WO2005000619A1 - ハイブリッド駆動装置及びこれを搭載した自動車 - Google Patents
ハイブリッド駆動装置及びこれを搭載した自動車 Download PDFInfo
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- WO2005000619A1 WO2005000619A1 PCT/JP2004/009200 JP2004009200W WO2005000619A1 WO 2005000619 A1 WO2005000619 A1 WO 2005000619A1 JP 2004009200 W JP2004009200 W JP 2004009200W WO 2005000619 A1 WO2005000619 A1 WO 2005000619A1
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- WO
- WIPO (PCT)
- Prior art keywords
- electric motor
- planetary gear
- transmission
- hybrid drive
- drive device
- Prior art date
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
- B60K6/36—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings
- B60K6/365—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings with the gears having orbital motion
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
- B60K6/40—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the assembly or relative disposition of components
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
- B60K6/44—Series-parallel type
- B60K6/445—Differential gearing distribution type
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/50—Architecture of the driveline characterised by arrangement or kind of transmission units
- B60K6/54—Transmission for changing ratio
- B60K6/547—Transmission for changing ratio the transmission being a stepped gearing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
- F16H3/727—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously with at least two dynamo electric machines for creating an electric power path inside the gearing, e.g. using generator and motor for a variable power torque path
- F16H3/728—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously with at least two dynamo electric machines for creating an electric power path inside the gearing, e.g. using generator and motor for a variable power torque path with means to change ratio in the mechanical gearing
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K1/00—Arrangement or mounting of electrical propulsion units
- B60K1/02—Arrangement or mounting of electrical propulsion units comprising more than one electric motor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
- F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
- F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
- F16H2037/0866—Power split variators with distributing differentials, with the output of the CVT connected or connectable to the output shaft
- F16H2037/0873—Power split variators with distributing differentials, with the output of the CVT connected or connectable to the output shaft with switching, e.g. to change ranges
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/62—Hybrid vehicles
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S903/00—Hybrid electric vehicles, HEVS
- Y10S903/902—Prime movers comprising electrical and internal combustion motors
- Y10S903/903—Prime movers comprising electrical and internal combustion motors having energy storing means, e.g. battery, capacitor
- Y10S903/904—Component specially adapted for hev
- Y10S903/909—Gearing
- Y10S903/91—Orbital, e.g. planetary gears
- Y10S903/911—Orbital, e.g. planetary gears with two or more gear sets
Definitions
- the present invention relates to a hybrid drive device mounted on a vehicle and a vehicle mounted with the same, and more particularly, to a hybrid drive device including two electric motors, a power distribution planetary gear, and a transmission disposed in a case member. Regarding placement.
- a hybrid drive device an engine, a generator, and an electric motor for driving (assisting) are connected to three elements of a planetary gear, respectively, and the electric motor for driving is connected to an output shaft to control the generator. Control the output tonolek of the planetary gears as described above, and, if necessary, combine with the torque force of another driving electric motor and the output torque of the planetary gears and output them to the output shaft. It is known to mount a hybrid (split type or two motor type) hybrid drive device on an automobile.
- the above-described hybrid drive device is disclosed, for example, in Japanese Patent Application Laid-Open No. 08-183347 for use in a front engine (FF), and further includes a transmission between an electric motor and an output shaft. This is disclosed in Japanese Patent Application Laid-Open No. 2002-225578.
- an internal combustion engine In an FR type automobile, an internal combustion engine, a hybrid drive device, and a propeller chart are arranged on substantially the same axis in order from the front side in the front-rear direction of the vehicle body.
- the hybrid drive device two electric motors (a first electric motor for power generation and a second electric motor for drive), a power distribution mechanism, a transmission, and the like are arranged in a cylindrical case member. It is stored so as to be arranged at different positions on the shaft.
- this hybrid drive device is formed such that the front end side connected to the internal combustion engine is thick and the rear end side that is the propeller shaft side is thin. Is preferred. Furthermore, comparing the above-mentioned two electric motors, the driving electric motor needs to generate a large torque when the vehicle starts moving, and therefore has a larger radial dimension than the electric motor for power generation. There is a tendency. If the radial dimension is to be reduced, the electric motor for driving becomes longer in the front-rear direction in order to secure a high torque at the time of starting. The length in the front-rear direction also becomes longer, and the mountability on the vehicle body becomes worse.
- the present invention arranges the second electric motor on the front side (closer to the internal combustion engine) than the first electric motor, thereby ensuring high torque and improving mountability. Accordingly, it is an object of the present invention to provide a hybrid drive device that solves the above-mentioned problems and an automobile equipped with the same.
- the invention according to claim 1 is the input shaft (10) for inputting power from the internal combustion engine (5), and the input shaft (10) and the input shaft (13) are arranged in a line on the one shaft (13).
- a first electric motor (20) arranged on the one shaft (13) and having a stator (24) and a rotor (25), the output shaft (12) being linked to the driving wheels (3, 3);
- a first rotating element (R0) disposed on the one shaft (13) and connected to the input shaft (10); and a first rotating element (R0) connected to the rotor (25) of the first electric motor (20).
- a transmission device that changes the speed and transmits it to the output shaft (12) (22), and the first electric motor (20), the power distribution planetary gear (21), the second electric motor (23), and the transmission (22)
- the first electric motor (20) and the second electric motor are housed in the material (14), are arranged in a system 1J on the one shaft (13), and are arranged on the case member (14).
- the stators (24, 28) of (23) are fixed so that the second electric motor (23) is located closer to the internal combustion engine (5) than the first electric motor (20).
- the first electric motor (20), the power distribution planetary gear (21), the second electric motor (23), and the transmission (22) are arranged along the one shaft (13).
- a hybrid drive device ( 7A, 7B).
- the invention according to claim 2 is characterized in that the second electric motor (23) is provided in the case member.
- the first electric motor (20), the power distribution planetary gear (21), the second electric motor (23), and the transmission ( 22) The hybrid drive device (7A, 7B) according to claim 1, which is disposed at the forefront end.
- the invention according to claim 3 is the hybrid drive according to claim 2, wherein the transmission (22) is provided adjacent to the second electric motor (23). It is in the equipment (7A, 7B).
- the rotor (29) of the second electric motor (23) is provided on both sides with supporting members (A, B) extended from the case member (14).
- the support member (A, b) is supported via a bearing member (a, b), and the support member (A, B) includes a support member (B) between the second electric motor (23) and the transmission (22).
- At least a part of the hydraulic chamber (45) is provided on an inner diameter side of a stator (coil end) (28) of the second electric motor (23).
- the hybrid drive device (7A, 7B) according to claim 4.
- the invention according to claim 6 is characterized in that, in order from the side closer to the internal combustion engine (5), the second electric motor (23), the transmission (22), and the power distribution planetary gear (21).
- the invention according to claim 7 is characterized in that the input shaft (10) passes through the second electric motor (23) and the inner peripheral side of the transmission (22) to allow the first rotating element ( R0), the output shaft (12) passes through the power distribution planetary gear (21), the inner peripheral side of the first electric motor (20), and the output element (22) of the transmission (22).
- the power distribution planetary gear (21) is constituted by a double pinion planetary gear, and the input shaft (10) is connected to the transmission (22) and the power distribution.
- the output shaft (12) is connected to the ring gear (R0) of the double pinion planetary gear through a space between the planetary gear (21), and the carrier (CR0) of the double pinion planetary gear is passed through the inner peripheral side of the power distribution planetary gear (21). ),
- the rotor (25) of the first electric motor (20) is connected to the sun gear (SO) of the double pinion planetary gear, and the output of the transmission (22) is connected.
- An element (CR1) connected to the first electric motor (20) side of the carrier (CR0) of the double pinion planetary gear through an outer peripheral side of the power distribution planetary gear (21).
- Item 7 The hybrid drive device (7A) described in Item 7.
- the rotor (25) of the first electric motor (20) is provided on both sides with support members (D, E) extended from the case member (14).
- the output shaft (12) is supported via a bearing member (t, u).
- the output shaft (12) is provided with a bearing member (s, V) on an outer peripheral surface thereof, and is provided with a rotor (25) of the first electric motor (20).
- the rotor (29) of the second electric motor (23) is a support member (A, B) having both sides extended from the case member (14).
- the input shaft (10) is provided with a bearing member (c) on an outer peripheral surface thereof, and is provided on an inner peripheral surface of a rotor (29) of the second electric motor (23).
- the invention according to claim 11 is characterized in that, in order from the side closer to the internal combustion engine (5), the second electric motor (23), the transmission (22), and the first electric motor ( 20)
- the invention according to claim 12 is characterized in that the input shaft (10) is connected to the second electric motor (23), the transmission (22), the first electric motor (20), and the power
- the output shaft (12) is connected to the outer peripheral side of the power distribution planetary gear (21) through the inner peripheral side of the distribution planetary gear (21), and is connected to the first rotating element (R0).
- Issue of (22) The hybrid according to claim 11, wherein a force element (CR1) is connected to the output shaft (12) through an inner peripheral side of the first electric motor (20) and the power distribution planetary gear (21). In the drive (7B).
- the power distribution planetary gear (21) is constituted by a double pinion planetary gear, and the input shaft (10) is connected to the rear of the power distribution planetary gear (21). Side, and connected to the ring gear (R0) of the double pinion planetary gear, and the output shaft (12) passes through the outer peripheral side of the power distribution planetary gear (21) to the first pinion planetary gear carrier (CR0). Connected to the electric motor (20),
- the rotor (25) of the first electric motor (20) is connected to the sun gear (SO) of the double pinion planetary gear, and the output element (CR1) of the transmission (22) is connected to the power distribution planetary gear (21).
- the rotor (25) of the first electric motor (20) is a support member (C, D) having both sides extended from the case member (14).
- the output element (CR1) of the transmission (22) is provided with a bearing member (q, r) on its outer peripheral surface, and the first electric motor (20)
- the rotor (29) of the second electric motor (23) has support members (A, B) whose both sides are extended from the case member (14).
- the input shaft (10) is provided with bearing members (c, d, 1) on the outer peripheral surface thereof, and the rotor (29) of the second electric motor (23).
- the hybrid drive unit (7B) according to claim 11, supported on an inner peripheral surface of the transmission device (22) and an inner peripheral surface of the output element (CR1) of the transmission (22).
- the invention according to claim 16 is the support member (B) between the second electric motor (23) and the transmission (22) among the support members (A, B). 12.
- a hydraulic chamber (45) of a hydraulic actuator (43) of the transmission (22) is formed in the transmission.
- the bridge drive (7B) In the bridge drive (7B).
- the transmission (22) includes a planetary gear unit (27), according to any one of claims 1 to 16.
- the transmission (22) has at least four shift elements (Sl, CRl, Rl, S2) and a first shift element (SI).
- the second electric motor (23) is connected to the rotor (29), the second transmission element (CR1) is connected to the output shaft (12), and the third and fourth transmission elements (Rl,
- the invention according to claim 19 is characterized in that the planetary gear unit (27) of the transmission (22) is constituted by a Ravigneaux planetary gear, and the carrier (CR1) of the Ravigneaux planetary gear is connected to the output shaft ( A hybrid drive device (7A, 7B) according to claim 17 connected to 12).
- the invention according to claim 20 provides the internal combustion engine (5), the hybrid drive means, and the rear wheels (3, 3) as drive wheels to which drive power from the hybrid drive means is transmitted.
- the hybrid drive device is the hybrid drive device (7A, 7B) according to any one of claims 1 to 4, wherein the hybrid drive device is a hybrid drive device.
- (7A, 7B) connects the input shaft (10) to the output shaft (12) of the internal combustion engine (5), and connects the propeller shaft (16) to the output shaft (12).
- An automobile (1) wherein the output shaft (6) of the engine, the input shaft (10), the output shaft (12), and the propeller shaft (16) are arranged substantially on the same axis. It is in.
- the second electric motor is provided on the front side of the first electric motor.
- the second electric motor which requires more power than the first electric motor, can be made larger in radial direction (compared to the first electric motor).
- the length in the front-rear direction can be reduced accordingly.
- the overall length of the hybrid drive device can be reduced in the front-rear direction to improve the mountability on the vehicle body.
- the second electric motor includes a first electric motor, a power distribution planetary gear, a second electric motor, and a second electric motor disposed on one axis of the case member.
- both sides of the rotor of the second electric motor are supported by the supporting member extended from the case member via the bearing member, and the second of the supporting members is supported by the second member.
- the second electric motor, the transmission, the planetary gear for power distribution, and the first electric motor are arranged in this order from the side closer to the internal combustion engine. This allows the second electric motor, which is not complicatedly arranged, to be disposed on the front side of the first electric motor.
- the first electric motor is supported on both sides of the rotor of the first electric motor by the supporting member extended from the case member through the bearing member, thereby providing the first electric motor. Since the motor motor can be reliably supported, the gap between the stator and the rotor can be set small, and the output of the first electric motor can be improved. Furthermore, since the output shaft is supported on the inner peripheral surface of the rotor of the first electric motor by the bearing provided on the outer peripheral surface, the rigidity of the output shaft is improved, and the diameter of the output shaft needs to be increased unnecessarily. What? Therefore, the diameter of the entire hybrid drive device can be reduced.
- the second electric motor by supporting both sides of the rotor of the second electric motor to the supporting member extended by the case member through a bearing member, the second electric motor Since the rotor of the motor can be reliably supported, the gap between the stator and the rotor can be set small, and the output of the second electric motor can be improved. This makes it possible to further reduce the length of the second electric motor in the front-rear direction. Further, since the input shaft can be supported on the inner peripheral surface of the rotor of the second electric motor by the bearing member provided on the outer peripheral surface, it is not necessary to increase the diameter of the input shaft unnecessarily. Therefore, it is possible to reduce the diameter S of the hybrid drive device as a whole.
- the second electric motor, the transmission, the planetary gear for power distribution, and the first electric motor are arranged in this order from the side closer to the internal combustion engine. This allows the second electric motor, which is not complicatedly arranged, to be disposed on the front side of the first electric motor.
- the first electric motor is supported on both sides of the rotor of the first electric motor by the support member extended by the case member via the bearing member, thereby providing the first electric motor. Since the rotor can be reliably supported, the gap between the stator and the rotor can be set small, and the output of the first electric motor can be improved. Furthermore, since the output element of the transmission is supported on the inner peripheral surface of the rotor of the first electric motor by the bearing provided on the outer peripheral surface, the support rigidity of the output shaft is improved, and the output shaft is not required to have a large diameter. There is no need to convert. Therefore, it is possible to reduce the diameter of the entire hybrid drive device.
- the second electric motor by supporting both sides of the rotor of the second electric motor to the supporting member extended by the case member via a bearing member, the second electric motor is provided. Since the rotor of the motor can be reliably supported, the gap between the stator and the rotor can be set small, and the output of the second electric motor can be improved. This makes it possible to further reduce the length of the second electric motor in the front-rear direction. Further, even if the input shaft is extended to the power distribution planetary gear provided at the rear end, the input member is provided on the outer peripheral surface by the bearing member provided on the inner peripheral surface of the rotor of the second electric motor and the output element of the transmission.
- the diameter of the entire hybrid drive device can be reduced. [0040] According to the invention of claim 16, by forming the hydraulic chamber of the hydraulic actuator of the transmission in the support member of the support member between the first electric motor and the transmission, Since the case member and the support member for forming the hydraulic chamber of the hydraulic actuator can be shared, the overall length of the hybrid drive device can be reduced in the front-rear direction.
- the transmission since the transmission is constituted by a planetary gear unit, the transmission can be provided on one shaft, so that the diameter of the hybrid drive device can be reduced.
- Power S can.
- the transmission has at least four transmission elements, and connects the first transmission element to the rotor of the second electric motor and outputs the second transmission element. Since it has a brake element that is connected to the shaft and can fix the third and fourth speed change elements to the case respectively, it is possible to reduce the rotational speed of the rotor of the second electric motor in at least two steps by merely providing a brake. it can.
- the hydraulic servo of the clutch is generally provided on the center shaft to supply oil to the hydraulic servo of the clutch, and further, in order to prevent oil leakage between the rotating members. Multiple seal rings are used.
- the seal ring is not required unlike the clutch, and it is not necessary to provide the seal ring on the center shaft. Therefore, by forming the two shift speeds using only the brake, the shaft length of the no- and hybrid drive devices can be shortened, so that the case rigidity is improved and the efficiency can be improved by reducing the number of seal rings.
- the planetary gear unit of the transmission is constituted by a Ravigneaux type planetary gear.
- the Ravigneaux planetary gear can use the same carrier for the two planetary gears, thereby reducing the shaft length of the transmission.
- the use of the same carrier for the two planetary gears increases the size of the carrier.
- the carrier can be reliably supported, so that the vibration caused by the whirling of the transmission can be suppressed.
- the invention set forth in claim 20 relates to an FR-type vehicle equipped with the hybrid drive device according to the present invention.
- the hybrid drive device can be mounted easily. Is improved.
- FIG. 1 is a plan view schematically showing an automobile according to the present invention equipped with a hybrid drive device according to the present invention.
- FIG. 2 is a skeleton diagram showing the hybrid drive device according to the first embodiment.
- FIG. 3 is a longitudinal sectional view showing a configuration of the hybrid drive device according to the first embodiment.
- FIG. 4 is a skeleton diagram showing a hybrid drive device according to a second embodiment.
- FIG. 5 is a longitudinal sectional view showing a configuration of a hybrid drive device according to a second embodiment.
- FIG. 1 shows an example of an automobile 1 according to the present invention, that is, an automobile 1 equipped with a hybrid drive device according to the present invention.
- the vehicle 1 shown in FIG. 1 is a FR (front engine / rear drive) type vehicle, and FIG. 1 is a plan view schematically showing a schematic configuration thereof.
- the direction of arrow F in the figure is the front side
- the direction of arrow R is the rear side.
- the automobile 1 shown in the figure includes a vehicle body 4 supported by left and right front wheels 2, 2 and left and right rear wheels 3, 3 serving as drive wheels.
- an internal combustion engine 5 is mounted via a rubber mount (not shown) with a crankshaft 6 as an output shaft thereof directed in the front-rear direction.
- the output shaft composed of a rearwardly projecting portion of the crankshaft is illustrated as the crankshaft 6.
- a hybrid drive 7 is connected to the rear end of the internal combustion engine 5.
- the hybrid drive device 7 includes an input shaft 10 connected to a crankshaft 6 of an internal combustion engine 5 via a damper device 8, a first electric motor 20, a planetary gear 21 for power distribution, a transmission device 22, It has a second electric motor 23 (see FIG. 2) and an output shaft 12 for outputting a driving force.
- the input shaft 10 and the output shaft 12 are arranged such that the input shaft 10 is located on the front side and the output shaft 12 is located on the rear side. And is arranged on one shaft 13.
- the input shaft 10 and the output shaft 12 are arranged in the front-rear direction with respect to the vehicle body 4, and include the first electric motor 20, the power distribution planetary gear 21, the transmission 22, and the second electric motor 23 described above. At the same time, it is housed in a case member 14 which is long in the front-rear direction.
- the hybrid drive 7 will be described later in detail.
- the output shaft 12 of the hybrid drive device 7 protrudes from the rear end of the case member 14 described above and extends further rearward, and has a flexible coupling 15 and a known propeller shaft 16 (actually, a universal joint and a center bearing). And the like, but not shown in the drawing). Further, the differential device 17 is connected to the left and right rear wheels 3, 3 via a left drive shaft 18L and a right drive shaft 18R.
- the power generated by the internal combustion engine 5 is input to the input shaft 10 of the hybrid drive device 7, and the first electric motor 20, the power distribution planetary gear 21 The output is adjusted by the transmission 22 and the second electric motor 23 and output from the output shaft 12. Then, the controlled power is transmitted to the left and right rear wheels 3, which are driving wheels, via the propeller shaft 16 and the like.
- hybrid drive device 7A As an example of the hybrid drive device 7 according to the present invention mounted on the automobile 1 shown in FIG. 1, a hybrid drive device 7A according to the present embodiment will be described. First, the overall outline of the hybrid drive device 7A will be described with reference to the skeleton diagram of FIG. 2, and then the specific configuration will be described in detail with reference to FIG. In these figures, the arrow F indicates the front side of the vehicle body (the internal combustion engine side), and the arrow R direction indicates the rear side of the vehicle body (the differential device side).
- the hybrid drive device 7A includes a second electric motor 23, a transmission 22 and a power distribution planetary gear in order from the side closer to the internal combustion engine 5 in FIG. 1, that is, from the front side to the rear side. 21, a first electric motor 20 is provided. These are all housed inside the case member 14 (see Fig. 1), and are arranged on the one axis 13 (around the one axis 13) in order from the front along the one axis 13 from the front. Is established.
- the second electric motor 23, the transmission 22, the power distribution planetary gear 21, and the first electric motor 20 will be described in this order. I will tell.
- the second electric motor 23 includes a stator 28 fixed to a case member 14 (see FIG. 1) and an inner diameter side of the stator 28 (in the following description, a radial position of the case member 14 And a rotor 29 rotatably supported at the center (one shaft 13) is closer to the inner diameter side and the far side is called the outer diameter side.
- the second electric motor 23 has its rotor 29 connected to a sun gear S1 of the transmission 22 described later.
- the second electric motor 23 is connected to an HV battery (hybrid drive battery: not shown) via an inverter (not shown), like the first electric motor 20 described later. But its main function is different.
- the second electric motor 23 functions as a drive motor to assist mainly the power (drive force) of the automobile 1 unlike the first electric motor 20 is mainly used for power generation. . However, it functions as a generator during braking and regenerates the vehicle's inertia as electric energy.
- the transmission 22 has a so-called Ravigneaux type planetary gear unit 27 composed of one double pinion planetary gear and a single planetary gear sharing the one pinion gear, and further has a first brake B 1, It has the second brake B2.
- the planetary gear unit 27 includes two sun gears SI and S2, a carrier CR1 supporting a pinion P1 and a pinion (common long pinion) P2, and a ring gear R1.
- the pinion P1 is combined with the sun gear S1 and the ring gear R1
- the common long pinion pinion P2 is combined with the sun gear S2 and the pinion P1.
- the ring gear R1 is connected to the first brake B1
- the sun gear S2 is connected to the second brake B2.
- a sun gear S1 serving as an input member is connected to the rotor 29 of the second electric motor 23, and a carrier CR1 serving as an output member is connected to a carrier CR0 of a planetary gear 21 for power distribution described later.
- the output shaft 12 is connected to the output shaft 12.
- this transmission 22 engages one of the first and second brakes Bl and B2 and releases the other, and vice versa. With this, it is possible to switch to two speed reduction stages with different reduction ratios. That is, the transmission 22 is connected to the second The magnitude of the power input from the electric motor 23 via the sun gear SI is changed and transmitted to the output shaft 12 via the carrier CR1.
- the power distribution planetary gear 21 is constituted by a double pinion planetary gear coaxially arranged with respect to the output shaft 12.
- the power distribution planetary gear 21 includes a carrier (third rotating element) CRO that supports a plurality of pinions PO (P01 and P02), a sun gear (second rotating element) SO that matches the pinion P01, and a pinion A ring gear (first rotating element) R0 that matches P02.
- the power distribution planetary gear 21 has a ring gear R0 connected to the input shaft 10, a sun gear SO connected to the rotor 25 of the first electric motor 20, and a carrier CR0 connected to the output shaft 12.
- Such a power distribution planetary gear 21 transfers the power input to the ring gear R0 via the input shaft 10 to the first electric motor 20 via the sun gear SO based on the rotation control of the first electric motor 20. And the output shaft 12 via the carrier CR0.
- the power distributed to the first electric motor 20 is used for power generation, while the power distributed to the output shaft 12 is used for driving the automobile 1.
- the first electric motor 20 has a stator 24 fixed to a case member (see Fig. 1) 14, and a rotor 25 rotatably supported on the inner diameter side of the stator 24.
- the first electric motor 20 has a rotor 25 connected to the sun gear SO of the power distribution planetary gear 21 described above.
- the first electric motor 20 generates power based on power input via the sun gear S0, and charges the HV battery via an inverter. is there.
- Hybrid drive device 7A shown in FIG. 2 includes second electric motor 23, transmission 22, planetary gear 21 for power distribution, and first electric motor 20, two of which are disposed on input shaft 10. 23, and the other two are arranged on the output shaft 12.
- the input shaft 10 extends rearward through the second electric motor 23 and the inner peripheral side of the transmission 22 to connect the rear of the transmission 22 and the front of the planetary gear 21 for power distribution.
- the rotor 29 of the second electric motor 23 extends rearward through a space between the outer peripheral side of the input shaft 10 and the inner peripheral side of the sun gear S2 of the transmission 22 and is connected to the sun gear S1 of the transmission 22.
- the carrier CR1 extends to the outer diameter side, passes through the outer peripheral side of the ring gear RO of the power distribution planetary gear 21, and is connected to the carrier CR0 of the power distribution planetary gear 21 from the rear side (the first electric motor 20 side). Further, the rotor 25 of the first electric motor 20 extends forward on the outer peripheral side of the output shaft 12 and is connected to the sun gear SO of the power distribution planetary gear 21. Then, as described above, the ring gear R0 is connected to the input shaft 10, the carrier CR0 is connected to the carrier CR1 of the transmission 22, and the sun gear SO is connected to the rotor 25 of the first electric motor 20. In the distribution planetary gear 21, the front side (the transmission 22 side) of the carrier CR0 is connected to the front end of the output shaft 12. The output shaft 12 extends rearward through the power distribution planetary gear 21 and the inner peripheral side of the first electric motor 20.
- the position of the above-described second electric motor 23, the transmission 22, the power distribution planetary gear 21, and the first electric motor 20 in the front-rear direction that is, the position along the one shaft 13
- at least the second electric motor 23 is disposed on the front side of the first electric motor 20.
- the second electric motor 23 is disposed on the most front side (the side near the internal combustion engine 5).
- Fig. 3 shows an upper half of a longitudinal section including the single shaft 13 of the hybrid drive device 7A.
- the hybrid drive device 7A shown in the figure includes an input shaft 10 and an output shaft 12 arranged on a single shaft 13, a periphery of the single shaft 13 (on a single shaft 13), and a single shaft 13 of a bracket.
- the case member 14 is integrally formed by joining portions divided into a plurality of portions in the front-rear direction along the one shaft 13 at joining surfaces in consideration of assemblability and the like.
- the front split case 14A and the rear split case 14B are The case member 14 is configured by being connected and integrated.
- the joining surface H is located near the rear end of the power distribution planetary gear 21, that is, slightly before the partition D described below.
- a plurality of partitions (support members), that is, partitions A, B, C, D, and E are sequentially formed at different positions in the front-rear direction, that is, from the front side.
- bulkheads A and E are respectively disposed near the front end and rear end of the case member 14, and the space in the case between the bulkheads A and E is bulkheads B, C and D. Is divided into four spaces in the front-rear direction along one axis 13.
- These partition walls A to E serve as strength members of the case member 14, and are used for holding the bearings (bearing members) a to x (described later) and forming the hydraulic chambers 40 and 45 (described later).
- the partition walls A and D are formed by attaching separate disk-shaped partition members, which are separate members, to the positions shown in the drawing (for example, fixing them with bolts). are doing.
- the radial dimension of the motor housing 14A1 between the partition walls A and B in the split case 14A is set to be larger than the radial dimension of the motor housing 14B1 in the split case 14B.
- the above-described second electric motor 23, the transmission 22, the power distribution planetary gear 21, and the first electric motor 20 are housed in spaces each divided into four by partitions A to E. That is, the second electric motor 23 is between the partition walls A and B, the transmission 22 is between the partition walls B and C, the planetary gear 21 for power distribution is between the partition walls C and D, and the first electric motor 20 is It is stored between the partition walls D and E, respectively.
- the second electric motor 23 will be described in detail in order.
- the second electric motor 23 is constituted by, for example, an AC permanent magnet synchronous type (brushless DC motor), and is disposed coaxially on the outer diameter side of the input shaft 10.
- the second electric motor 23 includes a stator 28 fixed to the inner peripheral surface of the case member 14 and a rotor 29 rotatably disposed on the inner diameter side of the stator 28 with a predetermined air gap G2 therebetween.
- the rotor 29 has a cylindrical shape on the inner diameter side, and stepped portions 48 and 50 are formed on a front outer peripheral surface and a rear outer peripheral surface of the cylindrical portion, respectively.
- the motor 29 is positioned between these steps 48, 50 and the bulkheads A, B in the front-rear direction.
- the second electric motor 23 is connected to an HV battery via an inverter, like the first electric motor 20 described later.
- the input shaft 10 includes a bearing c provided at a position overlapping the bearing a in the axial direction, an outer peripheral surface of a rear end portion of the input shaft 10, and an inner peripheral surface of a cylindrical portion at a front end of the output shaft 12.
- Bearing provided between the output gear 12 and the sun gear SO of the power distribution planetary gear 21 and the output shaft 12 !, s, and the rotor 25 and the partition wall D of the first electric motor 20 It is rotatably supported by the case member 14 via the bearing t between the two.
- the transmission 22 is provided between the partition walls B and C of the case member 14, that is, in the longitudinal direction of the case member 14.
- the transmission 22 has a Ravigneaux type planetary gear unit 27 disposed on the inner diameter side, and first and second brakes Bl and B2 disposed on the rear and front sides on the outer diameter side, respectively. are doing.
- the planetary gear unit 27 includes a first sun gear S1 (hereinafter simply referred to as “sun gear Sl”) and a second sun gear S2 (hereinafter referred to as “sun gear Sl”) disposed slightly outside in diameter in front of the sun gear S1.
- unsun gear S2 simply referred to as “sun gear S2”)
- a ring gear R1 disposed on the outer diameter side of the sun gear S1
- a pinion P1 which is combined with the sun gear S1 and the ring gear R1
- sun gear S2 and a pinion which constitute a common long pinion. It has a pinion P2 corresponding to P1, and a carrier CR1 supporting these pinions P1 and P2.
- the sun gear S1 will be described in order.
- the sun gear S1 is connected to the rear end of the rotor 29 of the second electric motor 23 via the sleeve 63 described above.
- This sun gear S1 together with the sleeve 63 as described above, It is rotatably supported by the input shaft 10 via bearings d and e fitted on the outer peripheral surface of the shaft 10.
- the sun gear S2 includes a flange portion 34 extending outward from the front end side along the front carrier plate CRlb of the carrier CR1 and a drum portion 35 extending rearward from the outer diameter end of the flange portion 35. Is formed in the body.
- a second brake B2 described below is interposed between the outer peripheral surface of the drum portion 35 and the inner peripheral spline 14a of the inner peripheral surface of the case member 14.
- the sun gear S2 includes bearings f and g fitted on the outer peripheral surface of the sleeve 63 integrated with the sun gear S1, and bearings fitted on the front and rear surfaces on the inner diameter side (base end side) of the flange portion 34, respectively. It is rotatably supported by h and i.
- the bearing h is interposed between the rear side of the inner diameter side of the bulkhead B, and the bearing i is interposed between the front side of the front carrier plate CRlb of the carrier CR1 described later and the front side of the inner side of the sun gear. It regulates the axial movement of S2.
- the ring gear R1 has, at its rear end, a flange portion 36 extending radially inward along the rear carrier plate CRla of the carrier CR1, and a front surface and a rear surface of the flange portion 36 on the radially inner side. It is rotatably supported by bearings j and k fitted to.
- the bearing j is interposed between the rear carrier plate CRla of the carrier CR1 and the bearing k is interposed between the inner side of the bulkhead C and the bearing k.
- a first brake B1 is interposed between the outer peripheral surface of the ring gear R1 and the inner peripheral spline 14a on the inner peripheral surface of the case member 14, and regulates the axial movement of the ring gear R1.
- the pinion P1 is rotatably supported by the carrier CR1, and is joined to the sun gear 1 on the inner diameter side and to the ring gear R1 on the outer diameter side.
- the pinion P2 is a common long pinion in which a large-diameter gear P2a formed on the front side and a small-diameter gear P2b formed on the rear side are integrally formed.
- the large diameter gear P2a of the pinion P2 is combined with the above-mentioned sun gear S2, and the small diameter gear P2b is combined with the above-mentioned pinion P1.
- the carrier CR1 rotatably supports the pinions PI and P2 by a front carrier plate CRlb and a rear carrier plate CRla, and the rear carrier plate CRla is connected. It is connected to a rear carrier plate CROa of a carrier CRO of a power distribution planetary gear 21 described later via a coupling member 64.
- the connecting member 64 includes a sleeve portion connected to the rear end of the rear carrier plate CRla of the carrier CR1 and extending rearward, a flange portion extending from the rear end of the sleeve portion to the outer diameter side, and an outer diameter of the flange portion.
- the carrier C R1 is relatively rotated by the bearing i described above fitted on the front surface on the inner diameter side of the front carrier plate CRlb, and the bearing j fitted on the rear surface on the inner diameter side of the rear carrier plate CRla. It is freely supported. Further, the carrier CR1 is fitted to the bearing h fitted to the front surface on the inner diameter side (base end side) of the flange portion 34 extending from the sun gear S2, and to the rear surface of the inner diameter side of the flange portion 36 extended from the ring gear R1. Through the bearing k, the axial movement of the partition walls B and C is regulated so as to be freely rotatable.
- the first brake B 1 has a number of disks and a friction plate (brake plate), and has an outer peripheral spline formed on the outer peripheral surface of the ring gear R 1 and an inner peripheral surface of the case member 14. It is spline-coupled to the formed inner peripheral spline 14a.
- a hydraulic actuator 37 for the first brake is provided behind the first brake B1.
- the hydraulic actuator 37 is provided on the outer diameter side front surface of the partition wall C so as to be movable in the front-rear direction behind the first brake B1, and the rear end side of the piston 38 is fitted in an oil-tight manner.
- a return spring (compression spring) 42 interposed between the first hydraulic chamber 40, the retainer 41 fixed to the partition C, and the front surface on the inner diameter side of the piston 38, and for urging the piston 38 rearward; have.
- the second brake B2 is disposed immediately in front of the above-described first brake B1.
- the second brake B2 has a large number of disks and a friction plate (brake plate), and has an outer peripheral spline formed on the outer peripheral surface of the drum portion 35 integrated with the sun gear S2, It is spline-coupled to the inner peripheral spline 14a formed on the peripheral surface.
- a hydraulic actuator 43 for the second brake is provided in front of the second brake B2.
- the hydraulic actuator 43 includes a piston 44 disposed in front of the second brake B2 so as to be movable in the front-rear direction, and a piston 44 provided on the outer diameter side rear surface of the partition wall B.
- a second hydraulic chamber 45 in which the front end side of the piston 44 is fitted in an oil-tight manner is interposed between a retainer 46 fixed to the partition wall B and a rear surface on the inner diameter side of the piston 44 so that the piston 44 faces forward. It has a return spring (compression spring) 47 for biasing.
- the output from the second electric motor 23 is transmitted to the sun gear S1 via the sleeve 63.
- the first brake B1 is engaged, and the second brake B2 is released. Therefore, the ring gear 1 is in the fixed state, the sun gear S2 is in the S-force free rotation state, and the rotation of the i-th sun gear S1 is greatly reduced through the pinion P1 and transmitted to the carrier CR1, and the rotation of the carrier CR1 is performed. It is transmitted to the output shaft 12.
- the first and second brakes Bl and B2 are engaged and released, respectively, to output a greatly decelerated rotation. Transmit to shaft 12.
- the first and second brakes Bl and B2 are released and engaged, respectively, thereby transmitting a relatively small decelerated rotation to the output shaft 12.
- the speed change device 22 can change the speed in two stages, so that the size of the second electric motor 23 can be reduced. That is, a small electric motor is used to transmit a sufficient drive torque to the output shaft 12 in a low state when starting the automobile 1 requiring a high tonnolek, for example. As a state, it is possible to prevent the rotor 29 from rotating at a high speed.
- the power distribution planetary gear 21 is disposed between the partition walls C and D of the case member 14.
- the power distribution planetary gear 21 is constituted by a double-pinion planetary gear coaxially arranged with respect to the output shaft 12, and includes a ring gear (first rotating element) RO and a sun gear (second gear).
- a rotating element A carrier (third rotating element) that supports SO and pinions P01 and P02 (these are collectively shown in FIG. 3 as pinion P0).
- CR0 the ring gear R0 extends forward and is fixed to the outer diameter side end of the flange portion 61 extending outward from the outer peripheral surface near the rear end of the input shaft 10 along the carrier CR0.
- the carrier CR0 has a front carrier plate CROb connected to the front end of the output shaft 12.
- the sun gear SO extends rearward and is connected to the rotor 25 of the first electric motor 20.
- Bearings ns are fitted to the power distribution planetary gears 21 at the following positions.
- the bearing n is between the inside rear surface of the flange of the connecting member 64 and the front surface of the inside of the flange 61
- the bearing o is the rear surface of the inside of the flange 61 and the front surface of the carrier plate CROb.
- the bearing p is fitted between the inner rear surface of the front carrier plate CROb and the front end surface of the sun gear SO.
- the bearing q is between the outer peripheral surface of the rear end of the input shaft 10 and the inner peripheral surface of the cylindrical portion at the front end of the output shaft 12, and the bearings r and s are the outer peripheral surface of this cylindrical portion and the sun gear SO.
- the power distribution planetary gear 21 has a ring gear R0 serving as an input unit fixed to the input shaft 10, and a sun gear S0 and a carrier CR0 serving as an output unit (power distribution destination) each having a first electric motor.
- the front end of the rotor 25 and the front end of the output shaft 12 are connected.
- the power distribution planetary gear 21 transfers the power of the internal combustion engine 5 (see FIG.
- the power distribution ratio at this time is determined based on the rotation state of the first electric motor 20 described below. That is, when a larger power is generated by the rotor 25 of the first electric motor 20, the amount of power generated by the first electric motor 20 increases, and the power output to the output shaft 12 decreases accordingly. On the other hand, when a small power is generated in the rotor 25 of the first electric motor 20, the amount of power generated by the first electric motor 20 decreases, and the power output to the output shaft 12 is correspondingly reduced. More.
- the first electric motor 20 is, for example, an AC permanent magnet synchronous type (brushless DC motor). It is housed between the partition walls D and E, and is arranged coaxially on the outer diameter side of the output shaft 12.
- the first electric motor 20 includes a stator 24 fixed to the inner peripheral surface of the case member 14 and a rotor 25 that is rotatably disposed on the inner diameter side of the stator 24 with a predetermined air gap G1 therebetween.
- the inner diameter side of the rotor 25 is formed in a cylindrical shape, and stepped portions 30 and 31 are formed on a front outer peripheral surface and a rear outer peripheral surface of the cylindrical portion, respectively.
- the rotor 25 is rotatably supported by the case member 14 through bearings t and u fitted between the step portions 30 and 31 and the partition walls D and E while being positioned in the front-rear direction. ing.
- the sun gear SO of the power distribution planetary gear 21 described above is fixed.
- the rotor 25 and the sun gear SO formed integrally with each other are rotatably supported by the output shaft 12 via bearings r, s, and v fixed to the outer peripheral surface on the front end side of the output shaft 12. I have.
- the bearings s and V are arranged at positions corresponding to the bearings t and u, respectively, in the arrangement position in the front-rear direction.
- the first electric motor 20 since the first electric motor 20 has the rotor 25 rotatably supported by the bearings t and u fixed to the partition walls D and E, the first electric motor 20 has a position in the front-rear direction and the radial direction of the rotor 25. Therefore, for example, even when a force acting to bend the case member 14 vertically or horizontally is applied, a predetermined air gap G1 is accurately maintained between the stator 24 and the rotor 25. can do.
- the first electric motor 20 is connected to the HV battery via the inverter.
- the main function of the first electric motor 20 having such a configuration is to generate power based on the power distributed to the sun gear SO of the power distribution planetary gear 21 described above, and to generate the second electric motor 23 via an inverter. To drive or charge the HV battery.
- the input shaft 10 includes a bearing c provided at a position axially overlapping the bearing a, an outer peripheral surface of a rear end portion of the input shaft 10, and an inner peripheral surface of a cylindrical portion at a front end of the output shaft 12.
- the case member 14 in which the second electric motor 23, the transmission 22, the power distribution planetary gear 21, and the first electric motor 20 are housed is located on the inner diameter side of the rearmost partition E.
- the outer diameter side of the partition wall E is formed to have a large thickness to form a mounting portion (mounting portion) 14c.
- the case member 14 has a front end connecting portion 14d connected to an internal combustion engine 5 rubber-mounted to the vehicle body 4 (see FIG. 1), and a rear end side of the case member 14 using a mounting portion 14c. Rubber mounted on part 4a. That is, a rubber pedestal 51 is provided on a part 4a of the vehicle body, and a stay 55 is fixed to the rubber pedestal 51 by a bonolet 52, a washer 53, and a nut 54.
- the case member 14 is attached to the stay 55 by a bolt 56 screwed to an attachment portion 14c near the rear end.
- the gap G3 between the bolt 52 on the part 4a side of the vehicle body and the bonolet 56 on the case member 14 side should be shorter than the tightening length (screw length) of the bolt 56.
- the power input to the input shaft 10 is input to the ring gear R0 of the power distribution planetary gear 21, and the sun gear SO and the carrier. Distributed (divided) to CR0.
- the power distributed to the sun gear SO is input to the rotor 25 of the first electric motor 20, and is used for power generation.
- the electricity generated in this way drives the second electric motor 23 via the inverter or is charged into the HV battery.
- the second electric motor 23 is supplied with electric power from an HV battery via an inverter, and drives the output shaft 12 via a transmission 22 and a carrier CR0.
- the power from the internal combustion engine 5 and the power from the second electric motor 23 are combined and output to the output shaft 12. Since the transmission 22 is switched between the high state and the low state as described above, a power corresponding to the high state or the low state is output to the output shaft 12.
- the second electric motor 23 is arranged on the front side (closer to the internal combustion engine 5) than the first electric motor 20. Then, the case member 14 has a radial force of the inner diameter of a portion where the stator 28 of the second electric motor 23 is fixed. It is formed to be larger than the inner diameter of the portion where the stator 24 of the electric motor 20 is fixed.
- the second electric motor 23 which needs to generate a large torque at the time of acceleration, for example, when the automobile 1 starts moving, has a larger radial dimension (compared with the first electric motor 20). ), And the length in the front-rear direction can be reduced accordingly, so that the overall length of the hybrid drive unit 7A is reduced in the front-rear direction to improve mountability on the vehicle body 4. Can be done.
- hybrid drive device 7B As another example of the hybrid drive device 7 according to the present invention mounted on the automobile 1 shown in FIG. 1, a hybrid drive device 7B according to the present embodiment will be described. First, the overall outline of the hybrid drive device 7B will be described with reference to the skeleton diagram of FIG. 4, and then the specific configuration will be described in detail with reference to FIG. In these figures, the arrow F indicates the front side of the vehicle body (the internal combustion engine side), and the arrow R direction indicates the rear side of the vehicle body (the differential device side).
- the hybrid drive device 7B includes a second electric motor 23, a transmission 22, and a first electric motor in order from the side closer to the internal combustion engine 5 in FIG. 1, that is, from the front side to the rear side.
- a motor 20 and a power distribution planetary gear 21 are provided. These are all housed inside the case member 14 (see Fig. 1), and are arranged on the one axis 13 (around the one axis 13) in order from the front along the one axis 13 from the front. Is established.
- the second electric motor 23, the transmission 22, the first electric motor 20, and the power distribution planetary gear 21 will be described in this order.
- the second electric motor 23 includes a stator 28 fixed to a case member (see Fig. 1) 14 and an inner diameter side of the stator 28 (in the following description, a radial position of the case member 14 is used). And a rotor 29 rotatably supported at the center (one shaft 13) is closer to the inner diameter side and the far side is called the outer diameter side.
- the second electric motor 23 has its rotor 29 connected to a sun gear S1 of the transmission 22 described later.
- the second electric motor 23 is connected to an HV battery (hybrid drive battery: not shown) via an inverter (not shown), like the first electric motor 20 described later. But its main function is different.
- the second electric motor 23 functions as the first electric motor 20 In contrast to this, it mainly functions as a drive for assisting the power (drive power) of the car 1. However, it functions as a generator during braking and regenerates vehicle inertia as electric energy.
- the transmission 22 has a so-called Ravigneaux type planetary gear unit 27 composed of one double pinion planetary gear and a single pinion planetary gear sharing one pinion, and further includes a first brake. B1 and a second brake B2.
- the planetary gear unit 27 includes two sun gears SI and S2, a carrier CR1 supporting a pinion P1 and a pinion (common long pinion) P2, and a ring gear R1.
- the pinion P1 mates with the sun gear S1 and the ring gear R1
- the common long pinion pinion P2 mates with the sun gear S2 and the pinion P1.
- the ring gear R1 is connected to the first brake B1
- the sun gear S2 is connected to the second brake B2.
- a sun gear S1 serving as an input member is connected to the rotor 29 of the second electric motor 23, and a carrier CR1 serving as an output member is connected to a carrier CR0 of a planetary gear 21 for power distribution described later.
- the output shaft 12 is connected to the output shaft 12.
- the transmission 22 engages one of the first and second brakes Bl and B2 and releases the other, and vice versa. With this, it is possible to switch between two reduction gears with different reduction ratios. That is, the transmission 22 changes the magnitude of the power input from the second electric motor 23 via the sun gear S1 and transmits the power to the output shaft 12 via the carrier CR1.
- the first electric motor 20 has a stator 24 fixed to a case member (see Fig. 1) 14, and a rotor 25 rotatably supported on the inner diameter side of the stator 24.
- the first electric motor 20 has a rotor 25 connected to a sun gear SO of a power distribution planetary gear 21 described later.
- the first electric motor 20 mainly generates electric power based on the power input through the sun gear SO, and charges the HV battery through the inverter. is there.
- the power distribution planetary gear 21 is a double It is composed of two-on planetary gears.
- the power distribution planetary gear 21 includes a carrier (third rotating element) CR0 that supports a plurality of pinions PO (P01 and P02), a sun gear (second rotating element) SO that matches the pinion P01, and a pinion.
- the power distribution planetary gear 21 has a ring gear R0 connected to the input shaft 10, a sun gear SO connected to the rotor 25 of the first electric motor 20, and a carrier CR0 connected to the output shaft 12.
- Such a power distribution planetary gear 21 transfers the power input to the ring gear R0 via the input shaft 10 to the first electric motor 20 via the sun gear SO based on the rotation control of the first electric motor 20. And the output shaft 12 via the carrier CR0.
- the power distributed to the first electric motor 20 is used for power generation, while the power distributed to the output shaft 12 is used for driving the automobile 1.
- the input shaft 10 extends rearward through the inner peripheral side of the second electric motor 23, the transmission 22, the first electric motor 20, and the planetary gear 21 for power distribution.
- the distribution planetary gear 21 is connected to the ring gear R0 from the rear side.
- the rotor 29 of the second electric motor 23 extends rearward through the space between the outer peripheral side of the input shaft 10 and the inner peripheral side of the sun gear S2 of the transmission 22, and is connected to the sun gear S1 of the transmission 22.
- the carrier CR1 of the transmission 22 extends rearward through the space between the outer peripheral surface of the input shaft 10 and the inner peripheral side of the first electric motor 20 and the planetary gear 21 for power distribution.
- the rear gear 21 is connected to the carrier CR0 from the rear side.
- the rotor 25 of the first electric motor 20 extends rearward and is connected to the sun gear SO of the power distribution planetary gear 21.
- the ring gear R0 is connected to the input shaft 10
- the carrier CR0 is connected to the carrier CR1 of the transmission 22, and the sun gear S0 is connected to the rotor 25 of the first electric motor 20.
- the front side of the carrier CR0 (the first electric motor 20 side) of the planetary gear 21 is connected to the front end of the output shaft 12 through the outer peripheral side of the ring gear R0 and the rear side of the power distribution planetary gear 21.
- This output shaft 12 extends rearward.
- the above-mentioned second electric motor 23, the transmission 22, the power distribution planetary gear 21, and the first electric motor 20 are arranged in the front-rear direction, that is, arranged along the one shaft 13.
- at least the second electric motor 23 is disposed on the front side of the first electric motor 20. Further, in the present embodiment, the second electric motor 23 is disposed on the most front side (the side near the internal combustion engine 5).
- the hybrid drive device 7B achieves good mountability on the vehicle body 4.
- Fig. 5 shows the upper half of the longitudinal section including the single shaft 13 of the hybrid drive device 7B.
- the hybrid drive device 7B shown in the figure has an input shaft 10 and an output shaft 12 arranged on a single shaft 13, and around the single shaft 13 (on the single shaft 13), A second electric motor 23, a transmission 22, a first electric motor 20, and a power distribution planetary gear 21 are arranged in line with each other. These are all stored in the case member 14. However, a part of the rear end side of the output shaft 12 protrudes rearward from the case member 14.
- the case member 14 is integrally formed by joining portions divided into a plurality of parts in the front-rear direction along one axis 13 at joining surfaces.
- the front divided case 14A and the rear divided case 14B are connected to each other at the joint surface H and integrated to form the case member 14.
- the contact surface H is located near the front end of the power distribution planetary gear 21, that is, a little after the partition D described below.
- a plurality of partitions (support members), that is, partitions A, B, C, D, and E are formed at different positions in the front-rear direction, that is, in order from the front side.
- bulkheads A and E are respectively disposed near the front end and rear end of the case member 14, and the space in the case between the bulkheads A and E is bulkheads B, C and D. Is divided into four spaces in the front-back direction along one axis 13.
- These partition walls AE serve as strength members of the case member 14, and are used for holding the bearings (bearing members) ax (described later) and forming the hydraulic chambers 40 and 45 (described later).
- partition A, D The partition walls A and D are configured by attaching a separate disk-shaped partition member, which is a separate member, to the position shown in FIG.
- the radial dimension of the motor storage portion 14A1 between the partition walls A and B in the divided case 14A is set to be larger than the radial dimension of the motor storage portion 14A2 between the partition walls C and D.
- the second electric motor 23, the transmission 22, the first electric motor 20, and the power distribution planetary gear 21 described above are housed in spaces each divided into four by a partition AE. That is, the second electric motor 23 is provided between the partition walls A and B, the transmission 22 is provided between the partition walls B and C, the first electric motor 20 is provided between the partition walls C and D, and the power distribution planetary gear 2 1 Are housed between the partition walls D and E, respectively.
- the details will be described in order from the second electric motor 23.
- the second electric motor 23 is constituted by, for example, an AC permanent magnet synchronous type (brushless DC motor), and is disposed coaxially with the input shaft 10 on the outer diameter side thereof.
- the second electric motor 23 includes a stator 28 fixed to the inner peripheral surface of the case member 14 and a rotor 29 rotatably disposed on the inner diameter side of the stator 28 with a predetermined air gap G2 therebetween.
- the rotor 29 has a cylindrical shape on the inner diameter side, and stepped portions 48 and 50 are formed on a front outer peripheral surface and a rear outer peripheral surface of the cylindrical portion, respectively.
- the rotor 29 is rotatably supported by the case member 14 via bearings a and b fitted between the step portions 48 and 50 and the partition walls A and B while being positioned in the front-rear direction. ing.
- the rear end of the cylindrical portion is connected to a later-described sun gear S1 of the transmission 22 via a sleeve 63 fitted on the outer peripheral surface of the input shaft 10.
- the rotor 29 and the sun gear S1 formed integrally with each other are supported by the input shaft 10 so as to be relatively rotatable via bearings c, d, and e fixed to the outer peripheral surface of the input shaft 10.
- the bearings c and d are located at the positions corresponding to the bearings a and b, respectively.
- the second electric motor 23 since the rotor 29 is rotatably supported by the bearings a and b fixed to the partition walls A and B, the position of the rotor 29 in the front-rear direction and the radial direction can be accurately determined. Therefore, even if, for example, a force is applied to the case member 14 so as to bend it vertically or horizontally, the gap between the stator 28 and the rotor 29 is maintained. Thus, the predetermined air gap G2 can be accurately maintained.
- the second electric motor 23 is connected to an HV battery via an inverter, similarly to a first electric motor 20 described later.
- the input shaft 10 includes a bearing c provided at a position axially overlapping the bearing a, an outer peripheral surface of a rear end portion of the input shaft 10, and an inner peripheral surface of a cylindrical portion at a front end of the output shaft 12. Via the bearing y provided between the inner surface of the output shaft 12 and the inner peripheral surface of the boss 14b extending rearward. 14 rotatably supported.
- the transmission 22 is provided between the partition walls B and C of the case member 14, that is, in the longitudinal direction of the case member 14.
- the transmission 22 has a Ravigneaux type planetary gear unit 27 disposed on the inner diameter side, and first and second brakes Bl and B2 disposed on the rear and front sides on the outer diameter side, respectively. are doing.
- the planetary gear unit 27 includes a first sun gear S1 (hereinafter simply referred to as “sun gear Sl”) and a second sun gear S2 (hereinafter referred to as “sun gear Sl”) disposed slightly outside in diameter in front of the sun gear S1.
- unsun gear S2 simply referred to as “sun gear S2”)
- a ring gear R1 disposed on the outer diameter side of the sun gear S1
- a pinion P1 which is combined with the sun gear S1 and the ring gear R1
- sun gear S2 and a pinion which constitute a common long pinion. It has a pinion P2 corresponding to P1, and a carrier CR1 supporting these pinions P1 and P2.
- the sun gear S1 will be described in order.
- the sun gear S1 is connected to the rear end of the rotor 29 of the second electric motor 23 via the sleeve 63 described above.
- the sun gear S1, together with the sleeve 63, is supported by the input shaft 10 via the bearings c, d, and e fitted on the outer peripheral surface of the input shaft 10 as described above.
- the sun gear S2 has a flange portion 34 extending outward from the front end side along the front carrier plate CRlb of the carrier CR1, and a drum portion 35 extending rearward from the outer diameter end of the flange portion 35. Is formed in the body.
- a second brake B2 described below is interposed between the outer peripheral surface of the drum portion 35 and the inner peripheral spline 14a of the inner peripheral surface of the case member 14.
- the sun gear S2 is fitted to the bearings f and g fitted on the outer peripheral surface of the sleeve 63 integrated with the sun gear S1 and the front and rear surfaces on the inner diameter side (base end side) of the flange portion 34, respectively. It is rotatably supported by bearings h and i.
- the bearing h is interposed between the rear surface of the inner wall of the bulkhead B and the bearing i is interposed between the front surface of the front carrier plate CRlb of the carrier CR1 and the front surface of the inner side of the carrier CRlb. It is.
- the ring gear R1 has, at its rear end, a flange portion 36 extending radially inward along the rear carrier plate CRla of the carrier CR1, and a front surface and a rear surface of the flange portion 36 on the radially inner side. It is rotatably supported by the bearings j and k fitted to it.
- the bearing j is interposed between the rear carrier plate CRla of the carrier CR1 and the bearing k is interposed between the inner side of the bulkhead C and the bearing k.
- a first brake B1 is interposed between the outer peripheral surface of the ring gear R1 and the inner peripheral spline 14a of the inner peripheral surface of the case member 14.
- the pinion P1 is rotatably supported by the carrier CR1, and is coupled to the sun gear 1 on the inner diameter side and to the ring gear R1 on the outer diameter side.
- the pinion P2 is a common long pinion in which a large-diameter gear P2a formed on the front side and a small-diameter gear P2b formed on the rear side are integrally formed.
- the large diameter gear P2a of the pinion P2 is combined with the above-mentioned sun gear S2, and the small diameter gear P2b is combined with the above-mentioned pinion P1.
- the carrier CR1 has a front carrier plate CRlb and a rear carrier plate CRla that rotatably support the pinions PI and P2, and a sleeve 65 on which the rear carrier plate CRla extends rearward.
- the sleeve 65 has a front end connected to a rear carrier plate CRla, an intermediate portion passing through the inside of a rotor 25 of a second electric motor 20, which will be described later, and a rear end located at the rear side of the power distribution planetary gear 21.
- the sleeve 65 is rotatably supported by a bearing 1 m fitted between the sleeve 65 and the outer peripheral surface of the input shaft 10.
- the carrier CR1 is composed of the bearing i described above fitted on the front surface on the inner diameter side of the front carrier plate CRlb, and the bearings n and j fitted on the inner surface front and rear surfaces of the rear carrier plate CRla, respectively. Are supported so as to be relatively rotatable.
- the bearing n is the sun gear S1 described above. It is interposed between the rear end face.
- the first brake B1 has a number of disks and a friction plate (brake plate), and has an outer peripheral spline formed on the outer peripheral surface of the ring gear R1 and an inner peripheral surface of the case member 14. It is spline-coupled to the formed inner peripheral spline 14a.
- a hydraulic actuator 37 for the first brake is provided behind the first brake B1.
- the hydraulic actuator 37 is provided behind the first brake B1 so as to be movable in the front-rear direction, and is provided on the front surface on the outer diameter side of the partition wall C, and the rear end side of the piston 38 is fitted in an oil-tight manner.
- a return spring (compression spring) 42 interposed between the first hydraulic chamber 40 and the retainer 41 fixed to the partition C and the front surface on the inner diameter side of the piston 38 to urge the piston 38 rearward; have.
- the second brake B2 is disposed immediately in front of the above-described first brake B1.
- the second brake B2 has a large number of disks and a friction plate (brake plate), and has an outer peripheral spline formed on the outer peripheral surface of the drum portion 35 integrated with the sun gear S2, It is spline-coupled to the inner peripheral spline 14a formed on the peripheral surface.
- a hydraulic actuator 43 for the second brake is arranged in front of the second brake B2.
- the hydraulic actuator 43 includes a piston 44 disposed in front of the second brake B2 so as to be movable in the front-rear direction, and a hydraulic actuator 43 provided on the rear surface on the outer diameter side of the partition wall B so that the front end side of the piston 44 is oil-tightly fitted. 2) and a return spring (compression spring) 47 interposed between a retainer 46 fixed to the partition wall B and the rear surface on the inner diameter side of the piston 44 to urge the piston 44 forward. I have it.
- the output from the second electric motor 23 is transmitted to the sun gear S1 via the sleeve 63.
- the first brake B1 is engaged, and the second brake B2 is released.
- the ring gear 1 is in the fixed state, the sun gear S2 is in the S-force free rotation state, and the rotation of the i-th sun gear S1 is greatly reduced through the pinion P1 and transmitted to the carrier CR1, and the rotation of the carrier CR1 is performed. It is transmitted to the output shaft 12.
- the speed change device 22 can change the speed in two stages, so that the size of the second electric motor 23 can be reduced. That is, a small electric motor is used to transmit a sufficient drive torque to the output shaft 12 in a low state when starting the automobile 1 requiring a high tonnolek, for example. As a state, it is possible to prevent the rotor 29 from rotating at a high speed.
- the first electric motor 20 is constituted by, for example, an AC permanent magnet synchronous type (brushless DC motor), is housed between the partition walls C and D, and is provided on the outer diameter side of the input shaft 10. It is arranged coaxially with this.
- the first electric motor 20 includes a stator 24 fixed to the inner peripheral surface of the case member 14 and a rotor 25 that is rotatably disposed on the inner diameter side of the stator 24 with a predetermined air gap G1 therebetween.
- the inner diameter side of the rotor 25 is formed in a cylindrical shape, and stepped portions 30 and 31 are formed on a front outer peripheral surface and a rear outer peripheral surface of the cylindrical portion, respectively.
- the rotor 25 is rotatably supported by the case member 14 via bearings o and p fitted in the front and rear positions between the stepped portions 30 and 31 and the partition walls C and D. ing.
- a sun gear SO of a power distribution planetary gear 21 described later is fixed.
- the rotor 25 and the sun gear SO formed integrally with each other are connected to the sleeve 65 via bearings q, r, and s fixed to the outer peripheral surface of the above-described sleeve 65 fitted on the outer peripheral surface of the input shaft 10.
- the bearings q and r are arranged at positions corresponding to the bearings o and p, respectively, in the longitudinal direction.
- the first electric motor 20 is configured such that the rotor 25 is sandwiched between the bearings o and p fixed to the partition walls C and D and the bearings q and r fixed to the outer peripheral surface of the sleeve 65.
- the rotor 25 is rotatably supported, the position in the front-rear direction and the radial direction of the rotor 25 is accurately secured. Therefore, for example, even when a force that bends the case member 14 vertically or horizontally is applied, A predetermined air gap G1 can be accurately maintained between the stator 24 and the rotor 25.
- the first electric motor 20 is connected to the HV battery via the inverter.
- the main function of the first electric motor 20 having such a configuration is to generate power based on the power distributed to the sun gear SO of the power distribution planetary gear 21 described later, and to generate the second electric motor via the inverter. 23 is to drive or charge the HV battery.
- the power distribution planetary gear 21 is disposed between the partition walls D and E of the case member 14.
- the power distribution planetary gear 21 is constituted by a double pinion planetary gear coaxially arranged with respect to the input shaft 10, and includes a ring gear (first rotating element) R0 and a sun gear (second gear). And a carrier (third rotating element) CR0 that supports the pinions P01 and P02 (these are collectively shown as a pinion P0 in FIG. 5).
- the ring gear R0 extends rearward and is fixed to the outer diameter side end of a flange portion 61 extending outward from the outer peripheral surface near the rear end of the input shaft 10 along the carrier CR0.
- the rear carrier plate CROa is connected to the rear end of the sleeve 65 on the inner diameter side.
- the front side of the carrier CR0, the carrier plate CROb is connected to the front end of the output shaft 12 via a connecting member 66.
- the connecting member 66 is connected to the outer diameter end of the front carrier plate CROb and extends rearward.
- the connecting member 66 is connected to the rear end of the drum portion and extends along the rear side of the flange 61. And a flange portion extending to the inner diameter side, and the inner diameter side of the flange portion is connected to the front end of the output shaft 12.
- Bearings are fitted to the power distribution planetary gear 21 at the following positions.
- the above bearings r and s are provided between the rear end side outer peripheral surface of the sleeve 65 and the inner peripheral surface of the sun gear SO integrated with the rear carrier plate CROa, and between the rear end inner peripheral surface of the sleeve 65 and the input shaft.
- a bearing m is fitted between the outer peripheral surface on the rear end side of the bearing 10.
- Bearings t and u are fitted on the front surface and the rear surface on the inner diameter side of the rear carrier plate CROa, respectively, between the rear end surface of the sun gear S0 and the inner diameter front surface of the flange portion 61.
- a bearing V is fitted between the inside rear surface of the flange portion 61 and the inside front surface of the flange portion of the connecting member 66.
- the ring gear R0 is integrated with the input shaft 10 via the flange 61 so as to be rotatable with respect to the case member 14, and the carrier CR0 and the sun gear SO are rotatable with respect to the input shaft 10 and the sleeve 65. It is supported for relative rotation.
- the ring gear R0 serving as the input portion is fixed to the input shaft 10 via the flange portion 61, and the sun gear SO and the carrier CR0 serving as the output portion (power distribution destination) are respectively provided with the first gear.
- the electric motor 20 is connected to the rear end of the rotor 25 and the front end of the output shaft 12.
- the power distribution planetary gear 21 transmits the power of the internal combustion engine 5 (see FIG. 1) input to the ring gear R0 via the input shaft 10 to the first electric motor 20 side via the sun gear SO and the carrier CR0. To the output shaft 12 side.
- the power distribution ratio at this time is determined based on the rotation state of the first electric motor 20 described above. That is, when a larger power is generated by the rotor 25 of the first electric motor 20, the amount of power generated by the first electric motor 20 increases, and the power output to the output shaft 12 decreases accordingly. On the other hand, when a small power is generated in the rotor 25 of the first electric motor 20, the amount of power generated by the first electric motor 20 decreases, and the power output to the output shaft 12 is correspondingly reduced. More.
- the case member 14 in which the second electric motor 23, the transmission 22, the first electric motor 20, and the power distribution planetary gear 21 are housed is located on the inner diameter side of the rearmost partition wall E.
- case member 14 has a front end side connecting portion 14d connected to the internal combustion engine 5 rubber-mounted on the vehicle body 4 (see FIG. 1), and a rear side provided on the outer diameter portion of the partition wall D. It is rubber-mounted on a part of the vehicle body using a mounting part (not shown).
- the power input to the input shaft 10 is input to the ring gear R0 of the power distribution planetary gear 21, and the sun gear SO and the carrier Distributed (divided) to CR0.
- the power distributed to the sun gear S0 is input to the rotor 25 of the first electric motor 20, and is used for power generation.
- the electricity generated in this way drives the second electric motor 23 via the inverter or charges the HV battery. Is charged.
- the second electric motor 23 is supplied with electric power from an HV battery via an inverter, and drives the output shaft 12 via a transmission 22 and a carrier CR0.
- the power from the internal combustion engine 5 and the power from the second electric motor 23 are combined and output to the output shaft 12. Since the transmission 22 is switched between the high state and the low state as described above, the power corresponding to the high state or the low state is output to the output shaft 12.
- the second electric motor 23 is disposed on the front side (closer to the internal combustion engine 5) than the first electric motor 20. Then, the case member 14 is formed to have a larger force than the inner diameter of the portion where the stator 24 of the first electric motor 20 is fixed, in the direction where the stator 24 of the second electric motor 23 is fixed. .
- the second electric motor 23 which needs to generate a large torque at the time of acceleration, for example, when the automobile 1 starts moving, has a larger radial dimension (compared with the first electric motor 20).
- the hybrid drive unit 7B as a whole has a shorter length in the front-rear direction to improve the mountability on the vehicle body 4. Can be done.
- the first and second brakes Bl, B2 described in the above-described Embodiments 1-2 are not limited to the hydraulic actuators, but may be electric actuators using a ball screw mechanism and an electric motor, or other actuators. May be used. Further, the invention is not limited to the friction engagement element, and may be, for example, a mating type.
- the above-described transmission 22 is not limited to the above-described embodiment, but may be an automatic transmission having two, three, or more stages, or an automatic transmission having a speed increasing stage (O / D). It goes without saying that a transmission may be used, and a continuously variable transmission (CVT) may be used. Further, the output of the transmission 22 is not limited to the output shaft 12, and may be connected to any part of a power transmission system from the output shaft 12 to the drive wheels.
- CVT continuously variable transmission
- the above-described hybrid drive device of the present invention can be applied to automobiles, and is particularly suitably used for FR automobiles.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- General Engineering & Computer Science (AREA)
- Hybrid Electric Vehicles (AREA)
- Arrangement Of Transmissions (AREA)
- Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
- Retarders (AREA)
- Arrangement And Driving Of Transmission Devices (AREA)
- Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
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EP04746669A EP1657094B1 (en) | 2003-06-30 | 2004-06-30 | Hybrid drive device and automobile with device mounted thereon |
US10/536,832 US7393296B2 (en) | 2003-06-30 | 2004-06-30 | Hybrid driving unit and vehicle carrying the same |
JP2005511091A JP4319186B2 (ja) | 2003-06-30 | 2004-06-30 | ハイブリッド駆動装置及びこれを搭載した自動車 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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JP2003-189104 | 2003-06-30 | ||
JP2003189104 | 2003-06-30 |
Publications (1)
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WO2005000619A1 true WO2005000619A1 (ja) | 2005-01-06 |
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PCT/JP2004/009200 WO2005000619A1 (ja) | 2003-06-30 | 2004-06-30 | ハイブリッド駆動装置及びこれを搭載した自動車 |
Country Status (6)
Country | Link |
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US (1) | US7393296B2 (ja) |
EP (1) | EP1657094B1 (ja) |
JP (1) | JP4319186B2 (ja) |
KR (1) | KR100824257B1 (ja) |
CN (1) | CN100366952C (ja) |
WO (1) | WO2005000619A1 (ja) |
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US7766778B2 (en) | 2004-09-14 | 2010-08-03 | Toyota Jidosha Kabushiki Kaisha | Drive device for vehicle |
WO2015046306A1 (ja) * | 2013-09-26 | 2015-04-02 | アイシン・エィ・ダブリュ株式会社 | ハイブリッド駆動装置 |
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DE10248715A1 (de) * | 2002-10-18 | 2004-05-13 | Compact Dynamics Gmbh | Hybridantrieb für ein Kraftfahrzeug |
DE10314234B3 (de) * | 2003-03-29 | 2004-10-28 | Aurator Treuhandgesellschaft Mbh | Vier-Wellen-Leistungsverzweigungsgetriebe |
DE102004002061A1 (de) * | 2004-01-15 | 2005-08-04 | Zf Friedrichshafen Ag | Verfahren zum Steuern und Regeln eines Antriebsstranges eines Hybridfahrzeuges und Antriebsstrang eines Hybridfahrzeugs |
DE102004024086A1 (de) * | 2004-05-14 | 2005-12-08 | Audi Ag | Antriebsvorrichtung für Kraftfahrzeuge |
DE102004042007A1 (de) * | 2004-08-31 | 2006-03-02 | Daimlerchrysler Ag | Leistungsverzweigtes Getriebe für ein Hybridfahrzeug |
JP4059876B2 (ja) * | 2004-10-14 | 2008-03-12 | トヨタ自動車株式会社 | ハイブリッド駆動装置 |
JP4059877B2 (ja) * | 2004-10-14 | 2008-03-12 | トヨタ自動車株式会社 | ハイブリッド駆動装置 |
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Also Published As
Publication number | Publication date |
---|---|
KR20060027309A (ko) | 2006-03-27 |
CN100366952C (zh) | 2008-02-06 |
EP1657094A1 (en) | 2006-05-17 |
JP4319186B2 (ja) | 2009-08-26 |
KR100824257B1 (ko) | 2008-04-24 |
EP1657094B1 (en) | 2011-10-19 |
JPWO2005000619A1 (ja) | 2006-09-28 |
US20060166772A1 (en) | 2006-07-27 |
US7393296B2 (en) | 2008-07-01 |
CN1700998A (zh) | 2005-11-23 |
EP1657094A4 (en) | 2007-03-14 |
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