum value of the torque can be reduced, further downsizing and cost reduction of the first planetary gear device PS1 can be achieved.
- the transmission gear ratio of the transmission 161 is controlled to a predetermined value on the acceleration side smaller than 1.0.
- the B2 rotor rotational speed VRB2 can be reduced relative to the vehicle speed VP, so that the failure of the second rotating machine 31 due to the excessive increase of the B2 rotor rotational speed VRB2 can be prevented. it can.
- the gear ratio of the transmission 161 has a value 1. It is controlled to a predetermined value on the deceleration side larger than zero.
- the transmission gear ratio of transmission 161 is controlled such that rotor rotational speed VRO and second magnetic field rotational speed VMF2 become predetermined first and second target values, respectively. Be done.
- These first and second target values are calculated by searching the map according to the vehicle speed VP when only the rotating machine 101 and the second rotating machine 31 are used as a power source, and the engine 3, the rotating machine 101 and When using the 2nd rotary machine 31 as a motive power source, it is calculated by searching another map besides the above according to engine revolving speed NE and vehicle speed VP.
- the first and second target values are such that high efficiency of the rotating machine 101 and the second rotating machine 31 can be obtained with respect to the vehicle speed VP (and the engine speed NE) at that time. It is set to a value. Further, in parallel with the control of the transmission 161, the rotor rotational speed VRO and the second magnetic field rotational speed VMF2 are controlled to the first and second target values, respectively. As described above, according to the present embodiment, high efficiency of the rotating machine 101 and the second rotating machine 31 can be obtained while the vehicle is traveling.
- the engine power is continuously changed by the rotating machine 101, the first planetary gear device PS1, and the second rotating machine 31 to drive the drive wheels DW, Since it can be transmitted to the DW, the frequency of the shift operation of the transmission 161 can be reduced. Therefore, the heat loss due to the speed change operation can be suppressed, whereby high driving efficiency of the power unit 1O can be secured.
- the effects of the fifteenth embodiment can be obtained similarly.
- the transmission 161 is a belt-type continuously variable transmission, it is a matter of course that it may be a toroidal or hydraulic continuously variable transmission or a gear-type stepped transmission.
- the input shaft 172 of the transmission 171 is directly connected to the crankshaft 3 a via the flywheel 5, and the output shaft (not shown) is directly connected to the first rotary shaft 4.
- the transmission 171 is provided between the crankshaft 3a and the first carrier C1 and the B1 rotor 34, and shifts the engine power and transmits it to the first carrier C1 and the B1 rotor 34.
- the number of teeth of the gear 9a of the differential gear mechanism 9 described above is larger than the number of teeth of the second gear 8c of the idler shaft 8, whereby transmission to the idler shaft 8 is performed.
- the motive power thus generated is transmitted to the drive wheels DW and DW in a decelerated state.
- the engine torque TENG transmitted to the first sun gear S1 and the B2 rotor 35 is transmitted to the drive wheels DW and DW in a state increased by deceleration by the second gear 8c and the gear 9a.
- the maximum value of the torque required for the rotating machine 101 and the second rotating machine 31 can be reduced, and the size and cost of the rotating machine 101 and the second rotating machine 31 can be further reduced. It is possible to reduce.
- the maximum value of the torque distributed to the first sun gear S1 and the first ring gear R1 via the first carrier C1 can be reduced, the further miniaturization and cost reduction of the first planetary gear device PS1 can be achieved. Can be
- the B1 rotor rotational speed VRB1 can be made smaller than when the shift position is the second speed, so the failure of the second rotating machine 31 due to the excessive B1 rotor rotational speed VRB1 It can be prevented.
- the B1 rotor 34 is made of a magnet, which is particularly effective because the above-mentioned problems are likely to occur.
- the gear position of the transmission 171 is controlled to the first speed.
- the first carrier rotational speed VCA1 is smaller than that of the second gear, so that according to the present embodiment, as is apparent from FIG. 89, the rotor rotational speed VRO can be reduced. Therefore, the failure of the rotating machine 101 due to the excessive increase of the rotor rotational speed VRO can be prevented.
- the speed of the transmission 171 is such that the rotor rotational speed VRO and the second magnetic field rotational speed VMF2 are respectively high efficiency of the rotating machine 101 and the second rotating machine 31 according to the engine speed NE and the vehicle speed VP. It is changed to become a value that can be obtained.
- the rotor rotational speed VRO and the second magnetic field rotational speed VMF are the engine rotational speed NE, the vehicle speed VP, the gear position of the transmission 171, It is controlled to a value determined by equation (44) and equation (53).
- shift shock control in order to suppress a shift shock, during ENG traveling and during the shift operation of the transmission 171, that is, when the transmission 171 disconnects between the engine 3 and the first carrier C1 and the B1 rotor 34.
- the rotary machine 101 and the second rotary machine 31 are controlled as follows.
- such control of the rotating machine 101 and the second rotating machine 31 is referred to as "shift shock control" as in the ninth embodiment.
- the present embodiment it is possible to suppress the shift shock due to the fact that the engine torque TENG is not transmitted to the drive wheels DW and DW during the shift operation, and to improve the commercial property. Note that this shift shock control is performed only during the shift operation of the transmission 171. In addition, according to the present embodiment, the effects of the fifteenth embodiment can be obtained similarly.
- the second rotating shaft 7 is not provided, and the first gear 8b is a gear 6b integrally provided on the connecting shaft 6.
- the first sun gear S1 and B2 rotor 35 transmit the transmission through the connecting shaft 6, gear 6b, first gear 8b, idler shaft 8, second gear 8c, gear 9a, differential gear mechanism 9, etc. It is mechanically connected to the drive wheels DW and DW without passing through 181.
- the transmission 181 is a gear type stepped transmission having the first to third speeds, which is configured in the same manner as the transmission 131 of the tenth embodiment, and has a flange at the first ring gear R1. And an output shaft 183 directly connected to the rotor 103 via a flange. The power input to the input shaft 182 is changed in speed, and is output to the output shaft 183. Further, the change of the gear position of the transmission 181 is controlled by the ECU 2. As described above, the first ring gear R1 is mechanically connected to the rotor 103 via the transmission 181, and the power transmitted to the first ring gear R1 is shifted by the transmission 181 and is transmitted to the rotor 103. It is transmitted.
- the shift position of the transmission 181 is the third speed (gear ratio ⁇ 1.1. It is controlled to 0).
- the torque transmitted to the first ring gear R1 is transmitted to the rotor 103 after being reduced in the transmission 181.
- the electric power generated by the rotating machine 101 is controlled such that the torque transmitted to the rotor 103 is reduced.
- the shift position of the transmission 181 is controlled to the third speed (gear ratio ⁇ 1.0).
- the torque of the rotating machine 101 is increased at the time of ENG start during stop by control of the transmission 181 described above. It is transmitted to the crankshaft 3a via the first ring gear R1, the first planetary gear P1 and the first carrier C1. Accordingly, the power supplied to the rotating machine 101 is controlled such that the rotating machine torque TMOT of the rotating machine 101 is reduced. As described above, according to the present embodiment, it is possible to further reduce the size and cost of the rotating machine 101.
- the size itself of the power transmitted from the first ring gear R1 to the rotor 103 does not change; Since the torque transmitted to the drive wheels DW and DW via the B2 rotor 35 can be controlled to an arbitrary magnitude when the power generated by the motor is transmitted to the B2 rotor 35 as power via the stator 33, the drive wheels DW, A sufficient torque can be transmitted to the DW.
- the gear position of the transmission 181 is It is controlled to the speed (gear ratio> 1.0).
- the rotor rotational speed VRO can be reduced relative to the first ring gear rotational speed VRI1 determined by the relationship between the engine rotational speed NE and the vehicle speed VP at that time, so that the rotating machine 101 by the excessive rotor rotational speed VRO. It is possible to prevent the failure of the
- the shift position of the transmission 181 is controlled such that the rotor rotational speed VRO becomes a predetermined target value.
- This target value is calculated by searching the map according to the vehicle speed VP when only the rotary machine 101 and the second rotary machine 31 are used as a power source, and the engine 3, the rotary machine 101 and the second rotary machine 31 are powered. When used as a source, it is calculated by searching another map than the above according to the engine speed NE and the vehicle speed VP. Further, in these maps, the target value is set to a value such that high efficiency of the rotary machine 101 can be obtained with respect to the vehicle speed VP (and the engine speed NE) at that time. Further, in parallel with such control of the transmission 181, the rotor rotational speed VRO is controlled to the above-mentioned target value. Thereby, according to the present embodiment, high efficiency of the rotating machine 101 can be obtained while the vehicle is traveling.
- the second drive equivalent torque TSE2 from the stator 33 and the engine torque TENG transmitted to the B1 rotor 34 are synthesized during the shift operation of the transmission 181, and the B2 rotor 35 is interposed. Since the torque is transmitted to the drive wheels DW and DW, it is possible to suppress a shift shock due to the engine torque TENG not being transmitted to the drive wheels DW and DW, and therefore, to improve the productability.
- the engine motive power can be continuously shifted by the rotating machine 101, the first planetary gear unit PS1, and the second rotating machine 31 and transmitted to the drive wheels DW and DW.
- the frequency of the shift operation can be reduced, and hence the drive efficiency of the power plant 1Q can be increased.
- the effects of the fifteenth embodiment can be obtained similarly.
- the second rotating shaft 7 is not provided, and the first gear 8b is a gear 6b integrally provided on the connecting shaft 6.
- the transmission 191 is a gear type stepped transmission having the first to third shift speeds, which is configured similarly to the transmission 131 of the seventh embodiment, and is directly connected to the first sun gear S1.
- the input shaft 192 and the output shaft (not shown) directly connected to the connecting shaft 6 are provided to shift the power input to the input shaft 192 and output it to the output shaft. Further, the change of the gear position of the transmission 191 is controlled by the ECU 2.
- the first sun gear S1 is mechanically connected to the drive wheels DW and DW via the transmission 191, the connecting shaft 6, the gear 6b, the first gear 8b, etc.
- the power transmitted to the sun gear S1 is shifted by the transmission 191 and transmitted to the drive wheels DW and DW.
- the B2 rotor 35 is mechanically connected to the drive wheels DW and DW without the transmission 191 via the connection shaft 6, the gear 6b, the first gear 8b, and the like.
- the transmission gear 191 has the first gear (gear ratio> It is controlled to 1.0).
- the torque transmitted to the first sun gear S1 is transmitted to the drive wheels DW and DW after being increased in the transmission 191.
- the power generated by the rotating machine 101 is controlled such that the torque distributed to the first sun gear S1 and the first ring gear R1 is reduced.
- the torque distributed to the first sun gear S1 and the first ring gear R1 via the first carrier C1 can be reduced, so that the first planetary gear unit PS1 can be further miniaturized and Cost reduction can be achieved.
- the torque transmitted from the first ring gear R1 to the rotor 103 can be reduced, the size reduction and cost reduction of the rotating machine 101 can be achieved.
- the shift position of the transmission 191 is controlled to the first speed.
- the rotor rotational speed VRO can be reduced, so that the rotor rotation It is possible to prevent the failure of the rotating machine 101 due to the increase of the speed VRO.
- the shift position of the transmission 191 is controlled such that the rotor rotational speed VRO becomes a predetermined target value.
- This target value is calculated by searching the map according to the vehicle speed VP when only the rotary machine 101 and the second rotary machine 31 are used as a power source, and the engine 3, the rotary machine 101 and the second rotary machine 31 are powered. When used as a source, it is calculated by searching another map than the above according to the engine speed NE and the vehicle speed VP. Further, in these maps, the target value is set to a value such that high efficiency of the rotary machine 101 can be obtained with respect to the vehicle speed VP (and the engine speed NE) at that time. Furthermore, in parallel with such control of the transmission 191, the rotor rotational speed VRO is controlled to the above-mentioned target value. Thereby, according to the present embodiment, high efficiency of the rotating machine 101 can be obtained while the vehicle is traveling.
- the second drive equivalent torque TSE2 and the engine torque TENG transmitted to the B1 rotor 34 are synthesized during the shift operation of the transmission 191, and the drive wheel DW is transmitted via the B2 rotor 35. , And DW, so it is possible to suppress a shift shock due to the fact that the engine torque TENG is not transmitted to the drive wheels DW and DW, and therefore, it is possible to improve the productability.
- the engine power can be transmitted steplessly to the drive wheels DW and DW by the rotating machine 101, the first planetary gear unit PS1 and the second rotating machine 31, the frequency of the speed change operation of the transmission 191 can be reduced.
- the driving efficiency of the power plant 1R can be enhanced.
- the effects of the fifteenth embodiment can be obtained similarly.
- the transmissions 171 to 191 are gear type stepped transmissions, but it is needless to say that belt type, toroidal type, hydraulic type continuously variable transmissions may be used. .
- This power unit 1S mainly includes a transmission that changes the ratio of the speed difference between the rotor rotational speed VRO and the vehicle speed VP to the speed difference between the vehicle speed VP and the engine speed NE as compared with the fifteenth embodiment. It is different. The differences from the fifteenth embodiment will be mainly described below.
- the second rotating shaft 7 is not provided, and the first gear 8b is mounted on the gear 6b integrally provided on the connecting shaft 6.
- the first sun gear S1 and the B2 rotor 35 are mechanically connected to the drive wheels DW and DW via the connecting shaft 6, the gear 6b, the first gear 8b, the differential gear mechanism 9 and the like. It is done.
- the transmission has the second planetary gear unit PS2 and the first and second clutches CL1 and CL2.
- the second sun gear S2 is integrally provided on the first rotation shaft 4, and is mechanically coupled directly to the first carrier C1, the crankshaft 3a and the B1 rotor 34.
- the second carrier C2 is mechanically directly coupled to the first ring gear R1 via a flange or a hollow shaft, and is thereby rotatable integrally with the first ring gear R1.
- the first clutch CL1 is provided between the second carrier C2 and the rotor 103. That is, the second carrier C2 is mechanically directly coupled to the rotor 103 via the first clutch CL1.
- the first clutch CL1 connects and disconnects the second carrier C2 and the rotor 103 as the degree of engagement is controlled by the ECU 2.
- the second clutch CL2 is provided between the second ring gear R2 and the rotor 103. That is, the second ring gear R2 is mechanically directly coupled to the rotor 103 via the second clutch CL2. Further, the second clutch CL2 connects and disconnects the second ring gear R2 and the rotor 103 as the degree of engagement is controlled by the ECU 2.
- the rotor 103 of the rotating machine 101 is mechanically coupled to the first ring gear R1 via the first clutch CL1 and the second carrier C2, and the second clutch CL2, the second ring gear R2, the It is mechanically connected to the first ring gear R1 via the 2 planetary gear P2 and the second carrier C2.
- FIG. 96 (a) is a velocity collinear chart showing an example of the relationship between the first sun gear rotational speed VSU1, the first carrier rotational speed VCA1, and the first ring gear rotational speed VRI1, the second sun gear rotational speed VSU2, and the second carrier rotation. It is shown with a velocity alignment chart showing an example of the relationship between the velocity VCA2 and the second ring gear rotational velocity VRI2.
- the first carrier rotational speed VCA1 and the second sun gear rotational speed VSU2 are equal to each other, and the first ring gear R1 and the second carrier C2 are directly connected to each other.
- the two velocity alignment charts related to the first and second planetary gear units PS1, PS2 in FIG. 96 (a) are shown as one velocity alignment chart as shown in FIG. 96 (b).
- FIG. 96 (b) As shown in the figure, by connecting various rotating elements of the first and second planetary gear units PS1 and PS2 as described above, four rotating elements whose rotational speeds are collinear with each other are formed. .
- FIG. 97 (a) is a velocity collinear chart showing an example of the relationship between the rotational speeds of the four rotating elements described above, the relationship between the rotor rotational speeds VRB1 and VRB2 of the second magnetic field rotational speeds VMF2, B1 and B2. It has shown with the velocity alignment chart which shows an example. As described above, since the first carriers C1 and B1 rotors 34 are directly connected to each other, the first carrier rotation speeds VCA1 and B1 rotor rotation speeds VRB1 are equal to each other. Further, since the first sun gear S1 and the B2 rotor 35 are directly connected to each other, the first sun gear rotational speed VSU1 and the B2 rotor rotational speed VRB2 are equal to each other. Therefore, the two velocity alignment charts of FIG. 97 (a) are shown as one velocity alignment chart as shown in FIG. 97 (b).
- crankshaft 3a, first carrier C1, B1 rotor 34 and second sun gear S2 are directly connected to each other, engine rotational speed NE, first carrier rotational speed VCA1, B1 rotor rotational speed VRB1 and second sun gear rotational speed VSU2 are equal to one another.
- the drive wheels DW and DW, the first sun gear S1 and the B2 rotor 35 are connected to each other, the vehicle speed VP and the first sun gear rotational speed VSU1 and B2 are assumed if there is no gear shift by the differential gear mechanism 9 or the like.
- the rotor rotational speeds VRB2 are equal to one another.
- the rotor 103 is directly connected to the second carrier C2 and the second ring gear R2 via the first and second clutches CL1 and CL2, respectively, the first clutch CL1 is connected and the second clutch CL2 is connected. Is interrupted (hereinafter, such a clutch engagement / disengagement state is referred to as "first transmission mode"), the rotor rotational speed VRO and the second carrier rotational speed VCA2 are equal to each other. Furthermore, when the first clutch CL1 is disconnected and the second clutch CL2 is connected (hereinafter, such a connected / disconnected state of the clutch is referred to as “second shift mode”), the rotor rotational speed VRO and The second ring gear rotational speeds VRI2 are equal to one another.
- the rotor rotational speed VRO, the engine rotational speed NE, the vehicle speed VP, and the second magnetic field rotational speed VMF2 become collinear as shown in FIG. 98A, for example, during the first shift mode.
- the second speed change mode for example, a collinear relationship as shown in FIG. 98 (b) is obtained.
- the distance between the vertical line representing the vehicle speed VP and the vertical line representing the rotor rotational speed VRO in the velocity nomograph is the first shift described above. Since the mode is smaller than the second transmission mode, the ratio of the rotational difference DN2 between the rotor rotational speed VRO and the vehicle speed VP to the rotational difference DN1 between the engine rotational speed NE and the vehicle speed VP (hereinafter referred to as "rotational ratio DN2 / DN1”) is smaller in the first shift mode.
- the first speed change is performed when the rotor rotational speed VRO determined by the relationship between the engine speed NE and the vehicle speed VP becomes excessive, such as during rapid acceleration when the engine speed NE is higher than the vehicle speed VP.
- the mode is used.
- the rotor rotation speed VRO can be made smaller than in the case where the second transmission mode is used. It is possible to prevent the failure of the rotating machine 101 due to the excessive VRO.
- TMOT - ⁇ ⁇ TDDW + (1 + ⁇ ) TDENG ⁇ / (R1 ⁇ r2 + r1 + 1 + ⁇ ) (68)
- the rotating machine torque TMOT is the same as that of the second shift mode for the drive wheel transmission torque TDDW and the engine transmission torque TDENG of the same magnitude. small. Therefore, at the time of ENG start during EV travel, the second shift mode is used.
- the second shift mode is used as described above, and the power generated by the rotating machine 101 is controlled based on the equation (68). Therefore, the maximum value of the torque required of the rotating machine 101 can be reduced, and thus, further downsizing and cost reduction of the rotating machine 101 can be achieved.
- the vehicle speed VP and the engine rotation during the operation of the engine 3 according to the vehicle speed VP during the stop of the engine 3 among the first and second shift modes.
- a transmission mode is selected, which allows higher efficiency of the rotating machine 101.
- the rotor rotational speed VRO can be controlled to an appropriate height while the vehicle is traveling, high efficiency of the rotating machine 101 can be obtained.
- switching between the first and second shift modes is performed when the second carrier rotational speed VCA2 and the second ring gear rotational speed VRI2 are equal to each other, as in the thirteenth embodiment.
- the switching of the first and second shift modes can be smoothly performed while maintaining the rotation of the drive wheels DW and DW and the engine 3, and good drivability is ensured. be able to.
- the second drive equivalent torque Since TSE2 and the engine torque TENG transmitted to the B1 rotor 34 are combined and transmitted to the drive wheels DW and DW via the B2 rotor 35, the shift is caused by the engine torque TENG not being transmitted to the drive wheels DW and DW
- the shock can be suppressed, and therefore, the marketability can be enhanced.
- the effects of the fifteenth embodiment can be obtained similarly.
- the second sun gear S2 is connected to the first carrier C1, and the second ring gear R2 is connected to the rotor 103 via the second clutch CL2, but the connection relationship between them is reversed. That is, the second ring gear R2 may be connected to the first carrier C1, and the second sun gear S2 may be connected to the rotor 103 via the second clutch CL2.
- 1st and 2nd clutch CL1 and CL2 are comprised with the friction type multiple disc clutch, you may comprise with an electromagnetic clutch etc., for example.
- FIGS. 100 (a) and 100 (b) show an example of the relationship between the rotational speeds of various types of rotary elements in the power unit 1S, (a) in the first shift mode and (b) in the second shift mode. It is a velocity alignment chart.
- the rotating machine 101 is "first rotating machine”
- the rotating machine 31 is “second rotating machine”
- the second sun gear S2 is "one gear” or "first gear”.
- the second ring gear R2 "the other gear” or “the second gear”, the second carrier C2 the “carrier”, the second output portion "the first rotary shaft 4", the first clutch "the first clutch CL1
- the second clutch is represented as “first clutch CL2”, the engine 3 as “heat engine”, and the drive wheels DW, DW as “driven parts”.
- the rotational speed of one gear of the second planetary gear unit PS2 is the first gear rotational speed VG1
- the rotational speed of the other gear of the second planetary gear unit PS2 is the second gear rotational speed VG2
- the second The rotational speed of the carrier of the planetary gear unit PS2 is taken as a carrier rotational speed VC.
- connection relationship In the connection relationship described above, various rotating elements are directly connected, and the second output of the second rotating machine is connected to the carrier by connection of the first clutch, and the second output is connected by disconnection of the second clutch.
- the relationship between the rotational speed of the heat engine and the speed of the driven part is shown, for example, as shown in FIG.
- first transmission mode such connection / disconnection states of the first and second clutches will be referred to as "first transmission mode”.
- first transmission mode when the second output of the second rotating machine is disconnected from the carrier by the disconnection of the first clutch, and the second output is connected to the other gear by the connection of the second clutch, the heat engine
- FIG. 100 (b) such a connection / disconnection state of the first and second clutches is referred to as a "second shift mode”.
- the distance from the vertical line representing the magnetic field rotational speed VF to the vertical line representing the second rotor rotational speed VR2 and the second rotor rotational speed VR2 The ratio of the vertical line representing the distance to the vertical line representing the first rotor rotational speed VR1 is 1: (1 / ⁇ ).
- the distance from the vertical line representing the first gear rotational speed VG1 to the vertical line representing the carrier rotational speed VC is Y
- the vertical line representing the carrier rotational speed VC is the second gear
- Z be the distance to the vertical line representing the rotational speed VG2.
- the drive equivalent torque Te the heat engine transmission torque TDHE
- the object to be heat-treated The relationship between the drive transmission torque TOUT and the second rotary machine torque TM2 is shown, for example, as shown in FIG. 101 (a). Further, the torque required for the second rotating machine, that is, the second rotating machine torque TM2 is expressed by, for example, the following equation (69).
- TM2 ⁇ ⁇ TOUT + [(1 / ⁇ ) +1] TDHE ⁇ / [Y + (1 / ⁇ ) +1] (69)
- the relationship between the driving equivalent torque Te, the heat engine transmission torque TDHE, the driven portion transmission torque TOUT, and the second rotary machine torque TM2 is, for example, as shown in FIG. Indicated. Further, the second rotary machine torque TM2 is represented by, for example, the following equation (70).
- TM2 ⁇ ⁇ TOUT + [(1 / ⁇ ) +1] TDHE ⁇ / [Z + Y + (1 / ⁇ ) +1] (70)
- the second rotary machine torque TM2 is the second shift mode with respect to the heat engine transmission torque TDHE and the driven part transmission torque TOUT of the same magnitude. Is smaller. Therefore, for example, when the torque required for the second rotating machine is increased as described above, the second rotating machine torque TM2 can be reduced by using the second shift mode, and hence, Further downsizing and cost reduction of the second rotating machine can be achieved.
- the rotational speed of the second rotating machine can be controlled to an appropriate size, thereby , High efficiency of the second rotating machine can be obtained. Furthermore, switching between the first and second shift modes described above is performed when the carrier rotational speed VC and the second gear rotational speed VG2 are equal to each other, so that the rotation of the driven parts and the heat engine can be maintained smoothly. It can be done to ensure good drivability.
- the torque THE of the heat engine transmitted to the second element is transmitted to the third element along with the power generation by the second rotating machine.
- the acting load torque is transmitted to the driven part via the first element as a reaction force. Therefore, at the time of transition between the first and second shift modes, if both the first and second clutches are disconnected, the third element and the second rotating machine are disconnected, As a result, the load torque from the second rotating machine does not act on the third element, and as a result, the torque THE of the heat engine transmitted via the second and first elements becomes extremely small.
- the power plant 1T is mainly different from the fifteenth embodiment in that the power plant 1T further includes a transmission 201.
- the differences from the fifteenth embodiment will be mainly described below.
- the second rotating shaft 7 is not provided, and the first gear 8b is integrally provided on the connecting shaft 6.
- the first sun gear S1 is mechanically connected to the drive wheels DW and DW via the connecting shaft 6, the gear 6b, the first gear 8b, the differential gear mechanism 9 and the like without the transmission 201 described above. Is linked to
- the transmission 201 is a gear-type stepped transmission having the first to third speeds, which is configured similarly to the transmission 131 of the tenth embodiment, and is directly connected to the B2 rotor 35.
- the input shaft 202 and the output shaft (not shown) directly connected to the connecting shaft 6 are provided, and the power input to the input shaft 202 is changed in speed, and is output to the output shaft. Further, the change of the gear position of the transmission 201 is controlled by the ECU 2.
- the B2 rotor 35 is connected to the drive wheels DW and DW via the transmission 201, the connecting shaft 6, the gear 6b, the first gear 8b, etc., and is transmitted to the B2 rotor 35.
- the power is shifted by the transmission 201 and transmitted to the drive wheels DW and DW.
- the transmission gear stage 201 is the first gear It is controlled to (gear ratio> 1.0).
- the B2 rotor transmission torque TRB2 transmitted to the B2 rotor 35 is increased in the transmission 201 and then transmitted to the drive wheels DW and DW.
- the power supplied to the stator 33 of the second rotating machine 31 is controlled such that the B2 rotor transmission torque TRB2 becomes smaller.
- the maximum value of the torque required for the second rotating machine 31 can be reduced, and further downsizing and cost reduction of the second rotating machine 31 can be achieved.
- the shift position of the transmission 201 is controlled to the third speed (gear ratio ⁇ 1.0).
- the B2 rotor rotational speed VRB2 can be reduced relative to the vehicle speed VP, so that the failure of the second rotating machine 31 due to the excessive increase of the B2 rotor rotational speed VRB2 can be prevented. it can.
- the shift position of the transmission 201 is controlled such that the second magnetic field rotational speed VMF2 becomes a predetermined target value.
- This target value is calculated by searching the map according to the vehicle speed VP when only the rotary machine 101 and the second rotary machine 31 are used as a power source, and the engine 3, the rotary machine 101 and the second rotary machine 31 are powered. When used as a source, it is calculated by searching another map than the above according to the engine speed NE and the vehicle speed VP. Further, in these maps, the target value is set to a value such that high efficiency of the second rotating machine 31 can be obtained with respect to the vehicle speed VP (and the engine speed NE) at that time. Further, in parallel with the control of the transmission 201, the second magnetic field rotational speed VMF2 is controlled to the above-mentioned target value. Thereby, according to the present embodiment, high efficiency of the second rotating machine 31 can be obtained while the vehicle is traveling.
- the engine motive power can be steplessly shifted and transmitted to the drive wheels DW and DW by the rotating machine 101, the first planetary gear unit PS1 and the second rotating machine 31.
- the frequency of the shift operation can be reduced, and hence the driving efficiency of the power plant 1T can be increased.
- the effects of the fifteenth embodiment can be obtained similarly.
- the transmission 201 is a gear-type stepped transmission, but may be a belt-type, toroidal-type, or hydraulic-type continuously variable transmission.
- the rotation of the first rotary shaft 4 is permitted only by the brake mechanism BL when rotating forward with the crankshaft 3a, the first carrier C1, and the B1 rotor 34, and reverse rotation with the crankshaft 3a etc. If you do, you will be blocked.
- the operation by the above-described EV creep and EV start is performed as follows. That is, power is supplied to the stator 102 of the rotating machine 101 to reversely rotate the rotor 103 together with the first ring gear R1, and power is supplied to the stator 33 of the second rotating machine 31. Rotate the rotating magnetic field forward. Further, the rotor rotational speed VRO and the second magnetic field rotational speed VMF2 are controlled such that ( ⁇ + 1) ⁇ VRO
- r1 ⁇ VMF2
- the reverse rotation of the first carrier C1 is blocked by the brake mechanism BL with respect to the first ring gear R1 rotating in reverse with the rotor 103 as described above, so that all the motive power of the rotating machine 101 is the first ring gear R1.
- the first sun gear S1 is transmitted to the first sun gear S1 via the first planetary gear P1, and acts to rotate the first sun gear S1 forward.
- the reverse rotation of the B1 rotor 34 is prevented by the brake mechanism BL with respect to the second rotating magnetic field of the stator 33 rotating normally as described above, all the power supplied to the stator 33 is transmitted to the B2 rotor 35. It is transmitted as motive power and acts to cause the B2 rotor 35 to rotate normally.
- the power transmitted to the first sun gear S1 and the B2 rotor 35 is transmitted to the drive wheels DW and DW, and causes the drive wheels DW and DW to rotate in the forward direction.
- the first carrier C1 and the B1 rotor 34 which are prevented from being reversely rotated by the brake mechanism BL, are controlled from the rotor 103 and the stator 33 by the control of the rotating machine 101 and the second rotating machine 31 described above.
- the torque acts to reverse.
- the crankshaft 3a and the first carrier C1 and the B1 rotor 34 are not only reversed but also held stationary.
- the drive wheels DW and DW can be driven by the rotating machine 101 and the second rotating machine 31 without using engine power. Further, during this driving, the crankshaft 3a is not only reversed but also kept stationary so that the engine 3 will not be dragged. The other effects of the fifteenth embodiment can be similarly obtained.
- the second pole-log ratio ⁇ of the second rotating machine 31 is set to the value 2.0, as in the first embodiment.
- the drive efficiency is lowered due to the occurrence of the loss due to the excessive second magnetic field rotational speed VMF2.
- the first planetary gear ratio r1 of the first planetary gear unit PS1 is set to a relatively large value, but setting the value to a smaller value achieves the following effect can get.
- the first planetary gear ratio r1 when the first planetary gear ratio r1 is set to a relatively large value, when the engine speed NE is higher than the vehicle speed VP (see the two-dot chain line in FIG. 89) The speed VRO may be higher than the engine speed NE and may be excessive.
- the first planetary gear ratio r1 by setting the first planetary gear ratio r1 to a smaller value, as is apparent from the comparison between the velocity alignment diagram shown by a broken line in FIG. 89 and the velocity alignment diagram shown by a two-dot chain line, The rotational speed VRO can be reduced, and therefore, the reduction of the driving efficiency due to the occurrence of the loss due to the increase of the rotor rotational speed VRO can be prevented.
- the first carrier C1 and the B1 rotor 34 are directly connected to each other, and the first sun gear S1 and the B2 rotor 35 are directly connected to each other.
- the first sun gear S1 and the B2 rotor 35 may not be directly connected to each other as long as they are connected to the crankshaft 3a, and the first sun gear S1 and the B2 rotor 35 may not be connected to each other as long as they are connected to the drive wheels DW and DW.
- the transmissions 161 and 171 according to the sixteenth and seventeenth embodiments may be provided as two transmissions as described below.
- one of the two transmissions constituting the transmission 161 may be provided between the first sun gear S1 and the drive wheels DW and DW, and the other may be provided between the B2 rotor 35 and the drive wheels DW and DW. Further, one of the two transmissions constituting the transmission 171 may be provided between the first carrier C1 and the crankshaft 3a, and the other may be provided between the B1 rotor 34 and the crankshaft 3a.
- the first sun gear S1 and the first ring gear R1 are connected to the drive wheels DW and DW and the rotating machine 101, respectively, but their connection relationship is reversed, that is, The first ring gear R1 and the first sun gear S1 may be connected to the drive wheels DW and DW and the rotating machine 101, respectively.
- the rotating machine torque TMOT is expressed by the following equation (71) at the time of ENG start during EV traveling where the torque required of the rotating machine 101 becomes particularly large.
- TMOT ⁇ ⁇ ⁇ TDDW + (1 + ⁇ ) TDENG ⁇ / (r1 ′ + 1 + ⁇ ) (71)
- r1 is the ratio of the number of teeth of the first ring gear to the number of teeth of the first sun gear S1 (the number of teeth of the first ring gear / the number of teeth of the first sun gear S1) as described above , Greater than 1.0.
- first planetary gear ratio r1 is the number of teeth of the first sun gear S1 / the number of teeth of the first ring gear as described above, and is smaller than the value 1.0, and the equation (66) and the equation
- the rotary machine torque TMOT can be made smaller, and therefore, the rotary machine 101 can be further miniaturized and the cost can be reduced.
- the first planetary gear unit PS1 is used as a differential device, but any other appropriate device may be used as long as it has the following function. That is, it has three elements and combines the function of distributing the power input to one of the three elements to the other two elements and the power input to these other two elements It may be a device which has a function of outputting to one of the above-mentioned elements and which rotates while maintaining the linear speed relationship during the distribution and combination of the power.
- a device having a plurality of rollers for transmitting power by friction between the surfaces and having the same function as the planetary gear set may be used.
- an apparatus configured by a combination of a plurality of magnets and a soft magnetic material as disclosed in Japanese Patent Application Laid-Open No. 2008-39045 may be used.
- a double pinion type planetary gear device may be used as the differential device. The above applies to the second planetary gear unit PS2 as well.
- the rotary machine 101 is a DC motor, but it is an apparatus having a function of converting supplied electric power into power and a function of converting input power into electric power.
- Other devices may be used, for example an AC motor.
- a brake mechanism BL may be provided to prevent reverse rotation of the crankshaft 3a.
- the brake mechanism BL is configured by the one-way clutch OC and the case CA, it may be configured by another mechanism, such as a band brake, as long as the reverse rotation of the crankshaft 3a can be prevented.
- the ECU 2 and the first and second PDUs 41 and 42 may be those capable of controlling the power generation / supply power of the stators 23, 33 and 102.
- the ECU 2 and the first and second PDUs 41 and 42 may be those capable of controlling the power generation / supply power of the stators 23, 33 and 102.
- it may be configured by an electric circuit or the like on which a microcomputer is mounted.
- the battery 43 may be, for example, a capacitor.
- the battery 43 may be omitted depending on the necessity.
- first stator magnetic poles eight first magnetic poles, and six cores 25a are set. That is, the embodiment is an example in which the ratio of the number of first stator magnetic poles, the number of first magnetic poles, and the number of first soft magnetic members is 1: 2: 1.5, but the ratio of these numbers is As long as 1: m: (1 + m) / 2 (m ⁇ 1.0) is satisfied, any number can be adopted as the number of the first stator magnetic pole, the first magnetic pole and the core 25a. The same applies to the second rotating machine 31 as well. Furthermore, in the embodiment, the cores 25a, 35a are made of steel plates, but may be made of another soft magnetic material.
- stator 23 and the A1 rotor 24 are respectively disposed on the outer side and the inner side in the radial direction, but may be arranged on the inner side and the outer side in the radial direction, respectively.
- the rotors 24 and 25 of the stators 23, A1 and A2 are arranged in the radial direction, and the first rotating machine 21 is configured as a so-called radial type.
- the rotors 24 and 25 may be arranged in the axial direction, and the first rotating machine 21 may be configured as a so-called axial type. The above applies to the second rotating machine 31 as well.
- one magnetic pole is comprised by the magnetic pole of the single permanent magnet 24a in embodiment
- the magnetic pole of several permanent magnets For example, by forming one magnetic pole by arranging the two permanent magnets in an inverted V shape such that the magnetic poles of the two permanent magnets approach each other on the stator 23 side, the directivity of the magnetic lines of force ML described above Can be enhanced.
- an electromagnet or a stator capable of generating a moving magnetic field may be used.
- the U-phase to W-phase coils 23c to 23e are wound by distributed winding in the slots 23b, but not limited to this, concentrated winding may be performed.
- the coils 23c to 23e are formed of U-phase to W-phase three-phase coils, but the number of phases of the coils is not limited to this as long as the first rotating magnetic field can be generated.
- any number other than those shown in the embodiment may be adopted as the number of slots 23b.
- the slots 23b, the permanent magnets 24a, and the cores 25a are arranged at equal intervals, but may be arranged at unequal intervals. The above applies to the second rotating machine 31 as well.
- the engine 3 as the heat engine is a gasoline engine, but may be another engine such as a diesel engine or an external combustion engine.
- the present embodiment is an example in which the power plant is applied to a vehicle, the present invention is not limited to this, and can be applied to, for example, a ship or an aircraft.
- the power plant 1 As shown in FIGS. 104 and 105, the power plant 1 according to the twenty-third embodiment drives the left and right front wheels 4, 4 of the hybrid vehicle (hereinafter referred to as "vehicle").
- vehicle the hybrid vehicle
- the first rotating machine 10 and the second rotating machine 20 are provided.
- the engine 3 is connected to the first rotating machine 10, and the first rotating machine 10 and the second rotating machine 20 are the gear mechanism 6, the differential gear mechanism 7 and the left and right drive shafts 8, 8. Are connected to the left and right front wheels 4, 4. Thereby, as described later, the power of the engine 3 and the power of the first rotating machine 10 and the second rotating machine 20 are transmitted to the front wheels 4. Further, the vehicle 2 is provided with left and right rear wheels 5, 5 which are idle wheels.
- the engine 3 corresponds to a heat engine
- the front wheel 4 corresponds to a driven part.
- the engine 3 is a multi-cylinder internal combustion engine fueled by gasoline, and its operating state is controlled by an ENG-ECU 29 described later. Further, the two rotating machines 10 and 20 and the gear mechanism 6 are both accommodated in a drive system housing (not shown) fixed to the cylinder block of the engine 3.
- the gear mechanism 6 includes first and second gear shafts 6a and 6b parallel to an output shaft 13 of the first rotating machine 10 described later, four gears provided on the output shaft 13 and two gear shafts 6a and 6b. 6c to 6f.
- the gear 6c is concentrically fixed to the right end of the output shaft 13, and is always in mesh with the gear 6d.
- the gear 6d is concentrically and rotatably fitted to the first gear shaft 6a, and in addition to the gear 6c, is always meshed with a gear 6e concentrically fixed to the right end of the second gear shaft 6b. .
- the gear 6 f is concentrically fixed to the left end portion of the second gear shaft 6 b and always meshes with the gear 7 a of the differential gear mechanism 7. With the above configuration, the rotation of the output shaft 13 is transmitted to the differential gear mechanism 7 via the gear mechanism 6.
- FIG. 106 schematically shows the cross-sectional configuration of the first rotating machine 10 and the second rotating machine 20
- FIG. 107 is a circle broken along the circumferential direction at the position of line AA in FIG. 106. It is the figure which showed the cyclic
- the first rotating machine 10 will be described. As shown in FIG. 106, the first rotating machine 10 is concentric with the case 11 fixed to the drive system housing described above, the input shaft 12 whose left end is directly connected to the crankshaft of the engine 3, and the input shaft 12 A first rotor 14 housed in the case 11 and rotating integrally with the output shaft 13, and a second rotor 15 housed in the case 11 and rotating integrally with the input shaft 12. And a stator 16 fixed to the inner peripheral surface of the peripheral wall 11 c of the case 11. The first rotor 14, the second rotor 15 and the stator 16 are arranged concentrically with each other from the inner side to the outer side in the radial direction.
- the case 11 includes left and right side walls 11a and 11b, and a cylindrical peripheral wall 11c fixed to the outer peripheral end of the side walls 11a and 11b.
- Bearings 11d and 11e are attached to central portions of the left and right side walls 11a and 11b, respectively, and the input shaft 12 and the output shaft 13 are rotatably supported by the bearings 11d and 11e, respectively. Further, the axial movement of the two shafts 12 and 13 is restricted by a thrust bearing (not shown) or the like.
- the first rotor 14 includes a rotary disc portion 14b concentrically fixed to the left end of the output shaft 13, and a cylindrical ring portion 14c fixed to the outer end of the rotary disc portion 14b.
- the ring portion 14c is formed of a soft magnetic material, and on the outer peripheral surface thereof, a permanent magnet array is provided along the circumferential direction so as to face the iron core 16a of the stator 16.
- This permanent magnet array is composed of eight permanent magnets 14a (magnetic poles) as shown in FIG.
- Each two adjacent permanent magnets 14a have different polarities from each other and are arranged at equal intervals, and the length in the axial direction of each permanent magnet 14a is set to a predetermined length.
- the N pole and the S pole of the permanent magnet 14a are denoted as (N) and (S), respectively, and the understanding is simplified. For this reason, illustration of things other than the main configuration (for example, the case 11 etc.) is omitted.
- the stator 16 generates a rotating magnetic field, and has an iron core 16a and U-phase, V-phase and W-phase coils 16c, 16d, 16e (see FIG. 107) wound around the iron core 16a.
- the iron core 16a has a cylindrical shape in which a plurality of steel plates are stacked, and is fixed to the case 11, and its axial length is set to the same length as that of the permanent magnet 14a.
- twelve slots 16b are formed on the inner peripheral surface of the iron core 16a, and these slots 16b extend in the axial direction, and the circumferential direction of the first main shaft 4 (hereinafter simply referred to as "circumferential direction") ) At equal intervals.
- the iron core 16a and the U-phase to W-phase coils 16c to 16e correspond to an armature and an armature row.
- U-phase to W-phase coils 16c to 16e are wound by distributed winding (wave winding) in slot 16b, and 1ST • PDU 31 and a bidirectional buck-boost converter (hereinafter referred to as “VCU”) described later. It is electrically connected to a battery 33 described later via 34.
- VCU bidirectional buck-boost converter
- stator 16 when power is supplied from battery 33 and current flows to U-phase to W-phase coils 16c to 16e, or when power generation is performed as described later, At the end on the first rotor 14 side, four magnetic poles are generated at equal intervals in the circumferential direction (see FIGS. 111 (a) to (c)), and the rotating magnetic field by these poles is moved in the circumferential direction.
- the magnetic poles generated on the iron core 16a are referred to as "stator magnetic poles”.
- the polarities of two stator poles adjacent in the circumferential direction are different from each other.
- the N pole and the S pole of the stator magnetic pole are denoted as (N) and (S), respectively, similarly to the N pole and the S pole of the permanent magnet 14a. .
- the second rotor 15 includes a rotary disk 15b fixed to the right end of the input shaft 12, a support 15c extending from the outer end of the rotary disk 15b toward the second rotary machine 20, and the support
- a soft magnetic core row is fixed to 15 c and disposed between the permanent magnet row of the first rotor 14 and the iron core 16 a of the stator 16.
- the soft magnetic core row is composed of six soft magnetic cores 15 a made of a soft magnetic material (for example, a laminate of steel plates).
- These soft magnetic cores 15a are arranged at equal intervals along the circumferential direction, and provided so as to have a predetermined distance from the permanent magnet 14a and the iron core 16a.
- the axial length of the soft magnetic core 15 a is set to the same length as the permanent magnet 14 a and the iron core 16 a of the stator 16.
- the stator 16 is referred to as a "stator”
- the first rotor 14 is referred to as a "first rotor”
- the second rotor 15 is referred to as a "second rotor”.
- the torque equivalent to the electric angular velocity of the rotating magnetic field generated by the power supply to the stator and the supplied electric power is the driving equivalent torque Te
- the driving equivalent torque Te is the driving equivalent torque Te
- the torque T1 transmitted to the first rotor The relationship between the torque T2 transmitted to the second rotor, the electrical angular velocity of the first and second rotors, and the electrical angular velocity of the rotating magnetic field will be described below.
- the first rotating machine 10 when configured to satisfy the following conditions (f1) and (f2), an equivalent circuit corresponding to such a first rotating machine 10 is as shown in FIG.
- a pair of N pole and S pole is referred to as “pole pair”, and the number of pole pairs is referred to as “pole-log number”.
- the stator has a three-phase coil of U-phase, V-phase and W-phase.
- Two stator magnetic poles that is, the number of pole poles of the stator magnetic poles is 1, and four poles, that is, the number of pole poles of the magnetic poles is 2, and the soft magnetic material is a total of the first to third soft magnetic materials Must be three.
- the magnetic flux ⁇ k1 of the magnetic pole passing through the first soft magnetic body is expressed by the following equation (72).
- ⁇ f indicates the maximum value of the magnetic flux of the magnetic pole
- ⁇ 1 and ⁇ 2 indicate the rotational angular position of the magnetic pole relative to the U-phase coil and the rotational angular position of the first soft magnetic body, respectively.
- the ratio of the number of pole pairs of the magnetic poles to the number of pole pairs of the stator poles is 2, the magnetic flux of the magnetic poles rotates (changes) at a period twice that of the rotating magnetic field.
- the value 2 is multiplied by ( ⁇ 2 ⁇ 1).
- the magnetic flux ⁇ u1 of the magnetic pole passing through the U-phase coil via the first soft magnetic body corresponds to the value obtained by multiplying the magnetic flux ⁇ k1 expressed by the equation (72) by cos ⁇ 2, the following equation (73) can get.
- the magnetic flux ⁇ u2 of the magnetic pole passing through the U-phase coil via the second soft magnetic material corresponds to the value obtained by multiplying the magnetic flux ⁇ k2 expressed by the equation (74) by cos ( ⁇ 2 + 2 ⁇ / 3), (75) is obtained.
- Equation (76) is obtained as a calculation equation of the magnetic flux ⁇ u3 of the magnetic pole passing through the U-phase coil via the third soft magnetic material.
- the magnetic flux ⁇ u of the magnetic pole passing through the U-phase coil through the three soft magnetic bodies is represented by the above equations (73), (75) and (76).
- the sum of the magnetic fluxes ⁇ u1 to ⁇ u3 is expressed by the following equation (77).
- a, b and c respectively indicate the number of pole pairs of the magnetic pole, the number of soft magnetic bodies and the number of pole pairs of the stator pole.
- equation (78) can be transformed based on the formula of the sum and product of trigonometric functions to obtain the following equation (79).
- equation (81) the integral term in the second term on the right side is rearranged using a formula of sum of series and an Euler's formula under the condition of a ⁇ c ⁇ 0 to obtain the following equation (82). That is, the second term of the right side of equation (81) has the value 0.
- equation (83) can be obtained by arranging the integral term in the third term on the right side using the formula of the sum of series and the formula of Euler under the condition of a ⁇ c ⁇ 0. . That is, the third term of the right side of equation (81) also has the value 0.
- ⁇ e2 is a value obtained by multiplying the rotation angle position ⁇ 2 of the soft magnetic body with respect to the U-phase coil by the pole count c of the stator magnetic poles, and therefore represents the electrical angle position of the soft magnetic body with respect to the U-phase coil.
- ⁇ e1 is a value obtained by multiplying the rotational angle position ⁇ 1 of the magnetic pole with respect to the U-phase coil by the number of pole pairs c of the stator magnetic pole, it represents the electrical angular position of the magnetic pole with respect to the U-phase coil.
- the magnetic flux ⁇ v of the magnetic pole passing through the V-phase coil via the soft magnetic material is such that the electrical angle position of the V-phase coil is advanced by the electrical angle 2 ⁇ / 3 with respect to the U-phase coil. Is represented by
- the magnetic flux ⁇ w of the magnetic pole passing through the W-phase coil via the soft magnetic material is lower in the following equation (88) because the electrical angle position of the W-phase coil is delayed by the electrical angle 2 ⁇ / 3 with respect to the U-phase coil. Is represented by
- ⁇ e1 represents a time differential value of ⁇ e1, that is, a value obtained by converting the angular velocity of the first rotor with respect to the stator into an electrical angular velocity (hereinafter referred to as “first rotor electrical angular velocity”)
- ⁇ e2 is a time derivative of ⁇ e2 A value, that is, a value obtained by converting the angular velocity of the second rotor with respect to the stator into an electrical angular velocity (hereinafter, referred to as "second rotor electrical angular velocity”) is represented.
- the magnetic flux of the magnetic pole passing directly through the U-phase to W-phase coil without passing through the soft magnetic material is extremely small, and the influence thereof can be ignored.
- the time derivative values d ⁇ u / dt to d ⁇ w / dt of the magnetic fluxes ⁇ u to ⁇ w of the magnetic poles passing through the U-phase to W-phase coils through the magnetic material respectively, cause the magnetic poles and the soft magnetic material to rotate relative to the stator row. Accordingly, counter electromotive voltages (induced electromotive voltages) generated in U-phase to W-phase coils are respectively represented.
- I represents the amplitude (maximum value) of the current flowing through the U-phase to W-phase coils.
- the first and second rotor transmission torques T1 and T2 are expressed by the following equations (100) and (101), respectively.
- the relationship between the three torques Te, T1 and T2 represented by the above equation (103) and the relationship between the three electric angular velocities ⁇ mf, ⁇ e1 and ⁇ e2 represented by the equation (96) described above are planetary gear devices
- the relationship between torque and rotational speed in the sun gear, ring gear and carrier of Furthermore, as described above, on the condition that b a + c and a ⁇ c ⁇ 0 are satisfied, the relationship between the electrical angular velocity of equation (96) and the relationship between torques of equation (103) are satisfied.
- the relationship between the electrical angular velocity shown in the equation (96) and the relationship between the torque shown in the equation (103) is established, whereby the first rotating machine 10 can be used as a sun gear, a ring gear and a carrier (hereinafter referred to as “planet gear It can be operated with the same operating characteristics as the three elements of the device.
- the first rotating machine 10 can be miniaturized and manufactured accordingly. Cost can be reduced. As a result, the power plant itself can be miniaturized, and the manufacturing cost can be reduced. Further, as apparent from the above equations (96) and (103), the relationship between the three electric angular velocities ⁇ mf, ⁇ e1 and ⁇ e2 can be freely set depending on the setting of the pole-log ratio ⁇ , ie, the pole number ratio m. While being able to do, the relationship of three torque Te, T1, and T2 can also be set up freely.
- the relationship between the three electric angular velocities ⁇ mf, ⁇ e1, and ⁇ e2 can be expressed, for example, as shown in FIG.
- the figure is a so-called velocity alignment chart.
- a vertical line intersecting a horizontal line passing the value 0 on the vertical axis is for representing the rotational speed of each parameter.
- the distance between the white circle and the horizontal line represented corresponds to the rotational speed of each parameter.
- the distance between the vertical line representing the magnetic field electrical angular velocity ⁇ mf in the velocity alignment chart and the vertical line representing the second rotor electrical angular velocity ⁇ e2 is Since the ratio becomes smaller, the ratio ( ⁇ 2 / ⁇ 1) of the difference ⁇ 2 between the second rotor electrical angular velocity ⁇ e2 and the magnetic field electrical angular velocity ⁇ mf to the difference ⁇ 1 between the first rotor electrical angular velocity ⁇ e1 and the second rotor electrical angular velocity ⁇ e2 becomes smaller .
- ⁇ F represents the maximum value of the magnetic flux of the magnet pole.
- ⁇ ER 1 is a first rotor electrical angle, and the rotational angle position of a specific permanent magnet 14 a of the first rotor 14 with respect to a specific U phase coil 16 c (hereinafter referred to as “reference coil”) is converted to an electrical angle position It is a value. That is, the first rotor electrical angle ⁇ ER1 is a value obtained by multiplying the rotation angle position of this specific permanent magnet 14a by the number of pole pairs (value 2) of the stator magnetic poles.
- ⁇ ER 2 is a second rotor electrical angle, which is a value obtained by converting the rotational angle position of a specific soft magnetic core 15 a of the second rotor 15 with respect to the above-mentioned reference coil into an electrical angle position. That is, the second rotor electrical angle ⁇ ER2 is a value obtained by multiplying the rotation angle position of this specific soft magnetic core 15a by the number of pole pairs (value 2) of the stator magnetic pole.
- ⁇ ER1 in the above equations (104) to (106) is a first rotor electrical angular velocity, which is a time differential value of ⁇ ER1, that is, a value obtained by converting the angular velocity of the first rotor 14 relative to the stator 16 into an electrical angular velocity.
- ⁇ ER2 is a second rotor electrical angular velocity, which is a value obtained by converting a time differential value of ⁇ ER2, that is, an angular velocity of the second rotor 15 with respect to the stator 16 into an electrical angular velocity.
- the current flowing through the U-phase coil 16c (hereinafter referred to as “the The U-phase current Iu), the current flowing through the V-phase coil 16 d (hereinafter referred to as “V-phase current”) Iv, and the current flowing through the W-phase coil 16 e (hereinafter referred to as “W-phase current”) Iw respectively (107) to (109).
- I represents the amplitude (maximum value) of the current flowing through the U-phase to W-phase coils 16c to 16e.
- the vector of the rotating magnetic field of the stator 16 relative to the reference coil is apparent as is apparent from the equations (95) and (96).
- the electric angular position (hereinafter referred to as “magnetic field electric angular position") .theta.MFR is expressed by the following equation (110), and the electric angular velocity (hereinafter referred to as “magnetic field electric angular velocity”) .omega. It is represented by).
- the relationship among the magnetic field electrical angular velocity ⁇ MFR, the first rotor electrical angular velocity ⁇ ER1, and the second rotor electrical angular velocity ⁇ ER2 is as shown in, for example, FIG.
- first torque the driving equivalent torque TSE and the torque transmitted to the first rotor 14
- second rotor transmission torque the driving equivalent torque TSE and the torque transmitted to the first rotor 14
- FIGS. 111 (a) to (c) to FIGS. 113 (a) and (b) the operation when power is supplied to the stator 16 while the first rotor 14 is held non-rotatable will be described. Do. In FIGS. 111 (a) to (c) to 113 (a) and (b), hatching is applied to only a specific stator magnetic pole and a specific soft magnetic core 15a for easy understanding. It has been subjected.
- the center of the soft magnetic core 15a at the left end in the figure and the center of the permanent magnet 14a at the left end in the figure coincide with each other in the circumferential direction.
- the rotating magnetic field is shown in FIG. It is generated to rotate leftward.
- the positions of the stator poles of the same polarity are made to coincide in the circumferential direction with the centers of the respective permanent magnets 14a whose centers coincide with the soft magnetic core 15a,
- the polarity is set to be different from the polarity of the magnet magnetic pole of the permanent magnet 14a.
- the magnetic field lines ML connect the stator magnetic pole, the soft magnetic core 15a and the magnet magnetic pole whose circumferential positions coincide with each other, and connect these stator magnetic poles, soft magnetic core 15a and It is generated so as to connect the stator magnetic poles on both sides in the circumferential direction of each of the magnet magnetic poles, the soft magnetic core 15a, and the magnet magnetic poles. Further, in this state, since the magnetic force lines ML are linear, no magnetic force acts on the soft magnetic core 15a to rotate it in the circumferential direction.
- the magnetic lines of force ML are bent.
- the magnetic force acts on the soft magnetic core 15a so that In this case, in the soft magnetic core 15a where the magnetic force acts, the magnetic field lines ML are convex in the direction opposite to the rotational direction of the rotational magnetic field (hereinafter referred to as "magnetic field rotational direction") with respect to the straight line connecting the stator magnetic pole and the magnet magnetic pole.
- magnetic field rotational direction the direction opposite to the rotational direction of the rotational magnetic field
- the soft magnetic core 15a is driven in the magnetic field rotation direction and rotates toward the position shown in FIG. 111 (c), and the second rotor 15 provided with the soft magnetic core 15a is also in the magnetic field rotation direction. Rotate.
- the broken lines in FIGS. 111 (b) and 111 (c) indicate that the magnetic flux amount of the magnetic lines of force ML is extremely small and the magnetic connection between the stator magnetic pole, the soft magnetic core 15a, and the magnet magnetic pole is weak. The same applies to the other drawings described later.
- FIGS. 115 (a) to (c) to 117 (a) and (b) the operation when power is supplied to the stator 16 with the second rotor 15 held non-rotatably Will be explained.
- FIGS. 115 (a) to (c) to 117 (a) and (b) hatching is applied to a specific stator magnetic pole and permanent magnet 14a for easy understanding.
- the center of the soft magnetic core 15a at the left end in the figure and the center of the permanent magnet 14a at the left end in the figure are And the center of the soft magnetic core 15a three right next to the soft magnetic core 15a and the center of the permanent magnet 14a four right next to the permanent magnet 14a from the soft magnetic core 15a in the circumferential direction.
- the rotating magnetic field is generated so as to rotate in the left direction in the figure in a state in which they coincide with each other.
- the positions of the stator poles of the same polarity are made to coincide in the circumferential direction with the centers of the respective permanent magnets 14a whose centers coincide with the soft magnetic core 15a,
- the polarity is set to be different from the polarity of the magnet magnetic pole of the permanent magnet 14a.
- the magnetic field lines ML connect the stator magnetic pole, the soft magnetic core 15a and the magnet magnetic pole whose circumferential positions coincide with each other.
- the stator magnetic pole, the soft magnetic core 15a, and the magnet magnetic pole are generated so as to connect the stator magnetic poles on both sides in the circumferential direction of the respective magnetic poles, the soft magnetic core 15a, and the magnetic magnetic pole.
- the magnetic force lines ML are linear, no magnetic force acts on the soft magnetic core 15a to rotate it in the circumferential direction.
- the magnetic lines of force ML are bent.
- the magnetic force acts on the permanent magnet 14a so that
- the permanent magnet 14a is at a position advanced in the magnetic field rotation direction than the extension of the stator magnetic pole and the soft magnetic core 15a mutually connected by the magnetic field line ML
- the magnetic force caused by the magnetic field line ML is the extension It acts to position the permanent magnet 14a on the line. That is, it acts so as to drive the permanent magnet 14a in the direction opposite to the magnetic field rotation direction.
- the permanent magnet 14a is driven in the direction opposite to the magnetic field rotation direction and rotates toward the position shown in FIG. 115 (c), and the first rotor 14 provided with the permanent magnet 14a is also reverse to the magnetic field rotation direction. Rotate in the direction.
- the permanent magnet 14a is positioned at a position where the permanent magnet 14a has advanced in the direction of the magnetic field rotation than the extension of the stator magnetic pole and the soft magnetic core 15a which are curved with each other.
- the magnetic force acts on the permanent magnet 14a so that the permanent magnet 14a and the first rotor 14 rotate in the direction opposite to the magnetic field rotation direction are repeated.
- the power supplied to the stator 16 is motive power by the action of the magnetic force caused by the magnetic lines of force ML as described above.
- the power is output from the first rotor 14.
- the magnetic lines of force ML connecting the magnet magnetic pole, the soft magnetic core 15a, and the stator magnetic pole described above.
- the power supplied to the stator is converted into motive power by the action of the magnetic force due to the magnetic force lines ML, and the motive power is output from the first rotor 14 or the second rotor 15.
- the relationship expressed by the above-mentioned equation (111) is established between the magnetic field electrical angular velocity ⁇ MFR and the first and second rotor electrical angular velocities ⁇ ER1 and ⁇ ER2, and the driving equivalent torque TSE, the first and second The relationship shown in the above-mentioned equation (112) is established between the rotor transmission torques TR1 and TR2.
- the relationship between these three torques TSE, TR1 and TR2 and the relationship between the electrical angular velocity ⁇ MFR, ⁇ ER1 and ⁇ ER2 are the same as the relationship between the torque and the rotational speed in the three elements of the planetary gear system.
- the first rotor 14 and / or the second rotor 15 can be made to the stator 16 When rotated, power is generated in the stator 16 and a rotating magnetic field is generated. At that time, a magnetic line of magnetic force ML connecting the magnet magnetic pole, the soft magnetic body and the stator magnetic pole is generated, and the relationship between the electrical angular velocity shown in equation (111) and the torque shown in equation (112) Relationship is established.
- the relationship between the three torques and the relationship between the three electrical angular velocities is the same as the relationship between the torque and the rotational speed in the three elements of the planetary gear device.
- the first rotating machine 10 can be operated with the same operating characteristics as the planetary gear set.
- the second rotating machine 20 is constituted by a DC brushless motor, and as shown in FIG. 106, the case 21 fixed to the drive system housing described above and the case 21 are accommodated in the case 21 and concentric with the output shaft 13
- the rotor 22 is fixed, and the stator 23 is fixed to the inner peripheral surface of the peripheral wall 21 c of the case 21.
- the case 21 includes left and right side walls 21a and 21b, and a cylindrical peripheral wall 21c fixed to the outer peripheral end of the side walls 21a and 21b.
- Bearings 21d and 21e are attached to inner end portions of the left and right side walls 21a and 21b, respectively, and the output shaft 13 is rotatably supported by the bearings 21d and 21e.
- the rotor 22 includes a rotary table 22a coaxially fixed to the output shaft 13, and a cylindrical ring 22b fixed to the outer end of the rotary table 22a.
- the ring portion 22b is made of a soft magnetic material, and on the outer peripheral surface thereof, permanent magnet arrays are provided along the circumferential direction.
- the permanent magnet array is composed of a predetermined number of permanent magnets 22c, and these permanent magnets 22c are arranged at an interval of the same predetermined angle, and each two adjacent magnets are arranged with different polarities.
- the stator 23 has a plurality of stators 23 a provided along the circumferential direction on the inner peripheral surface of the peripheral wall 21 c of the case 21. These stators 23a generate a rotating magnetic field, are arranged at an interval of the same predetermined angle from each other, and are electrically connected to the battery 33 via a 2ND ⁇ PDU 32 and a VCU 34 described later.
- the power unit 1 includes an ENG-ECU 29 for mainly controlling the engine 3 and a MOT-ECU 30 for mainly controlling the first rotating machine 10 and the second rotating machine 20. Is equipped.
- Each of these ECUs 29 and 30 is configured by a microcomputer (none of which is shown) including a RAM, a ROM, a CPU, an I / O interface, and the like.
- Various sensors such as a crank angle sensor, a drive shaft rotational speed sensor, an accelerator opening degree sensor, and a vehicle speed sensor are connected to the ENG-ECU 29. Based on detection signals of these various sensors, the ENG-ECU 29 operates the engine rotational speed NE, the rotational speed of the drive shaft 8 (hereinafter referred to as "drive shaft rotational speed") ND, and the accelerator opening degree AP (an accelerator pedal not shown) The operation of the engine 3 is controlled by calculating the amount), the vehicle speed VP and the like and driving the fuel injection valve, the spark plug and the like according to these parameters. Furthermore, the ENG-ECU 29 is electrically connected to the MOT-ECU 30, and transmits and receives various data such as the engine rotational speed NE and the drive shaft rotational speed ND with the MOT-ECU 30.
- a 1ST-PDU 31, a 2ND-PDU 32, a first rotation angle sensor 35 and a second rotation angle sensor 36 are connected to the MOT-ECU 30.
- the 1ST • PDU 31 is configured by an electric circuit including an inverter and the like, and is connected to the first rotating machine 10 and the battery 33.
- the 2ND • PDU 32 is configured by an electric circuit including an inverter and the like as in the 1ST • PDU 31 and is connected to the second rotating machine 20 and the battery 33. Both the 1ST • PDU 31 and the 2ND • PDU 32 are connected to the battery 33 via the VCU 34.
- the first rotation angle sensor 35 detects the rotation angle of the first rotor 14 with respect to the stator 16 and outputs a detection signal representing that to the MOT-ECU 30.
- the second rotation angle sensor 36 detects the rotation angle of the second rotor 15 with respect to the stator 16 and outputs a detection signal representing that to the MOT-ECU 30.
- the MOT-ECU 30 controls the operating states of the two rotating machines 10 and 20 as described below according to the detection signals of these sensors and the various data from the ENG-ECU 29 described above.
- the ENG-ECU 29 and the MOT-ECU 30 read data from a memory that stores various maps and the like necessary for performing the control.
- the ENG-ECU 29 or the MOT-ECU 30 derives the temperature of the battery 33 from a signal detected by a battery temperature sensor attached to the exterior body of the battery 33 or the periphery thereof.
- FIG. 118 is a block diagram showing driving force control in a power unit 1 according to a twenty-third embodiment.
- FIG. 119 is a velocity collinear diagram of the power unit 1 having a mechanism of one collinear three elements.
- the ENG • ECU 29 acquires a detection signal indicating the accelerator opening degree AP described above and a detection signal indicating the vehicle speed VP.
- the ENG-ECU 29 uses the driving force map stored in the memory 45 to derives a driving force (hereinafter referred to as "required driving force") according to the accelerator opening AP and the vehicle speed VP.
- the ENG • ECU 29 calculates an output according to the required driving force and the vehicle speed VP (hereinafter referred to as “required output”).
- the required output is an output required for the vehicle to travel in accordance with the driver's accelerator pedal operation.
- the ENG-ECU 29 acquires information on the remaining capacity (SOC: State of Charge) of the battery 33 from the detection signal representing the current / voltage value input / output to / from the battery 33.
- the ENG-ECU 29 determines the ratio of the output of the engine 3 to the required output according to the SOC of the battery 33.
- the ENG-ECU 29 uses the ENG operation map stored in the memory 45 to derive an optimum operating point according to the output of the engine 3.
- the ENG operation map is a map based on BSFC (Brake Specific Fuel Consumption) that indicates the fuel consumption rate at each operating point according to the relationship between the shaft rotational speed of the engine 3 and the torque and the output.
- BSFC Brain Specific Fuel Consumption
- the ENG-ECU 29 derives the shaft rotational speed of the engine 3 at the optimum operating point (hereinafter referred to as “required ENG shaft rotational speed”). Furthermore, the ENG-ECU 29 derives the torque of the engine 3 at the optimal operating point (hereinafter referred to as "ENG required torque").
- the ENG-ECU 29 controls the engine 3 to output the ENG required torque.
- the ENG-ECU 29 detects the shaft rotational speed of the engine 3.
- the shaft rotation speed of the engine 3 detected at this time is referred to as “the actual ENG shaft rotation speed”.
- the ENG ⁇ ECU 29 calculates a difference ⁇ rpm between the required ENG shaft rotational speed and the actual ENG shaft rotational speed.
- the MOT-ECU 30 controls the output torque of the first rotating machine 10 so that the difference ⁇ rpm approaches zero.
- the control is performed by regenerative power generation by the stator 16 of the first rotating machine 10, and as a result, the second rotor 15 of the first rotating machine 10 (MG1) receives the torque shown in the alignment chart of FIG. T12 is added.
- the electric energy (regenerative energy) generated by the regenerative power generation in the stator 16 of the first rotating machine 10 is sent to the 1ST PDU 31.
- the regenerative energy generated by the stator 16 of the first rotating machine 10 is indicated by a dotted line A.
- the MOT-ECU 30 controls the 2ND-PDU 32 so that the torque obtained by subtracting the calculated torque T11 from the previously calculated required driving force is applied to the rotor 22 of the second rotating machine 20.
- torque T22 is applied to the rotor 22 of the second rotating machine 20 (MG2).
- MG2 rotor 22 of the second rotating machine 20
- the torque T11 is applied to the first rotor 14 of the first rotating machine 21 and the torque T22 is applied to the rotor 22 of the second rotating machine 20. Since the first rotor 14 of the first rotating machine 10 and the rotor 22 of the second rotating machine 20 are connected to the output shaft 13, the sum of torque T11 and torque T22 is applied to the front wheels 4, 4 of the vehicle.
- the ENG-ECU 29 and the MOT-ECU 30 control the torque generated in the second rotor 15 of the first rotating machine 10 so that the engine 3 operates at the optimum operating point, and the front wheels of the vehicle
- the torque generated on the rotor 22 of the second rotating machine 20 is controlled so that the required driving force is transmitted to the fourth and fourth motors 4 and 5.
- the vehicle speed VP is used when deriving the required driving force and when deriving the required output, but instead of the vehicle speed VP, information on the number of revolutions of the axle may be used.
- the vehicle is stopped and the engine is stopped
- the rotational resistance of the first rotor 14 is extremely larger than that of the second rotor 15. Due to this, the second rotor 15 rotates in the rotational direction of the rotating magnetic field while the first rotor 14 is stopped. It will be driven. As a result, with the rotation of the rotating magnetic field, the second rotor 15 is driven, whereby the engine 3 can be started.
- start control is executed. First, since the output shaft 13, ie, the first rotor 14 is in the rotation stop state while the vehicle is stopped, all the power generated by the engine 3 is transmitted to the stator 16 of the first rotating machine 10 via magnetic lines. By generating a rotating magnetic field on this, an induced electromotive force (that is, a back electromotive voltage) is generated.
- the MOT-ECU 30 regenerates the induced electromotive force generated in the stator 16 by controlling the supply current to the stator 16, and all the regenerated electric power is transmitted to the second rotating machine 20 via the 1ST-PDU 31 and the 2ND-PDU 32. Supply to As a result, the output shaft 13 is driven by the rotor 22 of the second rotating machine 20 and the front wheels 4 and 4 are driven, whereby the vehicle 2 is started. After the vehicle 2 starts moving, the MOT-ECU 30 controls the regenerative power of the first rotating machine 10 to gradually decrease as the vehicle speed increases, and at the same time controls the regenerative power to be supplied to the second rotating machine 20 .
- shift control is executed.
- the power of engine 3 according to the operating state of engine 3 (for example, engine speed NE and accelerator opening AP) and / or the traveling state of vehicle 2 (for example, vehicle speed VP)
- the first rotary machine 10 is controlled to change the ratio of the power transmitted to the front wheels 4 through the first rotor 14 and the power regenerated as electric power by the first rotary machine 10, and this regeneration is performed.
- the second rotating machine 20 is controlled.
- the first rotating machine 10 since the first rotating machine 10 can be operated with the same operation characteristics as the planetary gear device, the first rotating machine 10 is controlled as described above, and the first rotating machine
- the second rotating machine 20 When the second rotating machine 20 is controlled by supplying the regenerative power at 10 to the second rotating machine 20, if the electrical loss is neglected, through the first rotating machine 10 and the second rotating machine 20, While transmitting all the power of the engine 3 to the front wheel 4, the ratio between the rotational speed of the second rotor 15 and the rotational speed of the output shaft 13, in other words, the ratio between the engine rotational speed NE and the drive shaft rotational speed ND, is arbitrarily changed can do. That is, by controlling the two rotating machines 10 and 20, a function as an automatic transmission can be realized.
- the power regeneration in the first rotating machine 10 is stopped.
- the rotational speed of the rotating magnetic field of the stator 16 is controlled to the value 0 by supplying a lock current to the stator 16 or performing short-circuit control on the first rotating machine 10 or the like.
- all the power of the engine 3 can be transmitted to the front wheel 4 via magnetism within the magnetically transmittable range, so the regenerative power in the first rotating machine 10 can be reduced by 2ND ⁇ PDU 32. Power transmission efficiency can be improved as compared with the case where control is performed so as to supply the second rotating machine 20 via the same.
- the remaining charge SOC of the battery 33 is less than or equal to a predetermined value SOC_REF (for example, 50%) while the engine is running and running (including during deceleration fuel cut), the first rotating machine 10 and / or The regenerative electric power in the two-rotating machine 20 is controlled, and charge control to the battery 33 is executed. As a result, in the battery 33, a sufficient remaining charge amount SOC can be secured.
- SOC_REF for example, 50%
- assist control is performed when a predetermined assist condition is satisfied during engine operation (for example, when starting on a slope, traveling uphill, or accelerating) Is executed.
- the power of the first rotating machine 10 and / or the second rotating machine 20 and the power of the engine 3 are supplied by supplying the power in the battery 33 to the first rotating machine 10 and / or the second rotating machine 20.
- the first rotating machine 10 and / or the second rotating machine 20 are controlled such that power is transmitted to the front wheel 4.
- the assist traveling or the assist start can be performed using the first rotating machine 10 and / or the second rotating machine 20 as a power source.
- a predetermined rotating machine start condition is satisfied (for example, the charge remaining amount SOC of the battery 33 is predetermined
- the rotary machine start control is executed when the accelerator opening AP is equal to or greater than a predetermined value). Specifically, with the engine 3 stopped, the power of the battery 33 is simultaneously supplied to the first rotating machine 10 and the second rotating machine 20, and the two rotating machines 10 and 20 are simultaneously driven.
- the output shaft 13 starts to rotate at the same time as the second rotary machine 20 starts to rotate, but in the first rotary machine 10, the rotational resistance on the second rotor 15 side connected to the stopped engine 3 Is considerably larger than the first rotor 14 side.
- the stator 16 to generate a rotating magnetic field
- the first rotor 14 can be driven, and the power of the first rotating machine 10 and the second rotating machine 20 can start the vehicle 2.
- the rotational resistance of the engine 3 is insufficient, the engine 3 may be locked or a device for increasing the rotational resistance may be provided.
- the vehicle 2 can be driven by using the engine 3, the first rotating machine 10 and the second rotating machine 20 as a power source.
- the first rotary machine 10 may be configured to include only one soft magnetic material row, the first rotary machine 10 can be miniaturized accordingly and the manufacturing cost can be reduced.
- the power plant 1 itself can be miniaturized, the manufacturing cost can be reduced, and the degree of freedom in design can be enhanced.
- three electric angular velocities ⁇ MFR, ⁇ ER1, ⁇ ER2 are determined depending on how to set the pole-log ratio ⁇ , that is, the pole number ratio m in the first rotating machine 10.
- the relationship among the three torques TSE, TR1, and TR2 can be freely set. As a result, the freedom of design can be further enhanced.
- the pole pair ratio ⁇ of the first rotating machine 10 is set to an arbitrary value other than the value 1 and the drive wheel is directly connected to the output shaft 13.
- the electrical angular velocity of the input shaft 12, that is, the second rotor 15 is ⁇ ENG
- the electrical angular velocity of the rotating magnetic field of the stator 16 is ⁇ MG 1
- the relationship is as shown in FIG. 120, for example, and the following equation (114) is established.
- the torque input from the engine 3 to the input shaft 12 is the engine torque TENG
- the torque equivalent to the regenerative electric power of the stator 16 and the electric angular velocity ⁇ MG1 of the rotating magnetic field is the first rotating machine torque TMG1.
- the torque equivalent to the supplied electric power and the electric angular velocity ⁇ MG2 is the second rotating machine torque TMG2
- the torque as the reaction force that the drive wheel receives from the road surface due to the transfer torque to the drive wheel is the drive torque TOUT.
- the relationship between these torques is as shown in FIG. In the following equations (115) and (116), the upward torque in FIG. 120 is represented by a positive value.
- the variation ⁇ TMG1 of the first rotating machine torque TMG1 when the pole pair ratio ⁇ is changed from the first predetermined value ⁇ 1 to the second predetermined value ⁇ 2 is the following equation (121 It is represented by).
- the change amount ⁇ TMG2 of the second rotating machine torque TMG2 when the pole pair ratio ⁇ is changed from the first predetermined value ⁇ 1 to the second predetermined value ⁇ 2 is the following equation (122) It is represented by).
- the pole-log ratio ⁇ is a first predetermined value ⁇ 1.
- the absolute value of the 1st and 2nd rotary machine torque TMG1 and TMG2 will decrease by changing into 2nd predetermined value alpha 2 from the above. That is, it can be understood that the first rotary machine 10 and the second rotary machine 20 can be miniaturized by setting the pole-log ratio ⁇ to a larger value.
- the regenerative power of the first rotating machine 10 is supplied to the second rotating machine 20 as it is, so (123) is established.
- the output ratio RW is 124).
- the twenty-third embodiment is an example in which the power plant 1 is applied to the vehicle 2 provided with the front wheel 4 as a driven part
- the present invention is not limited thereto, and can be applied to various industrial devices such as ships and aircraft. It is.
- a portion generating a propulsive force such as a screw corresponds to a driven portion
- the propulsive force of a propeller or a rotor is used.
- the resulting part corresponds to the driven part.
- the twenty-third embodiment is an example using the engine 3 which is an internal combustion engine fueled with gasoline as the heat engine
- the invention is not limited thereto, and it may be an apparatus for continuously converting heat energy into mechanical energy Just do it.
- the heat engine an internal combustion engine fueled by light oil or natural gas or an external combustion engine such as a Stirling engine may be used.
- the number of stator magnetic poles is “4”, the number of magnetic poles is “8”, and the number of soft magnetic cores 15a as soft magnetic bodies is “6”.
- the number of stator magnetic poles, the number of magnetic poles, and the number of soft magnetic members in the first rotating machine according to the present invention are not limited to these values, but the number of stator magnetic poles, the number of magnetic poles, and soft magnetism
- the ratio of the number of stator magnetic poles to the number of magnetic poles and the number of soft magnetic members that is, the element number ratio is 1: m: (1 + m) It may be set to be / 2.
- the pole number m is not limited thereto, and may be a positive number other than the value 1.
- the twenty-third embodiment is an example in which the magnetic poles of the permanent magnets 14a are used as the magnetic poles of the first rotor 14.
- the first rotor 14 is provided with a stator row, and the magnetic poles generated in the stator rows are the magnetic poles of permanent magnets. It may be used in place of
- the twenty-third embodiment is an example using the MOT-ECU 30, 1ST-PDU 31 and 2ND-PDU 32 as control means for controlling the operation of the first rotating machine 10 and the second rotating machine 20, but the first rotation
- the control means for controlling the machine 10 and the second rotating machine 20 is not limited to this, as long as the operation of these rotating machines 10 and 20 can be controlled.
- an electric circuit or the like equipped with a microcomputer may be used as control means for controlling the two rotating machines 10 and 20.
- the twenty-third embodiment is an example in which the first rotating machine 10 and the second rotating machine 20 are arranged on the output shaft 13 in the axial direction, but the arrangement of the first rotating machine 10 and the second rotating machine 20 is It is not limited to this.
- both may be arranged side by side in the radial direction so that the first rotating machine 10 is positioned outside the second rotating machine 20. In this way, the axial size of the two rotating machines 10 and 20 can be reduced, and the design freedom of the power plant 1 can be increased.
- the first rotor 14 of the first rotating machine 10 and the rotor 22 of the second rotating machine 20 may be disposed on separate axes.
- hatching of the cross section is omitted for easy understanding.
- the rotor 22 is provided not on the output shaft 13 described above but on the first gear shaft 6a. In this way, in the arrangement of the two rotating machines 10 and 20, the design freedom of the power plant 1 can be increased.
- a transmission 50 may be provided instead of the gear mechanism 6.
- the transmission 50 changes the reduction ratio between the output shaft 13 and the front wheel 4 stepwise or steplessly, and the shift operation is controlled by the MOT-ECU 30.
- the transmission 50 includes a stepped automatic transmission with a torque converter, a belt-type continuously variable transmission, a toroidal-type continuously variable transmission and an automatic MT (clutch connection / disconnection operation by an actuator, Any one of stepped automatic transmissions or the like for performing a gear shift operation may be used as appropriate.
- the transmission 51 may be provided in the middle of the input shaft 12 extending between the engine 3 and the second rotor 15.
- the transmission 51 changes the speed increasing ratio between the engine 3 and the second rotor 15 stepwise or steplessly, and the speed change operation is controlled by the MOT-ECU 30.
- any one of a geared automatic transmission with a torque converter, a belt type continuously variable transmission, a toroidal type continuously variable transmission, an automatic MT, etc. may be used as appropriate.
- the speed increase ratio for the low rotation / high load region of the transmission 51 and the final speed reduction ratio of the final reduction gear are both set large.
- the torque to be transmitted to the final reduction gear via the first rotating machine 10 and the second rotating machine 20 can be set small, whereby the first rotating machine 10 and the second rotating machine 20 can be miniaturized. it can.
- the rotational speed of the first rotating machine 10 and the second rotating machine 20 can be reduced by setting the speed increase ratio for the high vehicle speed / high load area in the transmission 51 small (or 1: 1). it can.
- the field rotation number can be reduced, so that energy loss can be reduced, transmission efficiency can be improved, and life can be extended.
- the second rotating machine 20 its operating efficiency can be improved, and its life can be extended.
- the position of the gear mechanism 6 is changed between the first rotor 14 and the rotor 22 of the output shaft 13 and the gear of the output shaft 13
- a transmission 52 may be provided between the mechanism 6 and the rotor 22.
- the transmission 52 changes the reduction ratio between the rotor 22 and the gear 6 c stepwise or steplessly, and the shift operation is controlled by the MOT-ECU 30.
- the transmission 52 as with the transmission 50 described above, any one of a stepped automatic transmission with a torque converter, a belt-type continuously variable transmission, a toroidal-type continuously variable transmission, an automatic MT, etc. may be suitably used. Used.
- the torque to be transmitted from the second rotating machine 20 to the front wheel 4 can be set small.
- the second rotating machine 20 can be miniaturized.
- the rotational speed of the second rotating machine 20 can be reduced by setting the reduction ratio for the high vehicle speed and high load area small in the transmission 52, thereby improving the operating efficiency as described above. As well as being able to extend the life.
- the power is supplied from the battery 33 to the first rotating machine 10 and / or the second rotating machine 20, and the first rotating machine 10 and The power generated by the second rotating machine 20 is charged to the battery 33. Further, as described above, the ENG-ECU 29 and the MOT-ECU 30 calculate the state of charge of the battery 33 based on a detection signal from a current / voltage sensor (not shown).
- the battery 33 is configured by a secondary battery such as a nickel hydrogen battery or a lithium ion battery.
- a secondary battery such as a nickel hydrogen battery or a lithium ion battery.
- SOC State of Charge
- the ENG-ECU 29 and the MOT-ECU 30 perform control according to the SOC of the battery 33 (hereinafter referred to as "battery SOC").
- FIG. 127 is a diagram showing the range of the battery SOC in which charge and discharge are repeated. As shown in FIG. 127, the ENG-ECU 29 and the MOT-ECU 30 control the operation of the engine 3 and the first and second rotating machines 10 and 20 so that the battery SOC falls within the range from the lower limit SOC to the upper limit SOC. Do.
- FIGS. 128 (a) and 128 (b) are (a) velocity alignment charts when the battery SOC is less than the first threshold when the operation mode of the operation device 1 is "engine running", and (b) The speed alignment chart when battery SOC is more than a 1st threshold value is shown. As shown in FIG.
- the first magnetic field rotational speed VMF1 of the first rotating magnetic field in the stator 16 of the first rotating machine 10 is as shown in FIG. It is controlled to be lower than the first magnetic field rotational speed VMF1 shown in FIG.
- the regenerative energy generated by the first rotating machine 10 in the case shown in FIG. 128 (b) is lower than the regenerative energy in the case shown in FIG. 128 (a).
- the ENG-ECU 29 operates the engine 3 so that it operates with the shaft rotation speed lower than the required ENG shaft rotation speed and without changing the output torque.
- the charge amount to the battery 33 is reduced. Therefore, when the battery SOC is equal to or greater than the first threshold value close to the upper limit SOC, the ENG • ECU 29 performs the control to prevent overcharging of the battery 33.
- the output of the engine 3 is reduced.
- the torque from the second rotating machine 20 is applied, the output torque transmitted to the drive wheels 4 and 4 does not change.
- the torque required of the engine 3 by the ENG • ECU 29 at the time of the control described above may be less than the ENG required torque described with reference to FIG.
- the ENG-ECU 29 controls the engine 3 to output a torque according to the shaft rotational speed at the time of the above control.
- the torque at the optimum operating point when the shaft rotation speed of the engine 3 is low is approximately proportional to the shaft rotation speed, so the torque at this time is smaller than the ENG required torque. With such control, the output of the engine 3 is further reduced, but the engine 3 can be operated at the optimum operating point.
- the engine 3 is controlled to operate at a shaft rotation number lower than the required ENG shaft rotation number of the engine 3.
- the regenerative energy per unit time generated in the stator 16 of the first rotating machine 10 with respect to the torque required for the engine 3 exceeds the specified value, it is lower than the ENG required torque described with reference to FIG.
- the engine 3 may be controlled to output a torque.
- the shaft rotational speed of the engine 3 may be equal to or less than the required ENG shaft rotational speed described with reference to FIG.
- 129 (a) and 129 (b) are (a) a speed alignment chart when the battery SOC is higher than the second threshold when the operation mode of the operating device 1 is "EV travel", and (b) the battery The velocity alignment chart when SOC is below a 2nd threshold value is shown. As shown in FIG. 129 (b), when the engine 3 is driven, regenerative energy is generated in the first rotating machine 10.
- the operation mode of the operation device 1 is “EV travel”
- the amount of discharge of the battery 33 is reduced by controlling the engine 3 to operate. Therefore, when the battery SOC is equal to or less than the second threshold value close to the lower limit SOC, the ENG • ECU 29 performs the control to prevent the overdischarge of the battery 33.
- the second threshold is variable.
- the energy required for the first rotating machine 10 to start the engine 3 varies depending on the vehicle speed VP, and the higher the vehicle speed VP, the greater the energy required. Therefore, the ENG • ECU 29 sets a second threshold value corresponding to the vehicle speed VP. That is, the ENG • ECU 29 sets the second threshold value higher as the vehicle speed VP is higher.
- FIGS. 130 (a) and 130 (b) are (a) velocity alignment charts when the battery SOC is less than the first threshold when the operation mode of the operation device 1 is “ENG backward start”, and (b) The speed alignment chart when battery SOC is more than a 1st threshold value is shown. As shown in FIG.
- the first magnetic field rotational speed VMF1 of the first rotating magnetic field in the stator 16 of the first rotating machine 10 is as shown in FIG. It is controlled to be lower than the first magnetic field rotational speed VMF1 shown in FIG. As a result, the regenerative energy generated in the first rotating machine 10 is reduced.
- the ECU 2 controls the engine 3 to operate at the shaft rotation speed lower than the required ENG shaft rotation speed and without changing the output torque.
- the charge amount to the battery 33 is reduced. Therefore, when the battery SOC is equal to or greater than the first threshold value close to the upper limit SOC, the ENG • ECU 29 performs the control to prevent overcharging of the battery 33.
- the output of the engine 3 is reduced. However, since the output torque of the engine 3 does not change, the output torque transmitted to the drive wheels 4 and 4 does not change.
- the torque required of the engine 3 by the ENG • ECU 29 at the time of the control described above may be less than the ENG required torque described with reference to FIG.
- the ENG-ECU 29 controls the engine 3 to output a torque according to the shaft rotational speed at the time of the above control.
- the torque at the optimum operating point when the shaft rotation speed of the engine 3 is low is approximately proportional to the shaft rotation speed, so the torque at this time is smaller than the ENG required torque. With such control, the output of the engine 3 is further reduced, but the engine 3 can be operated at the optimum operating point.
- the engine 3 is controlled to operate at a shaft rotation number lower than the required ENG shaft rotation number of the engine 3.
- the energy per unit time generated by the stator 16 of the first rotating machine 10 with respect to the torque required for the engine 3 exceeds the specified value, a torque lower than the ENG required torque described with reference to FIG.
- the engine 3 may be controlled to output the At this time, the shaft rotational speed of the engine 3 may be equal to or less than the required ENG shaft rotational speed described with reference to FIG.
- a power plant 1A according to a twenty-fourth embodiment will be described with reference to FIG.
- the power plant 1A is different from the power plant 1 of the twenty-third embodiment in that the second rotary machine 20 is used as a power source for driving the rear wheel, and other points are different.
- the power plant 1 according to the twenty-third embodiment is configured in substantially the same manner, and therefore, different points from the power plant 1 according to the twenty-third embodiment will be mainly described below. I omit explanation.
- the gear 6d on the first gear shaft 6a is always in mesh with the gear 7a of the differential gear mechanism 7, whereby the rotation of the output shaft 13 is achieved by the gears 6c and 6d and the differential gear mechanism 7. Is transmitted to the front wheels 4, 4.
- the second rotating machine 20 is connected to the left and right rear wheels 5, 5 via the differential gear mechanism 25 and the left and right drive shafts 26, 26, etc.
- the second rotating machine 20 The power of the rotating machine 20 is transmitted to the rear wheels 5 and 5 (second driven parts).
- the rotor 22 of the second rotating machine 20 is concentrically fixed to the left end of the gear shaft 24, and the gear 24 a is concentrically fixed to the gear shaft 24 at the right end of the gear shaft 24.
- the gear 24 a is in constant mesh with the gear 25 a of the differential gear mechanism 25.
- the same function and effect as the power unit 1 of the twenty-third embodiment can be obtained.
- the electric power regenerated by the first rotating machine 10 is supplied to the second rotating machine 20, whereby the vehicle can be started in the all-wheel drive state.
- the startability on the low ⁇ road can be improved.
- traveling can be performed in the all-wheel drive state, so traveling stability on a low ⁇ road can be improved.
- the transmission 53 is provided in the middle of the input shaft 12 extending between the engine 3 and the second rotor 15, and the transmission 54 is a gear. It may be provided between the gear 24 a of the shaft 24 and the rotor 22.
- the transmission 53 changes the speed increase ratio between the engine 3 and the second rotor 15 stepwise or steplessly, and the shift operation is controlled by the MOT-ECU 30.
- the transmission 54 changes the reduction ratio between the second rotary machine 20 and the rear wheel 5 stepwise or steplessly, and the transmission operation is controlled by the MOT-ECU 30.
- the transmissions 53 and 54 like the transmission 50 described above, any one of a geared automatic transmission with a torque converter, a belt type continuously variable transmission, a toroidal type continuously variable transmission, an automatic MT, etc. It is used suitably.
- the speed increase ratio for the low rotation / high load region of the transmission 53 and the final speed reduction ratio of the final reduction gear are both set large.
- the torque to be transmitted to the final reduction gear via the single rotation machine 10 can be set small, whereby the first rotation machine 10 can be miniaturized.
- the rotational speed of the first rotating machine 10 can be reduced by setting the speed increase ratio for the high vehicle speed / high load area in the transmission 53 small (or 1: 1).
- the field rotation number can be reduced, so that energy loss can be reduced, transmission efficiency can be improved, and life can be extended.
- the generated torque of the second rotating machine 20 can be set small, whereby the second rotating machine 20 can be set. It can be miniaturized.
- the rotational speed of the second rotating machine 20 can be reduced by setting the reduction ratio for the high vehicle speed and high load region in the transmission 54 small.
- the two transmissions 53 and 54 are provided in the power plant 1A, one of the transmissions 53 and 54 may be omitted.
- the power plant 1 B differs from the power plant 1 of the twenty-third embodiment in that the second rotary machine 20 and 2ND ⁇ PDU 32 etc. are omitted and an electromagnetic brake 55 is added. Since the other structure is substantially the same as that of the power plant 1 according to the twenty-third embodiment, the following description will mainly focus on the differences from the power plant 1 according to the twenty-third embodiment. The explanation is omitted.
- the gear 6d on the first gear shaft 6a is always meshed with the gear 7a of the differential gear mechanism 7 similarly to the power unit 1A of the twenty-fourth embodiment described above, and thereby the output shaft 13 Is transmitted to the front wheels 4, 4 via the gears 6c, 6d and the differential gear mechanism 7.
- the electromagnetic brake 55 (stopping device) is provided between the first rotating machine 10 of the input shaft 12 and the engine 3 and is electrically connected to the MOT-ECU 30.
- the electromagnetic brake 55 is switched ON / OFF by the MOT-ECU 30, and allows rotation of the input shaft 12 in the OFF state, and stops rotation of the input shaft 12 in the ON state.
- the electromagnetic brake 55 is controlled to be in the ON state only at the time of rotary machine start control described later, and is held in the OFF state in various controls other than the rotary machine start control.
- This engine start control is to start the engine 3 by the power of the first rotating machine 10 when the predetermined engine start condition described above is satisfied when the engine is stopped and the vehicle is at rest. Specifically, when the predetermined starting condition is satisfied, the power of the battery 33 is supplied to the first rotating machine 10 via the VCU 34 and the 1ST • PDU 31. Thereby, as described above, the second rotor 15 is driven while the first rotor 14 is stopped, and as a result, the engine 3 is started.
- the start control is executed.
- the start control when a predetermined start condition is satisfied, first, the power of the engine 3 is regenerated (ie, generated) as electric power in the first rotating machine 10. Then, after the start of the power regeneration, the first rotating machine 10 is controlled such that the regenerated power decreases.
- the vehicle 2 can be started by the power of the engine 3 while avoiding the engine stall.
- distribution control of engine power is performed during traveling while the engine is operating.
- the first rotor of the motive power of engine 3 according to the operating state of engine 3 (engine speed NE and accelerator opening AP, etc.) and / or the traveling state of vehicle 2 (vehicle speed VP, etc.)
- the first rotating machine 10 is controlled to change the ratio of the power transmitted to the front wheels 4 through 14 and the power regenerated as electric power by the first rotating machine 10.
- the vehicle 2 can be caused to travel while appropriately controlling the regenerative power according to the driving state of the engine 3 and / or the traveling state of the vehicle 2.
- the first rotating machine 10 is controlled such that the rotational speed of the rotating magnetic field of the stator 16 becomes zero.
- the motive power of the engine 3 can be all magnetically transmitted to the front wheel 4 through the second rotor 15 and the first rotor 14 as long as it is within the magnetically transmittable range.
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Abstract
Description
以下、図面を参照しながら、本発明に係る1共線4要素の仕組みを有する動力装置の実施形態について説明する。なお、図面中の断面を示す部分については、ハッチングを適宜、省略するものとする。
図1および図2は、第1実施形態による動力装置1を概略的に示している。この動力装置1は、車両(図示せず)の左右の駆動輪DW,DW(被駆動部)を駆動するためのものであり、図1に示すように、動力源である内燃機関3(熱機関)、第1回転機21および第2回転機31と、駆動輪DW,DWに駆動軸10,10を介して連結された差動ギヤ機構9と、第1パワードライブユニット(以下「第1PDU」という)41および第2パワードライブユニット(以下「第2PDU」という)42と、双方向型昇降圧コンバータ(以下「VCU」という)44とを備えている。また、動力装置1は、図2に示すように、内燃機関3や第1および第2の回転機21,31の動作を制御するためのECU2を備えている。第1および第2の回転機21,31は、後述するように無段変速装置としても機能する。
(A)第1ステータがU相、V相およびW相の3相コイルを有する
(B)第1ステータ磁極が2個、第1磁極が4個、すなわち、第1ステータ磁極のN極およびS極を1組とする極対数が値1、第1磁極のN極およびS極を1組とする極対数が値2であり、第1軟磁性体が第1コア、第2コアおよび第3コアから成る3つの軟磁性体で構成されている
なお、このように、本明細書で用いる「極対」は、N極およびS極の1組をいう。
TGE1=TRA1/α=-TRA2/(α+1)
=TRA1/2=-TRA2/3 ……(42)
また、ステータ23への電力供給中および発電中、第1回転磁界の回転速度(以下「第1磁界回転速度VMF1」という)と、A1およびA2のロータ24,25の回転速度(以下、それぞれ「A1ロータ回転速度VRA1」「A2ロータ回転速度VRA2」という)の間に、次式(43)が成立する。
VMF1=(α+1)VRA2-α・VRA1
=3・VRA2-2・VRA1 ……(43)
以上から明らかなように、第1回転機21は、遊星歯車装置と一般的な1ロータタイプの回転機とを組み合わせた装置と同じ機能を有する。
第2回転機31は、第1回転機21と同様に構成されており、以下、その構成と動作について簡単に説明する。図1および図18に示すように、第2回転機31は、ステータ33と、ステータ33に対向するように設けられたB1ロータ34と、両者33,34の間に設けられたB2ロータ35を有している。これらのステータ33、B2ロータ35およびB1ロータ34は、径方向に、外側からこの順で並んでおり、同心状に配置されている。図18では、図3と同様、第1回転軸4などの一部の要素を、図示の便宜上、スケルトン図的に描いている。
VMF2=(β+1)VRB2-β・VRB1
=3・VRB2-2・VRB1 ……(44)
TSE2=TRB1/β=-TRB2/(β+1)
=TRB1/2=-TRB2/3 ……(45)
TGE2=TRB1/β=-TRB2/(1+β)
=TRB1/2=-TRB2/3 ……(46)
以上のように、第2回転機31は、第1回転機21と同様、遊星歯車装置と一般的な1ロータタイプの回転機とを組み合わせた装置と同じ機能を有する。
ECU2は、バッテリ43の出力電圧又はバッテリ43への充電電圧を昇圧又は降圧するVCU44を制御する。ECU2によるVCU44の制御によって、VCU44の変圧比等が変更される。また、ECU2は、第1PDU41を制御することによって、第1回転機21のステータ23に供給される電力と、電力の供給に伴ってステータ23で発生する第1回転磁界の第1磁界回転速度VMF1を制御する。さらに、ECU2は、第1PDU41を制御することによって、ステータ23で発電する電力と、発電に伴ってステータ23で発生する第1回転磁界の第1磁界回転速度VMF1を制御する。
Tg1=-{β・TOUT+(β+1)TDHE}/(α+1+β) ……(47)
Tg2=-{α・THE+(1+α)TOUT}/(β+α+1) ……(48)
以下、上記説明した1共線4要素の仕組みを有する動力装置1においてECU2が行う駆動力制御について、図23及び図24を参照して説明する。図23は、第1実施形態の動力装置1における駆動力制御を示すブロック線図である。また、図24は、1共線4要素の仕組みを有する動力装置1における速度共線図である。
T11=α/(1+α)×T12 …(49)
T21=β/(1+β)×T22 …(50)
次に、ECU2による制御によって行われる動力装置1の動作について説明する。この動力装置1の動作モードには、EVクリープ、EV発進、EV走行中ENG始動、ENG走行、減速回生、停車中ENG始動、ENGクリープ、ENG発進、EV後退発進およびENG後退発進が含まれる。以下、これらの動作モードについて、図25などのトルクの伝達状況を示す図や、図26(a)、(b)などの各種の回転要素の回転速度の関係を示す速度共線図を参照しながら、EVクリープから順に説明する。この動作モードの説明の前に、これらの速度共線図について説明する。
このEVクリープは、エンジン3を停止した状態で、第1および第2の回転機21,31を用いて、車両のクリープ運転を行う動作モードである。具体的には、第2回転機31のステータ33に、バッテリ43から電力を供給するとともに、それに伴ってステータ33で発生する第2回転磁界を正転させる。また、第1回転機21のA1ロータ24に後述するように伝達される動力を用いて、第1回転機21のステータ23で発電を行うとともに、発電した電力を、ステータ33にさらに供給する。
このEV発進は、上述したEVクリープ中から、エンジン3を停止した状態で、第1および第2の回転機21,31を用いて、車両を発進させ、走行させる動作モードである。EV発進時、第2回転機31のステータ33に供給される電力および第1回転機21のステータ23で発電する電力をいずれも増大させる。さらに、式(43)および(44)に示す回転速度の関係を維持し、かつA2およびB1のロータ回転速度VRA2,VRB1すなわちエンジン回転数NEを値0に保持しながら、EVクリープ中に逆転していた第1回転磁界の第1磁界回転速度VMF1と、正転していた第2回転磁界の第2磁界回転速度VMF2をそれぞれ、それまでと同じ回転方向に上昇させる。以上により、図28(a)、(b)に太い実線で示すように、A1およびB2のロータ回転速度VRA1,VRB2、すなわち車速VPが、同図に破線で示すEVクリープ状態から上昇し、車両が発進する。なお、EV発進中におけるトルクの伝達状況は、図27に示すように、図25に示したEVクリープ中におけるトルクの伝達状況と同じである。
このEV走行中ENG始動は、上述したEV発進による車両の走行中に、エンジン3を始動する動作モードである。EV走行中ENG始動時、A1およびB2のロータ回転速度VRA1,VRB2、すなわち車速VPをそのときの値に保持しながら、EV発進時に上述したように逆転していた第1回転磁界の第1磁界回転速度VMF1を、値0になるように制御するとともに、正転していた第2回転磁界の第2磁界回転速度VMF2を、低下させるように制御する。そして、第1磁界回転速度VMF1が値0になった後には、第2回転機31のステータ33に加え、第1回転機21のステータ23にも、バッテリ43から電力を供給し、ステータ23で発生する第1回転磁界を正転させるとともに、第1磁界回転速度VMF1を上昇させる。
TGE1=-{β・TDDW+(β+1)TDENG}/(α+1+β)……(51)
このENG走行は、エンジン3の動力を用いて、車両を走行させる運転モードである。ENG走行中、エンジン3における燃焼によってクランク軸3aに出力される動力(以下「エンジン動力」という)を、基本的には、要求トルクを発生できる範囲で、最良の燃費(以下「最良燃費」という)が得られるように制御する。この要求トルクは、車両に要求されるトルクであり、例えば、検出された車速VPおよびアクセル開度APに応じ、マップ(図示せず)を検索することによって算出される。また、ENG走行中、A2ロータ25に伝達されるエンジン動力を用いて、第1回転機21のステータ23で発電を行うとともに、発電した電力を、バッテリ43に充電せずに、第2回転機31のステータ33に供給する。以下、この運転モードを「バッテリ入出力ゼロモード」という。図32は、このバッテリ入出力ゼロモードにおけるトルクの伝達状況を示している。
第1伝達経路:A2ロータ25→磁力線MLによる磁力→A1ロータ24→連結軸6→B2ロータ35
第2伝達経路:B1ロータ34→磁力線MLによる磁力→B2ロータ35
第3伝達経路:A2ロータ25→磁力線MLによる磁力→ステータ23→第1PDU41→第2PDU42→ステータ33→磁力線MLによる磁力→B2ロータ35
(a)要求トルク>第1所定値
(b)充電状態>下限値
ここで、第1所定値は、例えば、車速VPに応じ、マップ(図示せず)を検索することによって算出される。このマップでは、第1所定値は、そのときの車速VPに対して、エンジン3の最良燃費が得られるようなトルク値に設定されている。上記の下限値は、バッテリ43が過放電にならないような値に設定されている。このように、アシストモードによる運転は、そのときの車速VPおよび要求トルクで表される車両を駆動するのに必要な動力(以下「車両要求動力」という)が、最良燃費が得られるエンジン動力よりも大きいときに、かつバッテリ43に電力が十分に残っているときに行われる。
(c)要求トルク<第2所定値
(d)充電状態<上限値
ここで、第2所定値は、例えば、車速VPに応じ、マップ(図示せず)を検索することによって算出される。このマップでは、第2所定値は、そのときの車速VPに対して、最良燃費が得られるようなトルク値よりも小さな値に設定されている。上限値は、バッテリ43が過充電にならないような値に設定されている。このように、駆動時充電モードによる運転は、車両要求動力が、最良燃費が得られるエンジン動力よりも小さいときに、かつ充電状態が比較的小さいときに行われる。
TGE2=-{α・TENG+(1+α)TDDW}/(β+1+α) ……(52)
この減速回生は、車両の減速走行中、すなわち車両が惰性で走行しているときに、駆動輪DW,DWの慣性エネルギを用いて、第1回転機21や第2回転機31において発電を行うとともに、発電した電力をバッテリ43に充電する動作モードである。減速回生中、駆動輪DW,DWのトルク(慣性によるトルク)に対する、エンジン3に伝達される駆動輪DW,DWのトルクの割合が小さいときには、駆動輪DW,DWの動力の一部を用いて両ステータ23,33で発電を行うとともに、発電した電力をバッテリ43に充電する。具体的には、この発電は、第1回転機21のステータ23では、A2ロータ25に後述するように伝達される動力を用いて行われ、第2回転機31のステータ33では、B2ロータ35に後述するように伝達される動力を用いて行われる。
この停車中ENG始動は、車両の停止中に、エンジン3を始動する動作モードである。停車中ENG始動時、第1回転機21のステータ23に、バッテリ43から電力を供給し、それに伴ってステータ23で発生する第1回転磁界を正転させるとともに、B1ロータ34に後述するように伝達される動力を用いて、ステータ33で発電を行い、発電した電力をステータ23にさらに供給する。
このENGクリープは、エンジン動力を用いて、車両のクリープ運転を行う動作モードである。ENGクリープ中、A2ロータ25に伝達されるエンジン動力を用いて、ステータ23で発電を行うとともに、B1ロータ34に伝達されるエンジン動力を用いて、ステータ33で発電を行う。また、このように両ステータ23,33で発電した電力を、バッテリ43に充電する。
このENG発進は、エンジン動力を用いて車両を発進させる動作モードである。図43は、このENG発進時におけるトルクの伝達状況を示している。ENG発進時、ENGクリープ中に逆転していた第2回転磁界の第2磁界回転速度VMF2を、値0になるように制御し、正転していた第1回転磁界の第1磁界回転速度VMF1を上昇させるとともに、エンジン動力を増大させる。そして、第2磁界回転速度VMF2が値0になった後には、前述したバッテリ入出力ゼロモードによる運転を行う。以上により、図44(a)、(b)に太い実線で示すように、A1およびB2のロータ回転速度VRA1,VRB2すなわち車速VPが、同図に破線で示すENGクリープ状態から上昇し、車両が発進する。
このEV後退発進は、エンジン3を停止した状態で、第1および第2の回転機21,31を用いて、車両を後退発進させ、走行させる動作モードである。図45は、EV後退発進中におけるトルクの伝達状況を示している。また、図46(a)は、このEV後退発進中における第1および第2の回転機21,31の各速度共線図の一例を、図46(b)は、図46(a)に示した2つの速度共線図を合成した速度共線図を、それぞれ示している。
このENG後退発進は、エンジン動力を用いて車両を後退発進させる動作モードである。図47は、このENG後退発進中におけるトルクの伝達状況を示している。ENG後退発進時、ENGクリープ中に逆転していた第2回転磁界の第2磁界回転速度VMF2がさらに負の方向に上昇するよう制御し、かつ、正転していた第1回転磁界の第1磁界回転速度VMF1を上昇させるとともに、エンジン動力を増大させる。以上により、図48(a)、(b)に太い実線で示すように、車速VPが同図に破線で示すENGクリープ状態から負の方向に上昇し、車両が後退発進する。
上記説明したように、本実施形態の動力装置1の動作モードに応じて、バッテリ43から第1回転機21および/または第2回転機31に電力が供給され、また、第1回転機21および/または第2回転機31で発電された電力がバッテリ43に充電される。また、上記説明したように、ECU2は、電流電圧センサ56からの検出信号に基づいてバッテリ43の充電状態を算出する。
動作装置1の動作モードが「ENG発進」のとき、図43に示したように、第1回転機21のステータ23では回生発電が行われる。また、図44(a)、(b)に破線で示したように、動作装置1がENG発進の動作を行った直後、第2回転機31のステータ33における第2回転磁界の回転方向は逆転方向であり、ステータ33からは正のトルクがB2ロータ35に作用されるため、ステータ33でも回生発電が行われる。このとき、バッテリ43は、第1回転機21および第2回転機31の双方からの回生エネルギによって充電される。
動作装置1の動作モードが「EV走行」のとき、図27に示したように、第2回転機31のステータ33は力行運転状態であり、第1回転機21のステータ23では回生発電が行われる。第1回転機21の回生発電で得られた回生エネルギはステータ33に送られるが、足りない電力はバッテリ43から供給される。
動作装置1の動作モードが「ENG後退発進」のとき、図47に示したように、第2回転機31のステータ33は力行運転状態であり、第1回転機21のステータ23では回生発電が行われる。第1回転機21の回生発電で得られた回生エネルギはステータ33に送られるが、足りない電力はバッテリ43から供給される。
次に、図53~図56を参照しながら、第2~第5の実施形態による動力装置1A,1B,1C,1Dについて説明する。これらの動力装置1A~1Dはそれぞれ、第1実施形態と比較して、変速装置61,71,81,91をさらに備える点が主に異なっており、第2~第5の実施形態のいずれにおいても、エンジン3と第1および第2の回転機21,31と駆動輪DW,DWの間の連結関係は、第1実施形態と同様である。すなわち、A2およびB1のロータ25,34がエンジン3のクランク軸3aに機械的に連結されるとともに、A1およびB2のロータ24,35が駆動輪DW,DWに機械的に連結されている。また、図53~図56において、第1実施形態と同じ構成要素については、同じ符号を用いて示している。このことは、後述する他の実施形態を説明するための図においても同様に当てはまる。以下、第2実施形態の動力装置1Aから順に、第1実施形態と異なる点を中心に説明する。
図53に示すように、この動力装置1Aでは、変速装置61は、前述した互いに噛み合うギヤ7bおよび第1ギヤ8bに代えて設けられている。この変速装置61は、ベルト式の無段変速装置であり、前述した第2回転軸7に連結された入力軸と、アイドラ軸8に連結された出力軸と、入力軸および出力軸にそれぞれ設けられたプーリと、これらのプーリに巻きかけられた金属ベルト(いずれも図示せず)を有している。変速装置61は、これらのプーリの有効径を変更することによって、この入力軸に入力された動力を、変速した状態で出力軸に出力する。また、変速装置61の変速比(入力軸の回転数/出力軸の回転数)はECU2によって制御される。
図54に示す第3実施形態の動力装置1Bでは、変速装置71は、ギヤ式の有段変速装置であり、入力軸72および出力軸(図示せず)と、ギヤ比が互いに異なる複数のギヤ列と、これらの複数のギヤ列と入力軸72および出力軸との間をギヤ列ごとに接続・遮断するクラッチ(いずれも図示せず)を有している。変速装置71は、この入力軸72に入力された動力を、これらの複数のギヤ列の1つによって変速した状態で、出力軸に出力する。また、変速装置71では、これらの複数のギヤ列によって、前進用の第1速(変速比=入力軸72の回転数/出力軸の回転数>1.0)、第2速(変速比=1.0)および第3速(変速比<1.0)と、後進用の1つの変速段から成る計4つの変速段が設定され、その変更はECU2によって制御される。
図55に示す第4実施形態の動力装置1Cでは、第1実施形態と異なり、第2回転軸7にギヤ7bが設けられておらず、前述した第1ギヤ8bは、連結軸6に一体に設けられたギヤ6bに噛み合っている。これにより、A1ロータ24は、連結軸6、ギヤ6b、第1ギヤ8b、アイドラ軸8、第2ギヤ8c、ギヤ9a、および、差動ギヤ機構9などを介して、変速装置81を介さずに、駆動輪DW,DWに連結されている。
図56に示す第5実施形態による動力装置1Dでは、変速装置91は、遊星歯車装置などで構成されたギヤ式の有段変速装置であり、入力軸92および出力軸(図示せず)を有しており、変速段として、第1速(変速比=入力軸92の回転数/出力軸の回転数=1.0)と第2速(変速比<1.0)から成る計2つの変速段が設定されている。これらの変速段の変更はECU2によって行われる。
次に、図57を参照しながら、第6実施形態による動力装置1Eについて説明する。同図に示すように、この動力装置1Eは、第1実施形態の動力装置1にブレーキ機構BLを加えたものである。以下、第1実施形態と異なる点を中心に説明する。
次に、図58を参照しながら、第7実施形態による動力装置1Fについて説明する。この動力装置1Fは、第1実施形態の動力装置1と比較して、第2回転機31を、一般的なシングルピニオンタイプの第1遊星歯車装置PS1と一般的な1ロータタイプの回転機101に置き換えた点のみが異なっている。なお、同図において、第1実施形態と同じ構成要素については、同じ符号を用いて示している。このことは、後述する他の実施形態についても同様である。以下、第1実施形態と異なる点を中心に説明する。
VRI1=(r1+1)VCA1-r1・VSU1 ……(53)
ここで、VRI1は、第1リングギヤR1の回転速度(以下「第1リングギヤ回転速度」という)であり、VCA1は、第1キャリアC1の回転速度(以下「第1キャリア回転速度」という)であり、VSU1は、第1サンギヤS1の回転速度(以下「第1サンギヤ回転速度」という)である。
Tg=-{X・TOUT+(X+1)TDHE}/(α+1+X) ……(54)
TM2=-{α・THE+(1+α)TOUT}/(X+1+α) ……(55)
TM2=-{α・TOUT+(1+α)TDHE}/(X+α+1) ……(56)
Tg=-{X・THE+(1+X)TOUT}/(α+1+X) ……(57)
T11=α/(1+α)×T12 …(58)
T21=β/(1+β)×T22 …(59)
EVクリープ中には、回転機101のステータ102に、バッテリ43から電力を供給するとともに、ロータ103を正転させる。また、第1回転機21のA1ロータ24に後述するように伝達される動力を用いて、ステータ23で発電を行うとともに、発電した電力を、ステータ102にさらに供給する。これに伴い、回転機101のロータ103に出力されたトルク(以下「回転機トルク」という)は、第1キャリアC1を正転させるように作用するとともに、第1サンギヤS1を逆転させるように作用する。また、第1キャリアC1に伝達されたトルクの一部は、第2回転軸7などを介して駆動輪DW,DWに伝達され、それにより、駆動輪DW,DWが正転する。
EV発進時には、回転機101のステータ102に供給される電力および第1回転機21のステータ23で発電する電力をいずれも増大させる。さらに、式(43)および(53)に示すような回転速度の関係を維持し、エンジン回転数NEを値0に保持しながら、EVクリープ中に逆転していた第1回転磁界の第1磁界回転速度VMF1と、正転していたロータ103のロータ回転速度をそれぞれ、それまでと同じ回転方向に上昇させる。以上により、車速VPが上昇し、車両が発進する。
EV走行中ENG始動時には、車速VPをそのときの値に保持しながら、EV発進時に上述したように逆転していた第1回転磁界の第1磁界回転速度VMF1を、値0になるように制御するとともに、正転していたロータ103のロータ回転速度を、低下させるように制御する。そして、第1磁界回転速度VMF1が値0になった後には、回転機101のステータ102に加え、第1回転機21のステータ23にも、バッテリ43から電力を供給し、ステータ23で発生する第1回転磁界を正転させるとともに、第1磁界回転速度VMF1を上昇させる。
TGE1=-{r1・TDDW+(1+r1)TDENG}/(α+1+r1)……(60)
ENG走行中には、第1実施形態で述べた実行条件に応じて、バッテリ入出力ゼロモードや、アシストモード、駆動時充電モードによる運転が行われる。このバッテリ入出力ゼロモード中、A2ロータ25に伝達されるエンジン動力を用いて、第1回転機21のステータ23で発電を行うとともに、発電した電力を、バッテリ43に充電せずに、回転機101のステータ102に供給する。この場合、第1実施形態と同様、エンジントルクTENGの一部が、A2ロータ25を介して、ステータ23およびA1ロータ24に分配される。また、エンジントルクTENGの残りは、第1回転軸4を介して第1サンギヤS1に伝達される。さらに、上述したEV走行中ENG始動時と同様、回転機トルクTMOTと、第1サンギヤS1に上記のように伝達されたトルクは、合成され、第1キャリアC1に伝達される。また、第1キャリアC1には、A1ロータ24に上記のように分配されたエンジントルクTENGが、連結軸6を介してさらに伝達される。
第1伝達経路:A2ロータ25→磁力線MLによる磁力→A1ロータ24→連結軸6→第1キャリアC1
第2伝達経路:第1サンギヤS1→第1プラネタリギヤP1→第1キャリアC1
第3伝達経路:A2ロータ25→磁力線MLによる磁力→ステータ23→第1PDU41→第2PDU42→回転機101→第1リングギヤR1→第1プラネタリギヤP1→第1キャリアC1
これらの第1および第2の伝達経路では、エンジン動力が、電力に変換されることなく、磁気パスや、歯車の噛み合いによる、いわゆる機械パスによって、駆動輪DW,DWに伝達される。
TMOT=-{α・TENG+(1+α)TDDW}/(r1+1+α)……(61)
減速回生中、駆動輪DW,DWのトルク(慣性によるトルク)に対する、エンジン3に伝達される駆動輪DW,DWのトルクの割合が小さいときには、駆動輪DW,DWの動力の一部を用いて両ステータ23,102で発電を行うとともに、発電した電力をバッテリ43に充電する。ステータ102での発電に伴い、第1キャリアC1には、駆動輪DW,DWのトルクの全部と、A1ロータ24に後述するように分配されたトルクとを合成した合成トルクが伝達される。また、第1キャリアC1に伝達された上記の合成トルクは、第1サンギヤS1および第1リングギヤR1に分配され、第1リングギヤR1に分配されたトルクは、ロータ103に伝達される。
停車中ENG始動時、第1回転機21のステータ23に、バッテリ43から電力を供給し、それに伴ってステータ23で発生する第1回転磁界を正転させるとともに、回転機101のステータ102で発電を行い、発電した電力をステータ23にさらに供給する。第1実施形態で述べたように、ステータ23に電力が供給されるのに伴い、ステータ23からの第1駆動用等価トルクTSE1は、A2ロータ25を正転させるように作用するとともに、A1ロータ24を逆転させるように作用する。また、A2ロータ25に伝達されたトルクの一部は、クランク軸3aに伝達され、それにより、クランク軸3aが正転する。
ENGクリープ中には、ステータ23および102で発電を行う。また、このように両ステータ23,102で発電した電力を、バッテリ43に充電する。前述したバッテリ入出力ゼロモードの場合と同様、上記のステータ23での発電に伴って、A2ロータ25にエンジントルクTENGの一部が伝達されるとともに、A2ロータ25に伝達されたエンジントルクTENGが、ステータ23およびA1ロータ24に分配される。また、車速VPがほぼ値0であるのに対し、クランク軸3aが正転しているため、回転機101のロータ103が逆転する。このため、上記のステータ102での発電に伴って発生した回転機トルクTMOTは、上述した停車中ENG始動の場合と同様、第1キャリアC1を正転させるように作用する。また、回転機トルクTMOTに釣り合うように、第1サンギヤS1に伝達されたエンジントルクTENGが、第1キャリアC1にさらに伝達され、第1キャリアC1を正転させるように作用する。さらに、第1キャリアC1には、A1ロータ24に上記のように分配されたエンジントルクTENGが伝達される。
ENG発進時、ENGクリープ中に逆転していたロータ103のロータ回転速度VROを、値0になるように制御し、正転していた第1回転磁界の第1磁界回転速度VMF1を上昇させるとともに、エンジン動力を増大させる。そして、ロータ回転速度VROが値0になった後には、前述したバッテリ入出力ゼロモードによる運転を行う。以上により、車速VPが上昇し、車両が発進する。
EV後退発進時、回転機101のステータ102および第1回転機21のステータ23の双方に、バッテリ43から電力を供給する。その結果、ステータ23で発生する第1回転磁界を正転させ、ステータ102で発生する第2回転磁界を正転させる。EV後退発進中、第1回転機21のステータ23に電力が供給されるのに伴い、ステータ23からの第1駆動用等価トルクは、A2ロータ25を正転させるように作用するとともに、A1ロータ24を逆転させるように作用する。また、回転機101のステータ102に電力が供給されるのに伴い、ステータ102からの第2駆動用等価トルクTSE2は、第1遊星歯車装置PS1の第1キャリアC1を逆転させるように作用するとともに、第1遊星歯車装置PS1の第1サンギヤS1を正転させるように作用する。以上により、車速VPが負の方向に上昇し、車両が後退発進する。
ENG後退発進時、ENGクリープ中に逆転していた第2回転磁界の第2磁界回転速度VMF2がさらに負の方向に上昇するよう制御し、かつ、正転していた第1回転磁界の第1磁界回転速度VMF1を上昇させるとともに、エンジン動力を増大させる。以上により、車速VPが負の方向に上昇し、車両が後退発進する。
次に、図73~図77を参照しながら、第8~第12の実施形態による動力装置1G,1H,1I,1J,1Kについて説明する。これらの動力装置1G~1Kはそれぞれ、第7実施形態と比較して、変速装置111,121,131,141,151をさらに備える点が主に異なっており、第8~第12の実施形態のいずれにおいても、エンジン3、第1回転機21、第1遊星歯車装置PS1、回転機101、および駆動輪DW,DWの間の連結関係は、第7実施形態と同様である。すなわち、A2ロータ25および第1サンギヤS1がエンジン3のクランク軸3aに機械的に連結されるとともに、A1ロータ24および第1キャリアC1が駆動輪DW,DWに機械的に連結されている。また、回転機101のロータ103が、第1リングギヤR1に機械的に連結されている。さらに、図73~図77において、第7実施形態と同じ構成要素については、同じ符号を用いて示している。このことは、後述する他の実施形態を説明するための図においても同様に当てはまる。以下、第8実施形態の動力装置1Gから順に、第7実施形態と異なる点を中心に説明する。
図73に示すように、この動力装置1Gでは、変速装置111は、前述した互いに噛み合うギヤ7bおよび第1ギヤ8bに代えて設けられている。この変速装置111は、ベルト式の無段変速装置であり、前述した第2回転軸7に連結された入力軸と、アイドラ軸8に連結された出力軸と、入力軸および出力軸にそれぞれ設けられたプーリと、これらのプーリに巻きかけられた金属ベルト(いずれも図示せず)を有している。変速装置111は、これらのプーリの有効径を変更することによって、入力軸に入力された動力を変速した状態で出力軸に出力する。また、変速装置111の変速比(入力軸の回転数/出力軸の回転数)はECU2によって制御される。
図74に示す第9実施形態の動力装置1Hでは、変速装置121は、遊星歯車装置などで構成されたギヤ式の有段変速装置であり、入力軸122および出力軸(図示せず)を有しており、変速段として、第1速(変速比=入力軸122の回転数/出力軸の回転数=1.0)と第2速(変速比<1.0)から成る計2つの変速段が設定されている。これらの変速段の変更はECU2によって行われる。また、変速装置121の入力軸122は、フライホイール5を介してクランク軸3aに直結されるとともに、変速装置121の出力軸(図示せず)は、前述した第1回転軸4に直結されている。このように、変速装置121は、クランク軸3aと、A2ロータ25および第1サンギヤS1との間に設けられており、エンジン動力を変速して、A2ロータ25および第1サンギヤS1に伝達する。
図75に示す第10実施形態の動力装置1Iでは、変速装置131は、ギヤ式の有段変速装置であり、入力軸132および出力軸(図示せず)と、ギヤ比が互いに異なる複数のギヤ列と、これらの複数のギヤ列と入力軸132および出力軸との間をギヤ列ごとに接続・遮断するクラッチ(いずれも図示せず)を有している。変速装置131は、入力軸132に入力された動力を、これらの複数のギヤ列の1つによって変速した状態で、出力軸に出力する。また、変速装置131では、これらの複数のギヤ列によって、前進用の第1速(変速比=入力軸132の回転数/出力軸の回転数>1.0)、第2速(変速比=1.0)および第3速(変速比<1.0)と、後進用の1つの変速段から成る計4つの変速段が設定され、その変更はECU2によって制御される。
次に、図78を参照しながら、第13実施形態による動力装置1Lについて説明する。この動力装置1Lは、第7実施形態と比較して、ロータ回転速度VROおよび車速VPの速度差と車速VPおよびエンジン回転数NEの速度差との比を変更する変速装置をさらに備える点が主に異なっている。以下、第7実施形態と異なる点を中心に説明する。
る。この場合、第1変速モードを用いたときには、回転機101に要求されるトルク、すなわち回転機トルクTMOTは、前記式(61)で表される。一方、第2変速モードを用いたときには、回転機トルクTMOTは、次式(62)で表される。
TMOT=-{α・TENG+(1+α)TDDW}
/(r1・r2+r1+1+α) ……(62)
これらの式(61)と式(62)の比較から明らかなように、回転機トルクTMOTは、同じ大きさの駆動輪伝達トルクTDDWおよびエンジントルクTENGに対して、第2変速モードの方が小さい。このため、ENG走行中の急加速運転時には、第2変速モードが用いられる。
TM2=-{THE+[(1/α)+1]TOUT}/[Y+(1/α)+1]
……(63)
TM2=-{THE+[(1/α)+1]TOUT}/[Z+Y+(1/α)+1]
……(64)
次に、図86を参照しながら、第14実施形態による動力装置1Mについて説明する。この動力装置1Mは、第7実施形態の動力装置1Fに第6実施形態で述べたブレーキ機構BLを加えたものである。以下、第7実施形態と異なる点を中心に説明する。
TMOT=-{α・TENG+(1+α)TDDW}/(r1’+1+α)
……(65)
EVクリープ中には、第1実施形態と同様、第2回転機31のステータ33に、バッテリ43から電力を供給するとともに、第2回転磁界を正転させる。また、回転機101のロータ103に後述するように伝達される動力を用いて、ステータ102で発電を行うとともに、発電した電力をステータ23に供給する。これに伴い、第1実施形態で述べたように、ステータ33からの第2駆動用等価トルクTSE2は、B2ロータ35を正転させるように作用するとともに、B1ロータ34を逆転させるように作用する。また、B2ロータ35に伝達されたトルクの一部は、第2回転軸7などを介して駆動輪DW,DWに伝達され、それにより、駆動輪DW,DWが正転する。
EV発進時には、第2回転機31のステータ33に供給される電力および回転機101のステータ102で発電する電力をいずれも増大させる。さらに、式(44)および(53)に示すような回転速度の関係を維持し、エンジン回転数NEを値0に保持しながら、EVクリープ中に逆転していたロータ103のロータ回転速度VROと、正転していた第2回転磁界の第2磁界回転速度VMF2をそれぞれ、それまでと同じ回転方向に上昇させる。以上により、車速VPが上昇し、車両が発進する。
EV走行中ENG始動時には、車速VPをそのときの値に保持しながら、EV発進時に上述したように逆転していたロータ103のロータ回転速度VROを、値0になるように制御するとともに、正転していた第2回転磁界の第2磁界回転速度VMF2を、低下させるように制御する。そして、ロータ回転速度VROが値0になった後には、第2回転機31のステータ33に加え、回転機101のステータ102にも、バッテリ43から電力を供給し、ロータ103を正転させるとともに、ロータ回転速度VROを上昇させる。
TMOT=-{β・TDDW+(1+β)TDENG}/(r1+1+β)
……(66)
この式(66)から明らかなように、第1遊星ギヤ比r1が大きいほど、同じ大きさの駆動輪伝達トルクTDDWおよびエンジン伝達トルクTDENGに対して、回転機トルクTMOTが小さくなる。前述したように第1遊星ギヤ比r1が一般的な遊星歯車装置が取りうる値のなかで比較的大きな値に設定されているので、回転機101の小型化およびコストの削減を図ることができる。
ENG走行中には、第1実施形態で述べた実行条件に応じて、バッテリ入出力ゼロモードや、アシストモード、駆動時充電モードによる運転が行われる。このバッテリ入出力ゼロモード中、ロータ103に伝達されるエンジン動力を用いて、回転機101のステータ102で発電を行うとともに、発電した電力を、バッテリ43に充電せずに、第2回転機31のステータ33に供給する。この場合、このステータ102での発電によって、エンジントルクTENGの一部が、第1キャリアC1、第1プラネタリギヤP1および第1リングギヤR1を介して、ロータ103に伝達されるのに伴い、第1サンギヤS1にも、第1キャリアC1および第1プラネタリギヤP1を介して、エンジントルクTENGの一部が伝達される。すなわち、第1サンギヤS1および第1リングギヤR1に、エンジントルクTENGの一部が分配される。
第1伝達経路:第1キャリアC1→第1プラネタリギヤP1→第1サンギヤS1→連結軸6→B2ロータ35
第2伝達経路:B1ロータ34→磁力線による磁力→B2ロータ35
第3伝達経路:第1キャリアC1→第1プラネタリギヤP1→第1リングギヤR1→ロータ103→ステータ102→第1PDU41→第2PDU42→ステータ33→磁力線による磁力→B2ロータ35
これらの第1および第2の伝達経路では、エンジン動力が、電力に変換されることなく、磁気パスや機械パスによって、駆動輪DW,DWに伝達される。また、第3伝達経路では、エンジン動力が、電気パスによって駆動輪DW,DWに伝達される。
TGE2=-{r1・TENG+(1+r1)TDDW}/(β+1+r1) ……(67)
減速回生中、駆動輪DW,DWのトルク(慣性によるトルク)に対する、エンジン3に伝達される駆動輪DW,DWのトルクの割合が小さいときには、駆動輪DW,DWの動力の一部を用いて両ステータ102,33で発電を行うとともに、発電した電力をバッテリ43に充電する。ステータ33での発電に伴い、B2ロータ35には、駆動輪DW,DWのトルクの全部と、第1サンギヤS1に後述するように分配されたトルクとを合成した合成トルクが伝達される。また、B2ロータ35に伝達された上記の合成トルクは、ステータ33およびB1ロータ34に分配される。
停車中ENG始動時、回転機101のステータ102に、バッテリ43から電力を供給し、ロータ103を正転させるとともに、第2回転機31のステータ33で発電を行い、発電した電力をステータ102にさらに供給する。ステータ102への電力の供給に伴って第1リングギヤR1に伝達された回転機トルクTMOTは、第1プラネタリギヤP1を介して、第1キャリアC1および第1サンギヤS1に伝達され、第1キャリアC1を正転させるように作用するとともに、第1サンギヤS1を逆転させるように作用する。また、第1キャリアC1に伝達されたトルクの一部は、クランク軸3aに伝達され、それにより、クランク軸3aが正転する。
ENGクリープ中には、ステータ102および33で発電を行う。また、このように両ステータ102,33で発電した電力を、バッテリ43に充電する。前述したバッテリ入出力ゼロモードの場合と同様、上記のステータ102での発電に伴って、第1キャリアC1にエンジントルクTENGの一部が伝達されるとともに、第1キャリアC1に伝達されたエンジントルクTENGが、ステータ102および第1サンギヤS1に分配される。また、第1実施形態と同様、上述したステータ33での発電に伴って発生する第2回転磁界が逆転する。このため、上記のステータ33での発電に伴って発生した第2発電用等価トルクTGE2は、B2ロータ35を正転させるように作用する。また、第2発電用等価トルクTGE2に釣り合うように、B1ロータ34に伝達されたエンジントルクTENGが、B2ロータ35にさらに伝達され、B2ロータ35を正転させるように作用する。さらに、B2ロータ35には、第1サンギヤS1に上記のように分配されたエンジントルクTENGが伝達される。
ENG発進時、ENGクリープ中に逆転していた第2回転磁界の第2磁界回転速度VMF2を、値0になるように制御し、正転していたロータ103のロータ回転速度VROを上昇させるとともに、エンジン動力を増大させる。そして、第2磁界回転速度VMF2が値0になった後には、前述したバッテリ入出力ゼロモードによる運転を行う。以上により、車速VPが上昇し、車両が発進する。
次に、図91~図94を参照しながら、第16~第19の実施形態による動力装置1O,1P,1Q,1Rについて説明する。これらの動力装置1O~1Rはそれぞれ、第15実施形態と比較して、変速装置161,171,181,191をさらに備える点が主に異なっており、第16~第19の実施形態のいずれにおいても、エンジン3、回転機101、第1遊星歯車装置PS1、第2回転機31および駆動輪DW,DWの間の連結関係は、第15実施形態と同様である。すなわち、第1キャリアC1およびB1ロータ34がエンジン3のクランク軸3aに機械的に連結されるとともに、第1サンギヤS1およびB2ロータ35が駆動輪DW,DWに機械的に連結されている。また、回転機101のロータ103が、第1リングギヤR1に機械的に連結されている。さらに、図91~図94において、第15実施形態と同じ構成要素については、同じ符号を用いて示している。このことは、後述する他の実施形態を説明するための図においても同様に当てはまる。以下、第16実施形態の動力装置1Oから順に、第15実施形態と異なる点を中心に説明する。
図91に示すように、この動力装置1Oでは、変速装置161は、前述した互いに噛み合うギヤ7bおよび第1ギヤ8bに代えて設けられている。この変速装置161は、第8実施形態の変速装置111と同様、ベルト式の無段変速装置であり、前述した第2回転軸7に連結された入力軸と、アイドラ軸8に連結された出力軸と、入力軸および出力軸にそれぞれ設けられたプーリと、これらのプーリに巻きかけられた金属ベルト(いずれも図示せず)を有している。変速装置161は、これらのプーリの有効径を変更することによって、入力軸に入力された動力を変速した状態で出力軸に出力する。また、変速装置161の変速比(入力軸の回転数/出力軸の回転数)はECU2によって制御される。
図92に示す第17実施形態の動力装置1Pでは、変速装置171は、前述した第9実施形態の変速装置121と同様、遊星歯車装置などで構成されたギヤ式の有段変速装置であり、入力軸172および出力軸(図示せず)を有しており、変速段として、第1速(変速比=入力軸172の回転数/出力軸の回転数=1.0)と第2速(変速比<1.0)から成る計2つの変速段が設定されている。これらの変速段の変更はECU2によって行われる。また、変速装置171の入力軸172はフライホイール5を介してクランク軸3aに直結されるとともに、その出力軸(図示せず)が第1回転軸4に直結されている。このように、変速装置171は、クランク軸3aと、第1キャリアC1およびB1ロータ34との間に設けられており、エンジン動力を変速して、第1キャリアC1およびB1ロータ34に伝達する。
図93に示す第18実施形態の動力装置1Qでは、第15実施形態と異なり、第2回転軸7は設けられておらず、第1ギヤ8bは、連結軸6に一体に設けられたギヤ6bに噛み合っている。これにより、第1サンギヤS1およびB2ロータ35は、連結軸6や、ギヤ6b、第1ギヤ8b、アイドラ軸8、第2ギヤ8c、ギヤ9a、差動ギヤ機構9などを介して、変速装置181を介さずに、駆動輪DW,DWに機械的に連結されている。
図94に示す第19実施形態の動力装置1Rでは、第18実施形態と同様、第2回転軸7は設けられておらず、第1ギヤ8bは、連結軸6に一体に設けられたギヤ6bに噛み合っている。また、変速装置191は、第7実施形態の変速装置131と同様に構成された、第1速~第3速の変速段を有するギヤ式の有段変速装置であり、第1サンギヤS1に直結された入力軸192と、連結軸6に直結された出力軸(図示せず)を有しており、入力軸192に入力された動力を変速し、出力軸に出力する。さらに、変速装置191の変速段の変更は、ECU2によって制御される。
次に、図95を参照しながら、第20実施形態による動力装置1Sについて説明する。この動力装置1Sは、第15実施形態と比較して、ロータ回転速度VROおよび車速VPの速度差と車速VPおよびエンジン回転数NEの速度差との比を変更する変速装置をさらに備える点が主に異なっている。以下、第15実施形態と異なる点を中心に説明する。
TMOT=-{β・TDDW+(1+β)TDENG}
/(r1・r2+r1+1+β) ……(68)
これらの式(66)と式(68)の比較から明らかなように、回転機トルクTMOTは、同じ大きさの駆動輪伝達トルクTDDWおよびエンジン伝達トルクTDENGに対して、第2変速モードの方が小さい。このため、EV走行中ENG始動時には、第2変速モードが用いられる。
TM2=-{TOUT+[(1/α)+1]TDHE}/[Y+(1/α)+1]……(69)
TM2=-{TOUT+[(1/α)+1]TDHE}/[Z+Y+(1/α)+1]……(70)
次に、図103を参照しながら、第22実施形態による動力装置1Uについて説明する。同図に示すように、この動力装置1Uは、第15実施形態の動力装置1Nに、第6実施形態で述べたブレーキ機構BLを加えたものである。以下、第15実施形態と異なる点を中心に説明する。
ある。これに対し、第1遊星ギヤ比r1をより小さな値に設定することによって、図89に破線で示す速度共線図と二点差線で示す速度共線図との比較から明らかなように、ロータ回転速度VROを小さくすることができ、したがって、ロータ回転速度VROの過大化による損失の発生により駆動効率が低下するのを、防止することができる。
TMOT=-{β・TDDW+(1+β)TDENG}/(r1’+1+β)……(71)
以下、図面を参照しながら、本発明に係る1共線3要素の仕組みを有する動力装置について説明する。なお、以下の説明では、図104~図106の左側および右側をそれぞれ「左」および「右」という。
図104および図105に示すように、第23実施形態の動力装置1は、ハイブリッド車両(以下「車両」という)2の左右の前輪4,4を駆動するものであり、動力源として、エンジン3、第1回転機10および第2回転機20を備えている。
まず、第1回転機10について説明する。図106に示すように、第1回転機10は、前述した駆動系ハウジングに固定されたケース11と、左端部がエンジン3のクランクシャフトに直結された入力軸12と、この入力軸12と同心の出力軸13(回転軸)と、ケース11内に収容され、出力軸13と一体に回転する第1ロータ14と、ケース11内に収容され、入力軸12と一体に回転する第2ロータ15と、ケース11の周壁11cの内周面に固定されたステータ16などを備えている。これらの第1ロータ14、第2ロータ15およびステータ16は、径方向の内側から外側に向かって、互いに同心に配置されている。
(f1)ステータがU相、V相およびW相の3相コイルを有すること。
(f2)ステータ磁極が2個すなわちステータ磁極の極対数が値1であり、磁極が4個すなわち磁極の極対数が値2であるとともに、軟磁性体が第1~第3軟磁性体の計3個であること。
次に、第2回転機20について説明する。この第2回転機20は、DCブラシレスモータで構成されており、図106に示すように、前述した駆動系ハウジングに固定されたケース21と、ケース21内に収容され、出力軸13に同心に固定されたロータ22と、ケース21の周壁21cの内周面に固定されたステータ23などを備えている。
一方、動力装置1は、図105に示すように、エンジン3を主に制御するためのENG・ECU29と、第1回転機10および第2回転機20を主に制御するためのMOT・ECU30などを備えている。これらのECU29,30はいずれも、RAM、ROM、CPUおよびI/Oインターフェースなどからなるマイクロコンピュータ(いずれも図示せず)で構成されている。
以下、上記説明した1共線3要素の仕組みを有する動力装置1においてENG・ECU29およびMOT・ECU30が行う駆動力制御について、図118及び図119を参照して説明する。図118は、第23実施形態の動力装置1における駆動力制御を示すブロック線図である。また、図119は、1共線3要素の仕組みを有する動力装置1における速度共線図である。
T11=α/(1+α)×T12 …(113)
・エンジン停止中で停車中
まず、停車中のエンジン始動制御について説明する。この制御では、MOT・ECU30は、エンジン停止中で停車中の場合において、所定のエンジン始動条件が成立したとき(例えば、図示しないイグニッション・スイッチがOFF状態からON状態に切り換わったとき)に、バッテリ33の電力を、VCU34および1ST・PDU31を介して第1回転機10に供給し、回転磁界をステータ16に発生させる。この場合、第1回転機10では、第1ロータ14が前輪4に機械的に連結され、第2ロータ15がエンジン3のクランクシャフトに機械的に連結されているので、停車中でエンジン停止状態の場合、第1ロータ14の方が第2ロータ15よりも回転抵抗が極めて大きい状態となり、それに起因して、第1ロータ14が停止したままで、第2ロータ15が回転磁界の回転方向に駆動されることになる。その結果、回転磁界の回転に伴って、第2ロータ15が駆動され、それにより、エンジン3を始動することができる。
また、エンジン運転中で停車中の場合において、所定の発進条件が成立したとき(例えば、図示しないブレーキペダルが操作されておらず、アクセル開度APが所定値以上のとき)には、発進制御が実行される。まず、停車中は、出力軸13すなわち第1ロータ14が回転停止状態となっているので、エンジン3が発生する動力はすべて、磁力線を介して、第1回転機10のステータ16に伝達され、これに回転磁界を発生させることで、誘導起電力(すなわち逆起電圧)が発生する。MOT・ECU30は、ステータ16への供給電流を制御することにより、ステータ16で発生した誘導起電力を回生し、その回生電力をすべて、1ST・PDU31および2ND・PDU32を介して第2回転機20に供給する。その結果、第2回転機20のロータ22によって、出力軸13が駆動され、前輪4,4が駆動されることで、車両2が発進する。車両2の発進後、MOT・ECU30は、車速の上昇に伴い、第1回転機10における回生電力が漸減するように制御すると同時に、その回生電力を第2回転機20に供給するように制御する。
さらに、エンジン運転中で走行中のときには、変速制御が実行される。この変速制御では、エンジン3の運転状態(例えば、エンジン回転数NEおよびアクセル開度APなど)および/または車両2の走行状態(例えば車速VPなど)に応じて、エンジン3の動力のうちの、第1ロータ14を介して前輪4に伝達される動力と、第1回転機10で電力として回生される動力との割合を変更するように、第1回転機10が制御されるとともに、この回生電力を第2回転機20に供給することにより、第2回転機20が制御される。この場合、前述したように、第1回転機10は、遊星歯車装置と同様の動作特性で運転可能なものであるので、上記のように第1回転機10を制御するとともに、第1回転機10での回生電力を第2回転機20に供給することによって、第2回転機20を制御すると、電気的な損失を無視すれば、第1回転機10および第2回転機20を介して、エンジン3の動力をすべて前輪4に伝達しながら、第2ロータ15の回転数と出力軸13の回転数との比、言い換えればエンジン回転数NEと駆動軸回転数NDとの比を任意に変更することができる。すなわち、2つの回転機10,20を制御することで、自動変速装置としての機能を実現することができる。
また、エンジン運転中で所定のアシスト条件が成立したとき(例えば、坂道発進のとき、登坂走行中であるとき、または加速走行中であるとき)には、アシスト制御が実行される。具体的には、バッテリ33内の電力を第1回転機10および/または第2回転機20に供給することによって、第1回転機10および/または第2回転機20の動力と、エンジン3の動力とが前輪4に伝達されるように、第1回転機10および/または第2回転機20が制御される。それにより、エンジン3に加えて、第1回転機10および/または第2回転機20を動力源として、アシスト走行またはアシスト発進することができる。
さらに、エンジン3が停止中でかつ車両2が停止中の場合において、所定の回転機発進条件が成立したとき(例えば、バッテリ33の充電残量SOCが所定値SOC_REFを上回っており、ブレーキペダルが操作されていない状態で、アクセル開度APが所定値以上のとき)には、回転機発進制御が実行される。具体的には、エンジン3を停止したままで、バッテリ33の電力が第1回転機10および第2回転機20に同時に供給され、2つの回転機10,20が同時に駆動される。その際、第2回転機20が回転し始めるのと同時に、出力軸13が回転し始めるが、第1回転機10において、停止しているエンジン3に連結された第2ロータ15側の回転抵抗が第1ロータ14側よりもかなり大きくなる。その結果、ステータ16に回転磁界を発生させることにより、第1ロータ14を駆動することができ、第1回転機10および第2回転機20の動力によって、車両2を発進させることができる。なお、エンジン3の回転抵抗が不足する場合には、エンジン3をロックするか、回転抵抗を増大させる装置を設けてもよい。
上記説明したように、本実施形態の動力装置1の動作モードに応じて、バッテリ33から第1回転機10および/または第2回転機20に電力が供給され、また、第1回転機10および/または第2回転機20で発電された電力がバッテリ33に充電される。また、上記説明したように、ENG・ECU29およびMOT・ECU30は、図示しない電流電圧センサからの検出信号に基づいてバッテリ33の充電状態を算出する。
動作装置1の動作モードが「エンジン運転中」のとき、第1回転機10のステータ16では回生発電が行われる。このとき発生した回生エネルギはバッテリ33に送られ充電される。しかし、バッテリSOCが上限SOCに近い状態でバッテリ33が充電されると、バッテリSOCが上限SOCを超えてしまうおそれがある。したがって、ENG・ECU29およびMOT・ECU30は、バッテリSOCが図127に示した上限SOCよりも低い第1しきい値以上のとき、以下説明する制御を行う。
動作装置1の動作モードが「EV走行」のとき、第2回転機20のステータ23は力行運転状態である。したがって、動作装置1の動作モードが「EV走行」のとき、バッテリ33は放電する。しかし、バッテリSOCが下限SOCに近い状態でバッテリ33が放電されると、バッテリSOCが下限SOCを下回るおそれがある。したがって、ENG・ECU29は、バッテリSOCが図127に示した下限SOCよりも高い第2しきい値以下のとき、以下説明する制御を行う。
動作装置1の動作モードが「ENG後退発進」のとき、第1回転機10のステータ16では回生発電が行われる。このとき発生した回生エネルギはバッテリ33に送られ充電される。しかし、バッテリSOCが上限SOCに近い状態でバッテリ33が充電されると、バッテリSOCが上限SOCを越えてしまうおそれがある。したがって、ENG・ECU29およびMOT・ECU30は、バッテリSOCが図127に示した上限SOCよりも低い第1しきい値以下のとき、以下説明する制御を行う。
次に、図131を参照しながら、第24実施形態に係る動力装置1Aについて説明する。同図に示すように、この動力装置1Aは、第23実施形態の動力装置1と比べると、第2回転機20を後輪駆動用の動力源として用いた点が異なっており、それ以外は第23実施形態の動力装置1とほぼ同様に構成されているので、以下、第23実施形態の動力装置1と異なる点を中心に説明するとともに、同じ構成に関しては同一の符号を付し、その説明を省略する。
次に、図133を参照しながら、第25実施形態に係る動力装置1Bについて説明する。同図に示すように、この動力装置1Bは、第23実施形態の動力装置1と比べると、第2回転機20および2ND・PDU32などを省略するとともに、電磁ブレーキ55を付加した点が異なっており、それ以外は第23実施形態の動力装置1とほぼ同様に構成されているので、以下、第23実施形態の動力装置1と異なる点を中心に説明するとともに、同じ構成に関しては同一の符号を付し、その説明を省略する。
次に、図134を参照しながら、第26実施形態に係る動力装置1Cについて説明する。同図に示すように、この動力装置1Cは、第23実施形態の動力装置1と比べると、第1回転機10および第2回転機20の配置が異なっており、それ以外は第23実施形態の動力装置1とほぼ同様に構成されているので、以下、第23実施形態の動力装置1と異なる点を中心に説明するとともに、同じ構成に関しては同一の符号を付し、その説明を省略する。
・エンジン停止中で停車中
まず、停車中のエンジン始動制御について説明する。この制御では、エンジン停止中で停車中の場合において、前述した所定の始動条件が成立したときには、前述したバッテリ33の電力が第1回転機10および/または第2回転機20に供給され、第1回転機10および/または第2回転機20の動力が入力軸12を介してエンジン3に伝達されるように、第1回転機10および/または第2回転機20が力行制御される。それにより、第1回転機10および/または第2回転機20の動力によって、エンジン3を始動することができる。
また、エンジン運転中で停車中の場合において、前述した所定の発進条件が成立したときには、発進制御が実行される。具体的には、停車中、エンジン3の動力は、入力軸12に伝達され、第1回転機10の第1ロータ14が駆動される。その状態で、第1回転機10を制御することにより、第1回転機10で電力回生を実行するとともに、その回生電力を第2回転機20に供給すると、第2回転機20のロータ22によって、第1ロータ14が駆動され、エネルギ循環が発生する。この状態で、第1回転機10での回生電力を減少側に制御すると、第1回転機10の第2ロータ15が回転し、出力軸13が駆動され、前輪4,4が駆動されることで、車両2が発進する。車両2の発進以降、第1回転機10での回生電力をさらに減少側に制御するとともに、第1回転機10のステータ16の磁界回転方向が逆転から正転に移行した後は、第2回転機20を回生制御しかつ第1回転機10を力行制御することにより、車速が上昇する。
さらに、エンジン運転中で走行中のときには、変速制御が実行される。この変速制御では、エンジン3の運転状態(エンジン回転数NEおよびアクセル開度APなど)および/または車両2の走行状態(車速VPなど)に応じて、エンジン3の動力のうちの、入力軸12を介して第1ロータ14に伝達される動力と、第2回転機20で電力として回生される動力との割合を変更するように、第2回転機20が制御されるとともに、この回生電力を第1回転機10に供給することにより、第1回転機10が制御される。この場合、前述したように、第1回転機10が、遊星歯車装置と同様の動作特性を示すように運転可能であるので、上記のように第2回転機20を制御するとともに、第2回転機20での回生電力を第1回転機10に供給することによって、第1回転機10を制御すると、電気的な損失を無視すれば、第1回転機10および第2回転機20を介して、エンジン3の動力をすべて前輪4に伝達しながら、入力軸12の回転数と出力軸13の回転数との比、言い換えればエンジン回転数NEと駆動軸回転数NDとの比を任意に変更することができる。すなわち、2つの回転機10,20を制御することで、自動変速装置としての機能を実現することができる。
また、エンジン運転中で前述した所定のアシスト条件が成立したときには、アシスト制御が実行される。具体的には、バッテリ33内の電力を第1回転機10および/または第2回転機20に供給することによって、第1回転機10および/または第2回転機20の動力と、エンジン3の動力とが前輪4に伝達されるように、第1回転機10および/または第2回転機20が制御される。それにより、エンジン3に加えて、第1回転機10および/または第2回転機20を動力源として、アシスト走行またはアシスト発進することができる。
さらに、エンジン停止中でかつ停車中の場合において、前述した所定の回転機発進条件が成立したときには、回転機発進制御が実行される。具体的には、エンジン3を停止したままで、バッテリ33の電力をVCU34および2ND・PDU32を介して第2回転機20に供給し、第2回転機20(制止装置)を、ロータ22が回転停止状態に保持されるように制御することで、第1ロータ14の回転を制止するとともに、バッテリ33の電力をVCU34および1ST・PDU31を介して第1回転機10に供給し、第1回転機10の力行制御を実行する。その結果、第1回転機10の電力が磁気を介して出力軸13側に動力として伝達され、それにより、車両2を発進させることができる。
・エンジン運転中で停車中
まず、エンジン運転中で停車中の場合において、前述した所定の発進条件が成立したときには、発進制御が実行される。この発進制御では、上記所定の発進条件が成立すると、まず、第1回転機10において、エンジン3の動力を電力として回生し、電力回生の開始後、その回生電力が減少するように、第1回転機10が制御される。それにより、エンジンストールを回避しながら、エンジン3の動力によって、車両2を発進させることができる。
さらに、エンジン運転中で走行中には、エンジン動力の分配制御が実行される。この分配制御では、エンジン3の運転状態(エンジン回転数NEおよびアクセル開度APなど)および/または車両2の走行状態(車速VPなど)に応じて、エンジン3の動力のうちの、第2ロータ15を介して前輪4に伝達される動力と、第1回転機10で電力として回生される動力との割合を変更するように、第1回転機10が制御される。それにより、エンジン3の運転状態および/または車両2の走行状態に応じて、回生電力を適切に制御しながら、車両2を走行させることができる。
また、エンジン運転中で走行中の場合において、前述した所定のアシスト条件が成立したときには、アシスト制御が実行される。具体的には、バッテリ33内の電力が第1回転機10に供給され、エンジン3および第1回転機10の動力によって前輪4を駆動するように、第1回転機10が制御される。それにより、エンジン3に加えて、第1回転機10を動力源として、アシスト走行することができる。以上のように、第1回転機10のみを制御することによって、車両2を運転することができる。
次に、図140を参照しながら、第27実施形態に係る動力装置1Dについて説明する。この動力装置1Dは、上記第26実施形態の動力装置1Cにおける第2回転機20の位置を、前述した第24実施形態の動力装置1Aと同様に、エンジン3と第1回転機10の間の位置から後輪5側に変更するとともに、この第2回転機20によって後輪5を駆動するように構成したものである。この動力装置1Dによれば、前述した第24実施形態の動力装置1Aと同様に、車両2の発進時、全輪駆動状態で発進することができ、それにより、雪道などの低μ路での発進性を向上させることができる。また、走行中も、全輪駆動状態で走行可能となるので、低μ路での走行安定性を向上させることができる。
1A 動力装置
1B 動力装置
1C 動力装置
1D 動力装置
1E 動力装置
1F 動力装置
1G 動力装置
1H 動力装置
1I 動力装置
1J 動力装置
1K 動力装置
1L 動力装置
1M 動力装置
1N 動力装置
1O 動力装置
1P 動力装置
1Q 動力装置
1R 動力装置
1S 動力装置
1T 動力装置
1U 動力装置
DW 駆動輪(被駆動部)
2 ECU(第1制御器、第2制御器)
3a クランク軸(出力部、第1出力部)
3 エンジン(熱機関)
21 第1回転機 23 ステータ(第1ステータ)
23a 鉄芯(第1ステータ、ステータ)
23c U相コイル(第1ステータ、ステータ)
23d V相コイル(第1ステータ、ステータ)
23e W相コイル(第1ステータ、ステータ)
24 A1ロータ(第1ロータ)
24a 永久磁石(第1磁極、磁極)
25 A2ロータ(第2ロータ)
25a コア(第1軟磁性体、軟磁性体)
31 第2回転機(第1回転機)
33 ステータ(第2ステータ)
33a 鉄芯(第2ステータ、ステータ)
33b U相コイル(第2ステータ、ステータ)
33b V相コイル(第2ステータ、ステータ)
33b W相コイル(第2ステータ、ステータ)
34 B1ロータ(第3ロータ、第1ロータ)
34a 永久磁石(第2磁極、磁極)
35 B2ロータ(第4ロータ、第2ロータ)
35a コア(第2軟磁性体、軟磁性体)
41 第1PDU(第1制御器、第2制御器)
42 第2PDU(第2制御器、第1制御器)
43 バッテリ(蓄電装置)
61 変速装置
71 変速装置
81 変速装置
91 変速装置
101 回転機(第2回転機)
103 ロータ(第2出力部)
111 変速装置
121 変速装置
131 変速装置
141 変速装置
151 変速装置
161 変速装置
171 変速装置
181 変速装置
191 変速装置
201 変速装置
PS1 第1遊星歯車装置(差動装置)
S1 第1サンギヤ(第1要素、第3要素)
R1 第1リングギヤ(第3要素、第1要素)
C1 第1キャリア(第2要素)
BL ブレーキ機構
PS2 第2遊星歯車装置(遊星歯車装置)
S2 第2サンギヤ(サンギヤ)
R2 第2リングギヤ(リングギヤ)
P2 第2プラネタリギヤ(プラネタリギヤ)
C2 第2キャリア(キャリア)
CL1 第1クラッチ
CL2 第2クラッチ
1 動力装置
1A~1D 動力装置
3 エンジン(熱機関)
4 前輪(被駆動部)
5 後輪(第2被駆動部)
10 第1回転機
12 入力軸(回転軸)
13 出力軸(回転軸)
14 第1ロータ
14a 永久磁石(磁極)
15 第2ロータ
15a 軟磁性体コア(軟磁性体)
16 ステータ
16a 鉄芯(ステータ、ステータ列)
16c U相コイル(ステータ、ステータ列)
16d V相コイル(ステータ、ステータ列)
16e W相コイル(ステータ、ステータ列)
20 第2回転機(制止装置)
50~54 変速装置
55 電磁ブレーキ(制止装置)
56 クラッチ
57,58 変速装置
Claims (8)
- 隣り合う2つの磁極が互いに異なる極性を有する磁極列が周方向に設けられた第1ロータと、
前記第1ロータと径方向に対向するよう配置され、前記周方向に並んだ複数の電機子に発生する磁極の変化により前記周方向に移動する回転磁界が発生する電機子列を有する第1ステータと、
前記第1ロータと前記第1ステータの間に配置され、互いに間隔を空けて前記周方向に並んだ複数の軟磁性体を有する第2ロータと、を有し、
前記第1ステータの前記電機子列に発生する磁極の数と、前記第1ロータの前記磁極列の磁極の数と、前記第2ロータの前記軟磁性体の数との比が、1:m:(1+m)/2(但し、m≠1)に設定され、前記第1ロータ及び前記第2ロータの一方が駆動軸に接続された第1回転機と、
出力軸が前記第1ロータ及び前記第2ロータの他方と接続した原動機と、
前記駆動軸との間での動力の入出力と、前記第1回転機との間での電力の授受とが可能に構成された第2回転機と、
前記第1回転機及び前記第2回転機との間で電力を授受可能な蓄電器と、を備えた動力装置によって駆動するハイブリッド車両であって、
前記蓄電器の充電状態を検出する状態検出部と、
前記動力装置の制御を行う制御部と、を備え、
前記制御部は、当該ハイブリッド車両の発進のために前記原動機を駆動する際、前記蓄電器の残容量に基づいて、前記原動機の出力を制御することを特徴とするハイブリッド車両。 - 請求項1に記載のハイブリッド車両であって、
前記制御部は、
前記蓄電器の残容量が下限値から上限値までの範囲内に収まるよう前記動力装置を制御し、
前記蓄電器の残容量が前記上限値よりも低い第1しきい値以上の状態で、当該ハイブリッド車両の前方発進のために前記原動機を駆動する場合は、前記第1回転機の前記第1ステータに発生する前記回転磁界の磁界回転速度を制御して、前記原動機の回転数を低く制限することにより前記原動機の出力を下げることを特徴とするハイブリッド車両。 - 請求項1に記載のハイブリッド車両であって、
前記制御部は、
前記蓄電器の残容量が下限値から上限値までの範囲内に収まるよう前記動力装置を制御し、
前記蓄電器の残容量が前記下限値よりも高い第2しきい値以下の状態で、当該ハイブリッド車両の後方発進のために前記原動機を駆動する場合は、前記第1回転機の前記第1ステータに発生する前記回転磁界の磁界回転速度を制御して、前記原動機の回転数を低く制限することにより前記原動機の出力を下げることを特徴とするハイブリッド車両。 - 請求項2又は3に記載のハイブリッド車両であって、
前記制御部は、前記原動機の出力トルクを維持するよう前記原動機を制御することを特徴とするハイブリッド車両。 - 請求項2又は3に記載のハイブリッド車両であって、
前記制御部は、前記原動機に要求されたトルクに対する前記第1回転機の前記第1ステータに発生する単位時間当たりの回生エネルギが規定値を超える場合、前記原動機の出力トルクを低く制限するよう前記原動機を制御することを特徴とするハイブリッド車両。 - 請求項1に記載のハイブリッド車両であって、
前記制御部は、
前記蓄電器の残容量が下限値から上限値までの範囲内に収まるよう前記動力装置を制御し、
当該ハイブリッド車両が前記第1回転機からの駆動力による走行時に、前記蓄電器の残容量が前記下限値よりも高い第2しきい値以下であれば、前記原動機を駆動して、前記第1回転機の前記第1ステータに発生する前記回転磁界の磁界回転速度が低減するよう制御することを特徴とするハイブリッド車両。 - 請求項1~6のいずれか一項に記載のハイブリッド車両であって、
前記第2回転機は、
回転子及び電機子を有する電動機と、
共線関係を保って動作する第1回転要素、第2回転要素、及び前記回転子に接続された第3回転要素を有し、前記第2回転要素に入力されたエネルギを前記第1回転要素及び前記第3回転要素に分配する機能と、前記第1回転要素及び前記第3回転要素に入力された各エネルギを合成して前記第2回転要素に出力する機能と、を有する回転機構と、を有し、
前記第1ロータ及び前記第2回転要素と、前記第2ロータ及び前記第1回転要素とのうちの一方が前記原動機の前記出力軸に接続され、他方が前記駆動軸に接続されたことを特徴とするハイブリッド車両。 - 請求項1~6のいずれか一項に記載のハイブリッド車両であって、
前記第2回転機は、
隣り合う2つの磁極が互いに異なる極性を有する磁極列が周方向に設けられた第3ロータと、
前記第3ロータと径方向に対向するよう配置され、前記周方向に並んだ複数の電機子に発生する磁極の変化により前記周方向に移動する回転磁界が発生する電機子列を有する第2ステータと、
前記第3ロータと前記第2ステータの間に配置され、互いに間隔を空けて前記周方向に並んだ複数の軟磁性体を有する第4ロータと、を有し、
前記第2ステータの前記電機子列に発生する磁極の数と、前記第3ロータの前記磁極列の磁極の数と、前記第4ロータの前記軟磁性体の数との比が、1:m:(1+m)/2(但し、m≠1)に設定され、
前記駆動軸に前記第1ロータが接続され、前記原動機の前記出力軸に前記第2ロータが接続されている場合、前記第4ロータが前記駆動軸に接続され、前記第3ロータが前記原動機の前記出力軸に接続され、
前記駆動軸に前記第2ロータが接続され、前記原動機の前記出力軸に前記第1ロータが接続されている場合、前記第3ロータが前記駆動軸に接続され、前記第4ロータが前記原動機の前記出力軸に接続されたことを特徴とするハイブリッド車両。
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DE112010004022T DE112010004022T5 (de) | 2009-10-13 | 2010-07-23 | Hybridfahrzeug |
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JP (1) | JP5362840B2 (ja) |
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