WO2012111432A1 - 車両用駆動装置 - Google Patents
車両用駆動装置 Download PDFInfo
- Publication number
- WO2012111432A1 WO2012111432A1 PCT/JP2012/052263 JP2012052263W WO2012111432A1 WO 2012111432 A1 WO2012111432 A1 WO 2012111432A1 JP 2012052263 W JP2012052263 W JP 2012052263W WO 2012111432 A1 WO2012111432 A1 WO 2012111432A1
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- Prior art keywords
- oil
- hydraulic
- pressure
- oil chamber
- control valve
- Prior art date
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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
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- B60W20/00—Control systems specially adapted for hybrid vehicles
- B60W20/40—Controlling the engagement or disengagement of prime movers, e.g. for transition between prime movers
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- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
- B60K6/38—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the driveline clutches
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- B—PERFORMING OPERATIONS; TRANSPORTING
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- 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
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- 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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- B60—VEHICLES IN GENERAL
- B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
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- B60L50/10—Electric propulsion with power supplied within the vehicle using propulsion power supplied by engine-driven generators, e.g. generators driven by combustion engines
- B60L50/16—Electric propulsion with power supplied within the vehicle using propulsion power supplied by engine-driven generators, e.g. generators driven by combustion engines with provision for separate direct mechanical propulsion
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- B—PERFORMING OPERATIONS; TRANSPORTING
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- 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
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- F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
- F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
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- F16D25/00—Fluid-actuated clutches
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- F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
- F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
- F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
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- F16H—GEARING
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- F16H—GEARING
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- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/10—System to be controlled
- F16D2500/104—Clutch
- F16D2500/10406—Clutch position
- F16D2500/10412—Transmission line of a vehicle
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/70—Details about the implementation of the control system
- F16D2500/704—Output parameters from the control unit; Target parameters to be controlled
- F16D2500/70402—Actuator parameters
- F16D2500/70406—Pressure
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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
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H2045/002—Combinations of fluid gearings for conveying rotary motion with couplings or clutches comprising a clutch between prime mover and fluid 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
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/021—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type three chamber system, i.e. comprising a separated, closed chamber specially adapted for actuating a lock-up clutch
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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
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
- F16H2045/0226—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers
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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
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
- F16H2045/0284—Multiple disk type lock-up clutch
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/62—Hybrid vehicles
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/64—Electric machine technologies in electromobility
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/70—Energy storage systems for electromobility, e.g. batteries
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/7072—Electromobility specific charging systems or methods for batteries, ultracapacitors, supercapacitors or double-layer capacitors
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- 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
Definitions
- the present invention includes an input member that is drivingly connected to a rotating electrical machine, an output member that is drivingly connected to a wheel, a first engagement device that selectively drives and connects the input member to an internal combustion engine, the input member, and the
- the present invention relates to a vehicle drive device including a fluid coupling provided in a power transmission path connecting an output member.
- the vehicle drive device for a hybrid vehicle described in Patent Literatures 1 and 2 includes a first engagement device that selectively drives and connects an internal combustion engine to a power transmission mechanism.
- the internal combustion engine can be separated from the power transmission mechanism by releasing the engagement device by controlling the hydraulic pressure supplied to the first engagement device so that the vehicle can be driven by the driving force of only the rotating electrical machine.
- a first engagement device capable of selectively drivingly connecting the internal combustion engine and the power transmission system by hydraulic control is provided with the hybrid vehicle.
- Patent Document 1 does not disclose oil supply to the friction member of the first engagement device. For this reason, the technique of patent document 1 cannot respond to supplying and cooling oil to the friction member of a 1st engagement apparatus.
- the technique of Patent Document 2 in order to supply oil to the friction member of the first engagement device, the joint input side member and the joint output side member of the fluid coupling are directly coupled (locked up) within the cover of the fluid coupling.
- the first engagement device is accommodated. More specifically, the body coupling chamber that houses the body portion of the fluid coupling and the friction member of the first engagement device are housed in the cover of the fluid coupling, and the hydraulic pressure of the hydraulic oil in the piston of the first engagement device.
- a differential pressure forming chamber formed so as to apply a hydraulic pressure to the side opposite to the side on which the pressure acts is provided in communication (shared).
- a hydraulic pressure supply system for supplying hydraulic pressure to these is also shared.
- the engagement state of the second engagement device of the fluid coupling is controlled by at least the hydraulic pressure supplied to the main body housing chamber.
- the engagement state of the first engagement device is controlled by the differential pressure between the hydraulic pressure of the hydraulic oil of the first engagement device and the hydraulic pressure supplied to the differential pressure forming chamber.
- each control of the first and second engagement devices has its own aim, and each of the first and second engagement devices is controlled so as to match the aim.
- the main body housing chamber and the differential pressure forming chamber are communicated (shared), during one control of the first and second engagement devices, The hydraulic pressure fluctuations and the operation of one hydraulic supply system affect the other, and the controllability of the other or both may be deteriorated. Further, when both controls are performed at the same time, hydraulic pressure fluctuations occurring in the respective oil chambers and operations of the respective hydraulic pressure supply systems may interfere with each other, and the controllability of both may deteriorate.
- An input member that is drivingly connected to a rotating electrical machine, an output member that is drivingly connected to a wheel, a first engagement device that selectively drives and connects the input member to an internal combustion engine, and the input member according to the present invention.
- a fluid coupling provided in a power transmission path connecting the output member.
- the vehicle drive device includes a first friction member and a first friction member that presses the first friction member.
- the first piston is configured to accommodate the first friction member, and is configured to apply the hydraulic pressure to a side opposite to a side on which the hydraulic pressure for operation is applied in the first piston.
- An oil chamber, and the fluid coupling is drivably coupled to a main body housing chamber that accommodates a main body portion of the fluid coupling.
- the second engagement device that directly connects the joint output side member Comprising a second oil chamber for controlling the oil pressure of the engagement state of,
- a first hydraulic control valve that controls a first hydraulic pressure that is a hydraulic pressure supplied to the first hydraulic chamber; a second hydraulic pressure that is a hydraulic pressure supplied to the second hydraulic chamber; Includes a second hydraulic control valve that is independently controlled.
- the “rotary electric machine” is used as a concept including a motor (electric motor), a generator (generator), and a motor / generator that functions as both a motor and a generator as necessary.
- driving connection refers to a state in which two rotating elements are connected so as to be able to transmit a driving force, and the two rotating elements are connected so as to rotate integrally, or the two This is used as a concept including a state in which two rotating elements are connected so as to be able to transmit a driving force via one or more transmission members.
- Such a transmission member examples include various members that transmit rotation at the same speed or a variable speed, and include, for example, a shaft, a gear mechanism, a belt, a chain, and the like.
- an engagement element that selectively transmits rotation and driving force such as a friction clutch or a meshing clutch, may be included.
- the “fluid coupling” is used as a concept including both a torque converter having a torque amplification function and a normal fluid coupling having no torque amplification function.
- the 1st oil chamber hydraulic pressure supplied to a 1st oil chamber And a second hydraulic control valve that controls the second hydraulic chamber hydraulic pressure supplied to the second hydraulic chamber independently of the first hydraulic chamber hydraulic pressure. That is, the first hydraulic control valve and the hydraulic supply system to the first oil chamber including the oil passage from the first hydraulic control valve to the first oil chamber, the second hydraulic control valve, and the second hydraulic control valve And a hydraulic pressure supply system to the second oil chamber including the oil passage to the second oil chamber.
- first hydraulic supply system and the second hydraulic supply system are provided independently, even during the control of one or both of the first engagement device and the second engagement device, due to mutual interference, Variations in the amount of oil supplied to the first oil chamber can be suppressed, and variations in the cooling performance of the first friction member provided in the first oil chamber can be suppressed.
- the exhaust oil passage for discharging the hydraulic pressure supplied from the first hydraulic control valve to the first oil chamber from the first oil chamber is provided with a throttle portion for reducing the flow rate.
- the throttle part is provided on the discharge port side of the first oil chamber, the first oil chamber located on the upstream side of the throttle part and the supply from the first hydraulic control valve to the first oil chamber It becomes easy to equalize the oil pressure in the oil passage, and the control accuracy of the oil pressure in the first oil chamber can be improved. Therefore, the control accuracy of the engagement state of the first engagement device can be improved. Further, since the throttle portion is provided on the discharge port side of the first oil chamber, the flow rate of the oil flowing through the first oil chamber can be adjusted by adjusting the throttle amount of the throttle portion. Therefore, it becomes easy to appropriately cool the first friction member housed in the first oil chamber.
- the first engagement device includes an urging mechanism that urges the first piston with a predetermined initial engagement load so that the first piston presses the first friction member toward the engagement side.
- the first hydraulic control valve controls the first oil chamber hydraulic pressure so as to generate a hydraulic pressure in the first oil chamber that presses the first piston toward the disengagement side with a load larger than the initial engagement load. It is preferable that the configuration is controlled.
- the urging mechanism that urges the piston with a predetermined initial engagement load is provided so that the piston presses the first friction member toward the engagement side, the first engagement device is released. Even when the rotating electrical machine or the drive circuit of the rotating electrical machine fails and the hydraulic pump cannot be driven by the rotating electrical machine, if the internal combustion engine is started, the first engagement is caused by the pressing force of the first urging mechanism.
- the torque of the internal combustion engine can be transmitted to the hydraulic pump via the device to generate the hydraulic pressure, and the first engagement device can be brought into the engaged state. Therefore, even when the rotating electric machine does not move, the driving force of the internal combustion engine can be transmitted to the wheel side to drive the wheel.
- the first oil chamber hydraulic pressure is generated so that the first oil pressure control valve generates hydraulic pressure in the first oil chamber that presses the piston toward the disengagement side with a load larger than the initial engagement load. Therefore, in a normal state where no trouble has occurred, the first oil chamber hydraulic pressure generated by the first hydraulic control valve can release the engagement of the first engagement device by the pressing force of the urging mechanism. it can. Therefore, when the wheel is driven by the rotating electrical machine (during electric travel), it is possible to suppress the torque of the rotating electrical machine from being transmitted to the internal combustion engine via the first engagement device by the pressing force of the urging mechanism. The deterioration of energy efficiency can be suppressed.
- a first line pressure control valve that controls the output pressure of the hydraulic pump as a first line pressure
- a second line pressure control valve that further reduces the first line pressure and controls it as a second line pressure.
- the first hydraulic control valve receives the supply of the oil of the first line pressure controlled by the first line pressure control valve and supplies the oil of the first oil chamber hydraulic pressure to the first oil chamber.
- the second hydraulic control valve is configured to receive the second line pressure oil controlled by the second line pressure control valve and supply the second oil chamber hydraulic oil to the second oil chamber. This is preferable.
- the first line pressure which is the output pressure of the hydraulic pump, rises quickly after the hydraulic pump is started.
- the second line pressure generated by reducing the first line pressure rises later than the first line pressure after the start of driving of the hydraulic pump. Since the first line pressure, which is the output pressure of the hydraulic pump, is supplied to the first hydraulic control valve as in the above configuration, the first hydraulic control valve is controlled immediately after the hydraulic pump starts driving.
- the first oil chamber hydraulic pressure can be raised and supplied to the first oil chamber. Therefore, immediately after the drive of the hydraulic pump is started, the hydraulic pressure acting on the side opposite to the side on which the hydraulic pressure for actuation in the first piston acts can be generated, and the working accuracy of the first engagement device can be ensured.
- the cooling performance of the first friction member accommodated in the first oil chamber can be ensured. Further, as described above, when the biasing mechanism that presses the first friction member toward the engagement side is provided, the first engagement by the pressing force of the biasing mechanism is promptly performed after the hydraulic pump starts to be driven. The device can be disengaged.
- the second line pressure is controlled by further reducing the first line pressure
- the second line pressure is less susceptible to the pressure pulsation than the first line pressure that is susceptible to the pressure pulsation due to the discharge of the hydraulic pump.
- the pressure is stable. Since the second line pressure generated by further reducing the first line pressure is supplied to the second hydraulic control valve as in the above configuration, the second line pressure that is more stable than the first line pressure is reduced. By using this, a stable second oil chamber hydraulic pressure can be generated. Therefore, the operation accuracy of the second engagement device can be stabilized.
- the second engagement device when the second engagement device is provided with an urging mechanism that presses the second friction member toward the release side, as with the first engagement device, the second engagement device is immediately applied after the hydraulic pump starts driving. Since it is not necessary to release the engagement of the second engagement device by the biasing mechanism, the second engagement device can be stably operated after the start of driving of the hydraulic pump even when the second line pressure is used.
- the second engagement device includes a second friction member and a second piston that presses the second friction member, and the second oil chamber includes the second friction member and the fluid therein.
- the joint input side member and the joint output side member of the joint are accommodated, and formed so that the hydraulic pressure is applied to the side opposite to the side on which the hydraulic pressure for operation is applied in the second piston. It is preferable that
- the control accuracy of the hydraulic pressure acting on the side opposite to the side on which the hydraulic pressure for operation of the second piston of the second engagement device acts is improved.
- the control accuracy of the engagement state of the second engagement device can be improved.
- variation of the cooling performance of the 2nd friction member accommodated in the 2nd oil chamber can be suppressed.
- FIG. 1 is a schematic diagram illustrating a schematic configuration of a drive device 1 according to the present embodiment.
- the drive apparatus 1 schematically includes an internal combustion engine IE and a rotating electrical machine MG as drive force sources, and the drive force of these drive force sources is converted into a power transmission mechanism. Via the wheel W.
- the driving device 1 includes an input shaft I that is drivingly connected to the rotating electrical machine MG, an output shaft O that is drivingly connected to the wheels W, and a first engagement device C1 that selectively drives and connects the input shaft I to the internal combustion engine IE.
- the drive device 1 includes a transmission device TM in a power transmission path between the torque converter TC and the output shaft O.
- the input shaft I corresponds to the “input member” in the present invention
- the output shaft O corresponds to the “output member” in the present invention.
- the first engagement device C ⁇ b> 1 includes a first friction member 101, a first piston 106 that presses the first friction member 101, and a first friction member. 101 is accommodated, and a first oil chamber 102 is formed so that the hydraulic pressure is applied to the back pressure side opposite to the side on which the hydraulic pressure for operation in the first piston 106 is applied. It has.
- the torque converter TC directly connects a pump impeller 41 that is drivingly connected to the input shaft I side and a turbine runner 51 that is drivingly connected to the output shaft O side to a main body housing chamber 137 that houses the main body of the torque converter TC.
- the second oil chamber 112 for controlling the engagement state of the second engagement device C2 to be hydraulically controlled is provided.
- the pump impeller 41 is a “joint input side member” in the present invention
- the turbine runner 51 is a “joint output side member” in the present invention.
- the drive device 1 includes a first hydraulic control valve 104 that controls a first oil chamber oil pressure 103 that is oil pressure supplied to the first oil chamber 102, and a second oil chamber that is oil pressure supplied to the second oil chamber 112. It has a feature in that it includes a second hydraulic control valve 114 that controls the hydraulic pressure 113 independently of the first hydraulic chamber hydraulic pressure 103.
- a first hydraulic control valve 104 that controls a first oil chamber oil pressure 103 that is oil pressure supplied to the first oil chamber 102
- a second oil chamber that is oil pressure supplied to the second oil chamber 112. It has a feature in that it includes a second hydraulic control valve 114 that controls the hydraulic pressure 113 independently of the first hydraulic chamber hydraulic pressure 103.
- the driving device 1 includes an internal combustion engine IE and a rotating electrical machine MG as driving force sources for driving the vehicle, and the internal combustion engine IE and the rotating electrical machine MG are connected in series.
- the drive device 1 is for a hybrid vehicle.
- the drive device 1 includes a torque converter TC and a transmission device TM as a power transmission mechanism.
- the torque converter TC and the transmission device TM allow the internal combustion engine IE and the rotating electrical machine MG as driving force sources. And the torque is converted and transmitted to the output shaft O.
- the internal combustion engine IE, the rotating electrical machine MG, the torque converter TC, and the transmission device TM are arranged coaxially and from the internal combustion engine IE side to the output shaft O along the axial direction.
- the rotating electrical machine MG, the torque converter TC, and the transmission TM are arranged in this order.
- the internal combustion engine connecting shaft EC, the input shaft I, the intermediate shaft M, and the output shaft O are also arranged coaxially therewith.
- the axis of each member of the drive device 1 arranged on the same axis is set as a device axis X1. Further, in the description of the embodiment, when the axial direction, the radial direction, and the circumferential direction are simply referred to, the direction based on the device axis X1 is assumed.
- the internal combustion engine IE is a prime mover that outputs power by combustion of fuel, and for example, various known internal combustion engines such as a gasoline engine and a diesel engine can be used.
- an output rotation shaft such as a crankshaft of the internal combustion engine IE is drivingly connected to the input shaft I via the internal combustion engine connection shaft EC and the first engagement device C1.
- the first engagement device C1 selectively connects the input shaft I to the internal combustion engine IE.
- the first engagement device C1 is a friction engagement element that is engaged or released by the hydraulic pressure for operation supplied from the first servo hydraulic control valve 109 (see FIG. 2).
- a friction engagement element for example, a wet multi-plate clutch or a wet multi-plate brake is preferably used.
- the output rotation shaft of the internal combustion engine IE is drivingly connected integrally with the internal combustion engine connecting shaft EC, or driven and connected via another member such as a damper.
- the rotating electrical machine MG includes a stator St fixed to the case 3 and a rotor Ro that is rotatably supported on the radially inner side of the stator St.
- the rotor Ro of the rotating electrical machine MG is drivingly connected so as to rotate integrally with the input shaft I. That is, in the present embodiment, both the internal combustion engine IE and the rotating electrical machine MG are drivingly connected to the input shaft I.
- the rotating electrical machine MG is electrically connected to a battery (not shown) as a power storage device.
- the rotating electrical machine MG can perform a function as a motor (electric motor) that generates power upon receiving power supply and a function as a generator (generator) that generates power upon receiving power supply. It is possible.
- the rotating electrical machine MG is powered by receiving power supplied from the battery, or stores in the battery the power generated by the rotational driving force transmitted from the internal combustion engine IE or the wheels.
- the battery is an example of a power storage device, and another power storage device such as a capacitor may be used, or a plurality of types of power storage devices may be used in combination.
- a torque converter TC is provided in the power transmission path connecting the input shaft I and the output shaft O.
- the torque converter TC is a device that transmits the rotational driving force of the internal combustion engine IE and the rotating electrical machine MG as a driving force source to the output shaft O side.
- the torque converter TC includes a pump impeller 41 as a joint input side member drivingly connected to the rotating electrical machine MG (input shaft I) and a turbine as a joint output side member drivingly connected to the transmission TM (intermediate shaft M).
- a runner 51 and a stator 56 provided between them and provided with a one-way clutch 57 are provided.
- the torque converter TC transmits driving force between the driving-side pump impeller 41 and the driven-side turbine runner 51 via oil filled therein.
- the torque converter TC includes a second engagement device C2 as a friction engagement element for lockup.
- the second engagement device C2 is configured to rotate the pump impeller 41 and the turbine runner 51 integrally in order to eliminate the rotational speed difference (slip) between the pump impeller 41 and the turbine runner 51 and increase the transmission efficiency.
- the clutch to be connected. Therefore, when the second engagement device C2 is engaged, the torque converter TC directly transmits the driving force of the driving force source without using the internal oil (fluid) to the transmission device TM (intermediate shaft M). To communicate.
- the second engagement device C2 is engaged or released by the hydraulic pressure for operation supplied from the second servo hydraulic control valve 119.
- the drive device 1 includes a hydraulic pump OP that is drivingly connected to the pump impeller 41 side of the torque converter TC.
- the hydraulic pump OP is driven by the rotational driving force transmitted from the driving force source, sucks the oil stored in the oil storage unit OT to generate hydraulic pressure, and supplies the hydraulic pressure to the hydraulic control device (see FIG. 2).
- the transmission TM is drivingly connected to the intermediate shaft M as the output shaft of the torque converter TC.
- the transmission apparatus TM is a stepped automatic transmission apparatus having a plurality of shift stages having different speed ratios.
- the transmission apparatus TM includes a gear mechanism such as a planetary gear mechanism and a plurality of friction engagement elements in order to form the plurality of shift stages.
- the plurality of friction engagement elements are engagement elements such as clutches and brakes each having a friction material.
- Each of the plurality of friction engagement elements is supplied with oil regulated by a hydraulic control device for the transmission apparatus TM, and is engaged or released.
- a friction engagement element for example, a wet multi-plate clutch or a wet multi-plate brake is preferably used.
- the torque transmitted from the transmission device TM to the output shaft O is distributed and transmitted to the two left and right wheels W via the output differential gear mechanism DF.
- the first engagement device C1 includes the first hydraulic servo mechanism 100 including the first piston 106, the first friction member 101, the first piston 106 that presses the first friction member 101, and the first The first oil chamber is formed so that one friction member 101 is accommodated and the hydraulic pressure is supplied to the back pressure side opposite to the side on which the hydraulic pressure for operation of the first piston 106 acts. 102.
- the torque converter TC directly connects a pump impeller 41 that is drivingly connected to the input shaft I side and a turbine runner 51 that is drivingly connected to the output shaft O side to a main body housing chamber 137 that houses the main body of the torque converter TC.
- the second oil chamber 112 for controlling the engagement state of the second engagement device C2 to be hydraulically controlled is provided.
- the torque converter TC is configured to include a second engagement device C2 as shown in FIG. 2, and the second engagement device C2 includes a second hydraulic servo including a second piston 116.
- a mechanism 110, a second friction member 111, and a second piston 116 that presses the second friction member 111 are provided.
- the second oil chamber 112 accommodates the second friction member 111 of the second engagement device C2, the pump impeller 41 of the torque converter TC, and the turbine runner 51, and is supplied with hydraulic pressure to be in the second piston 116.
- the hydraulic pressure is applied to the back pressure side opposite to the side on which the hydraulic pressure for operation is applied.
- the driving device 1 includes a first servo hydraulic control valve 109 and a second servo hydraulic control valve 119.
- the driving device 1 includes a first hydraulic control valve 104 that controls a first oil chamber oil pressure 103 that is oil pressure supplied to the first oil chamber 102, and a second oil chamber that is oil pressure supplied to the second oil chamber 112. And a second hydraulic control valve 114 that controls the hydraulic pressure 113 independently of the first oil chamber hydraulic pressure 103.
- the side on which the hydraulic pressure for operation in the first piston 106 acts refers to the side of the first servo oil chamber 108 in the first piston 106 and is opposite to the side on which the hydraulic pressure for actuation in the first piston 106 acts.
- the side (back pressure side) refers to the first oil chamber 102 side of the first piston 106.
- the hydraulic pressure acting on the side (back pressure side) opposite to the side on which the operating hydraulic pressure acts on the first piston 106 is the back pressure of the first piston 106 or the first hydraulic servo mechanism 100. This is called back pressure.
- the first hydraulic servo mechanism 100 includes a first piston 106, a first cylinder 105, and a first servo oil chamber 108 surrounded by the first cylinder 105 and the first piston 106.
- the side on which the hydraulic pressure for operation in the second piston 116 acts refers to the second servo oil chamber 118 side in the second piston 116 and is opposite to the side on which the hydraulic pressure for actuation in the second piston 116 acts.
- the side (back pressure side) refers to the second oil chamber 112 side of the second piston 116.
- the hydraulic pressure acting on the opposite side (back pressure side) of the second piston 116 to the working hydraulic pressure is referred to as the back pressure of the second piston 116 or the second hydraulic servo mechanism 110. This is called back pressure.
- the second hydraulic servo mechanism 110 includes a second piston 116, a second cylinder 115, and a second servo oil chamber 118 surrounded by the second cylinder 115 and the second piston 116.
- the main body housing chamber 137 is formed to house at least the pump impeller 41, the turbine runner 51, and the stator 56 as the main body of the torque converter TC.
- the second oil chamber 112 is integrally formed in the cover member of the torque converter TC so as to communicate with the main body housing chamber 137.
- the main body housing chamber 137 and the second oil chamber 112 are collectively referred to as a second oil chamber 112.
- the hybrid vehicle drive device 1 includes a first engagement device C1 that selectively drives and connects the internal combustion engine IE to the power transmission mechanism.
- the first engagement device C1 When the vehicle is driven by the driving force of only the rotating electrical machine MG, the first engagement device C1 is released by controlling the hydraulic pressure supplied to the first engagement device C1, and power is transmitted to the internal combustion engine IE. It is configured to be separable from the mechanism.
- the first engagement device C1 is engaged by controlling the hydraulic pressure supplied to the first engagement device C1, so that the internal combustion engine IE is
- the power transmission mechanism is configured to be drivingly connected.
- a torque shock may be generated and transmitted to the wheels W.
- the second engagement device C2 of the torque converter TC is engaged and the pump impeller 41 and the turbine runner 51 are directly connected, the first engagement device C1 is engaged.
- the second engagement device C2 is controlled to the released state or the sliding engagement state. Thereby, it can suppress that the torque shock which arose in the 1st engagement apparatus C1 is transmitted to the wheel W side from the torque converter TC.
- torque shock may occur, and similarly, the second engagement device C2 is controlled to be in a release state or a sliding engagement state.
- the hydraulic pressure supplied to the first engagement device C1 when the hydraulic pressure supplied to the first engagement device C1 is controlled, the hydraulic pressure supplied to the second engagement device C2 may be controlled at the same time. In this case, in order to suppress the fluctuation of the torque transmitted to the wheel W, it becomes a problem to improve the control accuracy of the hydraulic pressure supplied to the first engagement device C1 and the second engagement device C2.
- the first oil chamber 102 that generates the back pressure of the first hydraulic servo mechanism 100 (first piston 106) of the first engagement device C1, and the second engagement device C2 of the first engagement.
- a second oil chamber 112 that generates a back pressure of the two hydraulic servo mechanism 110 (second piston 116) is provided independently of each other. Therefore, even when the first hydraulic servo mechanism 100 of the first engagement device C1 and the second hydraulic servo mechanism 110 of the second engagement device C2 are operated at the same time, the operation of the first hydraulic servo mechanism 100 is performed.
- the first hydraulic control valve 104 that controls the first oil chamber hydraulic pressure 103 supplied to the first oil chamber 102 and the second oil chamber hydraulic pressure supplied to the second oil chamber 112 are used.
- a second hydraulic control valve 114 for controlling 113 independently of the first oil chamber hydraulic pressure 103. That is, a first hydraulic control valve 104, a hydraulic supply system (first hydraulic supply system) to the first oil chamber 102 including an oil passage from the first hydraulic control valve 104 to the first oil chamber 102, and a second hydraulic pressure
- a control valve 114 and a hydraulic supply system (second hydraulic supply system) to the second oil chamber 112 including an oil passage from the second hydraulic control valve 114 to the second oil chamber 112 are provided independently. .
- the first hydraulic servo mechanism 100 of the first engagement device C1 and the second hydraulic servo mechanism 110 of the second engagement device C2 are operated at the same time, the first oil chamber 102 or the second oil chamber 102 It is possible to suppress the oil pressure fluctuation in the oil chamber 112 and the operation of the first hydraulic pressure supply system or the second hydraulic pressure supply system from interfering with each other. Therefore, the control accuracy of the back pressure of the first hydraulic servo mechanism 100 and the back pressure of the second hydraulic servo mechanism 110 can be improved, and the engagement state of the first engagement device C1 and the second engagement device C2 can be improved. Control accuracy can be improved. And when engaging or releasing 1st engagement apparatus C1, the fluctuation
- the drive device 1 is a throttle unit that restricts the flow rate to a discharge oil passage for discharging the hydraulic pressure supplied from the first hydraulic control valve 104 to the first oil chamber 102 from the first oil chamber 102.
- a first diaphragm 120 As a first diaphragm 120.
- the first diaphragm 120 is the “diaphragm” in the present invention.
- the first throttle portion 120 is provided on the discharge port side of the first oil chamber 102, the first oil chamber 102 and the first hydraulic control valve 104 located on the upstream side of the first throttle portion 120. It becomes easy to equalize the oil pressure in the supply oil passage to the first oil chamber 102. Therefore, the control accuracy of the hydraulic pressure in the first oil chamber 102 can be improved, and the control accuracy of the engagement state of the first engagement device C1 can be improved. Further, since the first throttle portion 120 is provided on the discharge port side of the first oil chamber 102, the flow rate of the oil flowing in the first oil chamber 102 can be adjusted by adjusting the throttle amount of the first throttle portion 120. Can be adjusted. Therefore, it becomes easy to appropriately cool the first friction member 101 accommodated in the first oil chamber 102.
- a first urging mechanism 107 that urges the first piston 106 with a predetermined initial engagement load is provided so that the first piston 106 presses the first friction member 101 toward the engagement side. Yes. Then, the first hydraulic control valve 104 generates the first oil chamber hydraulic pressure so that the first oil chamber 102 generates a back pressure that presses the first piston 106 toward the disengagement side with a load larger than the initial engagement load. 103 is controlled.
- the first biasing mechanism 107 is the “biasing mechanism” in the present invention.
- the first biasing mechanism 107 that biases the first piston 106 with a predetermined initial engagement load is provided so that the first piston 106 presses the first friction member 101 toward the engagement side.
- the first hydraulic control valve 104 generates hydraulic pressure in the first oil chamber 102 that presses the first piston 106 toward the disengagement side with a load larger than the initial engagement load.
- the first oil chamber oil pressure 103 is controlled so that, in a normal state where no trouble occurs, the first oil chamber oil pressure 103 generated by the first oil pressure control valve 104 is used to push the first urging mechanism 107.
- the engagement of the first engagement device C1 due to the pressure can be released.
- the torque of the rotating electrical machine MG is transmitted to the internal combustion engine IE through the first engagement device C1 by the pressing force of the first urging mechanism 107. This can be suppressed, and deterioration of energy efficiency during electric travel can be suppressed.
- the drive device 1 further reduces the first line pressure 131 by controlling the output pressure of the hydraulic pump OP as the first line pressure 131, and the first line pressure 131.
- a second line pressure control valve 140 that is controlled as 141.
- the first hydraulic control valve 104 receives the supply of oil at the first line pressure 131 controlled by the first line pressure control valve 130 and supplies the oil in the first oil chamber hydraulic pressure 103 to the first oil chamber 102.
- the second hydraulic control valve 114 receives the supply of the oil of the second line pressure 141 controlled by the second line pressure control valve 140 and supplies the oil of the second oil chamber hydraulic pressure 113 to the second oil chamber 112.
- the first line pressure 131 which is the output pressure of the hydraulic pump OP, rises quickly after the drive of the hydraulic pump OP is started, for example, in order to start the driving device 1.
- the second line pressure 141 generated by reducing the first line pressure 131 rises later than the first line pressure 131 after the drive of the hydraulic pump OP is started.
- the first line pressure 131 that is the output pressure of the hydraulic pump OP is supplied to the first hydraulic control valve 104.
- the first oil chamber hydraulic pressure 103 controlled by the hydraulic control valve 104 rises and can be supplied into the first oil chamber 102.
- the back pressure of the first hydraulic servo mechanism 100 (first piston 106) can be generated quickly, and the operation accuracy of the first engagement device C1 can be ensured.
- the engagement of the first engagement device C1 due to the pressing force of the one biasing mechanism 107 can be released. Further, the cooling performance of the first friction member 101 accommodated in the first oil chamber 102 can be ensured.
- the second line pressure 141 is a hydraulic pressure obtained by further reducing the first line pressure 131
- the second line pressure 141 is less affected by the pressure pulsation than the first line pressure 131 that is easily affected by the pressure pulsation caused by the discharge of the hydraulic pump OP. It is difficult to receive and the pressure is stable.
- the second line pressure 141 generated by further reducing the first line pressure 131 is supplied to the second hydraulic control valve 114, the second line pressure 141 is more stable than the first line pressure 131.
- a stable second oil chamber oil pressure 113 can be generated using the second line pressure 141. Therefore, the operation accuracy of the second engagement device C2 can be stabilized.
- the hydraulic pump OP is driven as in the first engagement device C1. Since it is not necessary to release the engagement of the second engagement device C2 by the biasing mechanism after the start, even if the second line pressure 141 is used, the second engagement device C2 is stabilized after the drive of the hydraulic pump OP is started. Can be activated.
- the first line pressure control valve 130 that controls (regulates) the output pressure of the hydraulic pump OP as the first line pressure 131 is a pressure regulating valve that includes a spool 130p and a spring 130s that biases the spool 130p.
- a pressure regulator valve which is a kind of the above, is used. That is, the first line pressure control valve 130 has a pressing force for pressing the spool 130p in the first direction (downward in FIG. 2) by the reference pressure 136 and the spring 130s supplied to the reference pressure chamber 130a, and the feedback pressure chamber 130b.
- One line pressure 131 is adjusted. Specifically, when the pressing force in the second direction by the first line pressure 131 exceeds the pressing force in the first direction by the reference pressure 136 and the spring 130s, the spool 130p moves to the second direction. The amount of communication opening between the pressure regulating port 130c to which the first line pressure 131 is supplied and the discharge port 130d increases, and the amount of oil discharged from the hydraulic pump OP increases from the discharge port 130d. The first line pressure 131 decreases.
- the spool 130p moves to the first direction.
- the communication opening amount between the pressure adjusting port 130c and the discharge port 130d is reduced, the drain amount from the discharge port 130d is decreased, and the first line pressure 131 is increased. Therefore, the first line pressure control valve 130 balances the pressing force in the second direction by the first line pressure 131 with the pressing force in the first direction by the reference pressure 136 and the spring 130s.
- the first line pressure 131 is adjusted in a feedback manner by moving the spool 130p to increase or decrease the communication opening amount to the discharge port 130d.
- the oil of the first line pressure 131 is sent to the first hydraulic control valve 104, the first servo hydraulic control valve 109, and the like that control the hydraulic pressure supplied to the first engagement device C1. Further, the oil drained from the discharge port 130d is sent to the oil reservoir OT or the suction port of the hydraulic pump OP.
- the reference pressure 136 supplied to the reference pressure chamber 130a is controlled (regulated) by the reference pressure control valve 135.
- a linear solenoid valve that is a hydraulic control valve having functions of a solenoid and a pressure regulating valve (pressure reducing valve) is used as the reference pressure control valve 135.
- the reference pressure control valve 135 generates a reference pressure 136 by controlling the pressure reduction amount of the hydraulic pressure supplied from the hydraulic pump OP in accordance with the driving force of the solenoid.
- the reference pressure 136 controlled (regulated) by the reference pressure control valve 135 is also supplied to the second line pressure control valve 140.
- a pressure regulator valve which is a kind of pressure regulating valve including a spool 140p and a spring 140s for urging the spool 140p is used. That is, like the first line pressure control valve 130, the second line pressure control valve 140 moves the spool 140p in the second direction (upward in FIG. 2) by the reference pressure 136 and the spring 140s supplied to the reference pressure chamber 140a.
- the first line pressure control valve 130 is a balance between the pressing force to be pressed and the pressing force to press the spool 140p in the first direction (downward in FIG. 2) by the second line pressure 141 supplied to the feedback pressure chamber 140b.
- the first line pressure 131 is further reduced to adjust the second line pressure 141.
- the oil of the second line pressure 141 is sent to the second hydraulic control valve 114, the second servo hydraulic control valve 119, etc. that control the hydraulic pressure supplied to the second engagement device C2.
- the oil drained from the discharge port 140d is sent to the oil reservoir OT or the suction port of the hydraulic pump OP.
- the first line pressure 131 controlled (regulated) by the first line pressure control valve 130 is supplied to the first hydraulic control valve 104.
- the first hydraulic control valve 104 is composed of a spool 104p and a spring 104s that urges the spool 104p, etc., and simultaneously opens and closes the oil passage from the original pressure and opens and closes the oil passage to the drain.
- the pressure regulating valve pressure reducing valve
- the pressure regulating valve pressure reducing valve
- the spool 104p moves to the first direction side.
- the communication opening amount between the output port 104e that outputs the first oil chamber hydraulic pressure 103 and the discharge port 104d increases, and the communication opening amount between the output port 104e and the input port 104i decreases.
- the amount of oil drained from the discharge port 104d from the first oil chamber oil pressure 103 increases, and the amount of oil in the first line pressure 131 supplied from the input port 104i to the output port 104e decreases.
- the changing speed of the one oil chamber oil pressure 103 changes in the decreasing direction of the first oil chamber oil pressure 103.
- the spool 130p moves to the second direction and outputs.
- the communication opening amount between the port 104e and the discharge port 104d decreases, and the communication opening amount between the output port 104e and the input port 104i increases.
- the amount of oil drained from the discharge port 104d by the oil in the first oil chamber hydraulic pressure 103 decreases, and the amount of oil in the first line pressure 131 supplied from the input port 104i to the output port 104e increases.
- the changing speed of the one oil chamber oil pressure 103 changes in the increasing direction of the first oil chamber oil pressure 103.
- the spool 104p moves so that the pressing force in the first direction by the first oil chamber hydraulic pressure 103 and the pressing force in the second direction by the spring 104s are balanced. Then, the first oil chamber hydraulic pressure 103 is adjusted in a feedback manner by increasing or decreasing the communication opening amount to the discharge port 104d and the communication opening amount to the input port 104i. Then, the oil in the first oil chamber hydraulic pressure 103 adjusted by the first hydraulic control valve 104 is sent to the first oil chamber 102 of the first engagement device C1. Further, the oil drained from the discharge port 104d is sent to the oil reservoir OT or the suction port of the hydraulic pump OP. Note that, as the first hydraulic control valve 104, a pressure regulating valve (pressure reducing valve) of a type that only opens and closes the oil passage to the drain, like the second hydraulic control valve 114, may be used.
- a pressure regulating valve pressure reducing valve
- the first hydraulic control valve 104 generates a back pressure that presses the first piston 106 toward the disengagement side with a load larger than the initial engagement load by the first urging mechanism 107.
- the first oil chamber hydraulic pressure 103 is controlled so as to be generated at the same time.
- the oil pressure in the first oil chamber 102 varies with respect to the first oil chamber oil pressure 103 controlled by the first oil pressure control valve 104 due to various fluctuation factors.
- the fluctuation factors include the pipeline resistance of the oil passage from the first hydraulic control valve 104 to the first oil chamber 102, the static factors such as the oil temperature, the line pressure, and the rotation speed of the member, the oil temperature, and the line pressure.
- the first hydraulic control valve 104 has the first oil chamber hydraulic pressure 103 with a load larger than the initial engagement load by the first biasing mechanism 107.
- the first oil chamber hydraulic pressure 103 is controlled so that a back pressure is generated in the first oil chamber 102 to press the 106 toward the disengagement side.
- the first hydraulic control valve 104 is configured to control the first oil chamber hydraulic pressure 103 so as to be a predetermined hydraulic pressure in consideration of the maximum hydraulic pressure fluctuation range due to these fluctuation factors.
- the first hydraulic chamber hydraulic pressure 103 is controlled by the design of the load of the spring 104 s of the first hydraulic control valve 104 or the sectional area of the spool p of the feedback pressure chamber 104 b. It has been adjusted to meet the conditions.
- the oil in the first oil chamber hydraulic pressure 103 adjusted by the first hydraulic control valve 104 is supplied to the first oil chamber 102.
- the first oil chamber 102 is an oil-tight oil chamber that generates the back pressure of the first hydraulic servo mechanism 100 and houses the first friction member 101 of the first engagement device C1.
- the first hydraulic servo mechanism 100 includes a first cylinder 105, a first piston 106, and a first servo oil chamber 108 surrounded by the first cylinder 105 and the first piston 106.
- the back surface of the first piston 106 is the wall surface of the first oil chamber 102, and the first oil chamber oil pressure 103 is the back pressure of the first piston 106.
- the oil supplied to the first supply port 122 of the first oil chamber 102 flows through a predetermined path (circulation path) in the first oil chamber 102 and circulates. 102 is configured to be discharged from the first discharge port 123.
- the circulation path of the first oil chamber 102 is configured such that oil flows along the back surface of the first piston 106 and the first friction member 101.
- the oil supplied to the first oil chamber 102 circulates in the first oil chamber 102 to generate a back pressure of the first piston 106 and cool the first friction member 101.
- the oil that circulates in the first oil chamber 102 and is discharged from the first discharge port 123 of the first oil chamber 102 passes through the first throttle portion 120 to the suction port of the oil reservoir OT or the hydraulic pump OP. Sent.
- the second line pressure 141 controlled (regulated) by the second line pressure control valve 140 is supplied to the second hydraulic control valve 114 via the second restrictor 125.
- the second throttle portion 125 regulates the amount of oil of the second line pressure 141 supplied to the second oil chamber oil pressure 113 side.
- the second oil pressure control valve 114 adjusts the oil drain amount of the supplied second line pressure 141 to adjust the second oil chamber oil pressure 113.
- a pressure regulating valve pressure reducing valve
- the second hydraulic control valve 114 causes the spool 114p to be first driven by the pressing force pressing the spool 114p in the second direction (upward in FIG. 2) by the spring 114s and the second oil chamber hydraulic pressure 113 supplied to the input port 114a.
- the second line pressure 141 is further reduced to adjust the second oil chamber oil pressure 113 by adjusting the oil drain amount based on the balance with the pressing force pressing in one direction (downward in FIG. 2).
- the spool 114p moves to the first direction side.
- the communication opening amount between the input port 114a to which the oil in the second oil chamber oil pressure 113 is supplied and the discharge port 114b increases, and the amount of oil in which the oil in the second oil chamber oil pressure 113 is drained from the discharge port 114b increases.
- the changing speed of the second oil chamber oil pressure 113 changes in the decreasing direction of the second oil chamber oil pressure 113.
- the second hydraulic control valve 114 moves the spool 114p so that the pressing force in the first direction by the second oil chamber hydraulic pressure 113 and the pressing force in the second direction by the spring 114s are balanced. Then, the second oil chamber hydraulic pressure 113 is regulated in a feedback manner by increasing or decreasing the communication opening amount to the discharge port 114b. Then, the oil in the second oil chamber hydraulic pressure 113 adjusted by the second hydraulic control valve 114 is sent to the second oil chamber 112 of the second engagement device C2. Further, the oil drained from the discharge port 114b is sent to the oil reservoir OT or the suction port of the hydraulic pump OP.
- a pressure regulating valve pressure reducing valve of the type that simultaneously opens and closes the oil passage from the original pressure and opens and closes the oil passage to the drain is used as in the first hydraulic control valve 104. You may be made to do.
- the second oil chamber 112 is an oil-tight oil chamber that generates the back pressure of the second hydraulic servo mechanism 110.
- the second oil chamber 112 houses the second friction member 111 of the second engagement device C2, the pump impeller 41 of the torque converter TC, and the turbine runner 51.
- the second hydraulic servo mechanism 110 includes a second cylinder 115, a second piston 116, and a second servo oil chamber 118 surrounded by the second cylinder 115 and the second piston 116.
- the back surface of the second piston 116 is the wall surface of the second oil chamber 112, and the second oil chamber oil pressure 113 is the back pressure of the second piston 116.
- the oil supplied to the second supply port 127 of the second oil chamber 112 circulates in the second oil chamber 112 through a predetermined path (circulation path) in the second oil chamber 112, and the second oil chamber 112 112 is discharged from the second discharge port 128.
- the circulation path of the second oil chamber 112 is configured such that oil flows along the back surface of the second piston 116, the second friction member 111, the pump impeller 41, and the turbine runner 51.
- the oil supplied to the second oil chamber 112 circulates in the second oil chamber 112, generates a back pressure of the second piston 116, cools the second friction member 111, and performs the pump impeller 41 and the turbine. Supplied as operating oil for the runner 51.
- the oil that circulates in the second oil chamber 112 and is discharged from the second discharge port 128 of the second oil chamber 112 is sent to the oil reservoir OT or the suction port of the hydraulic pump OP.
- the first line pressure 131 controlled (regulated) by the first line pressure control valve 130 is supplied to the first servo hydraulic control valve 109.
- the first servo hydraulic control valve 109 a linear solenoid valve that is a hydraulic control valve having the functions of a solenoid and a pressure regulating valve (pressure reducing valve) is used.
- the first line pressure control valve 130 generates a first servo hydraulic pressure 121 by controlling the pressure reduction amount of the supplied first line pressure 131 according to the driving force of the solenoid.
- the first servo hydraulic pressure control valve 109 is not shown, but includes a pressing force that presses the spool by the driving force of a spring and a solenoid, and a first servo hydraulic pressure 121 supplied to the feedback pressure chamber 109b.
- the oil supply amount of the first line pressure 131 supplied from the input port 109i and the oil drain amount of the first servo hydraulic pressure 121 discharged from the discharge port 109d are adjusted by the balance with the pressing force for pressing the spool.
- the first servo pressure 121 is regulated by further reducing the first line pressure 131.
- a duty solenoid valve and a pressure regulating valve (pressure reducing valve) in which a solenoid function and a pressure regulating valve (pressure reducing valve) function are separated may be used.
- the hydraulic pressure supplied to the first oil chamber 102 and the first servo oil chamber 108 of the first engagement device C1 is regulated by reducing the first line pressure 131, and is described above.
- the first oil chamber hydraulic pressure 103 and the first servo hydraulic pressure 121 can be quickly started up after the driving of the hydraulic pump OP is started. Therefore, it is possible to quickly generate the back pressure of the first hydraulic servo mechanism 100 and to control the hydraulic pressure supplied to the first servo oil chamber 108 after the start of driving of the hydraulic pump OP.
- the operation accuracy of the combined device C1 can be ensured.
- the first hydraulic servo is immediately activated after the drive of the hydraulic pump OP is started.
- the back pressure of the mechanism 100 can be raised to disengage the first engagement device C1 by the first biasing mechanism 107.
- Second Servo Hydraulic Control Valve the second line pressure 141 controlled (regulated) by the second line pressure control valve 140 is supplied to the second servo hydraulic control valve 119.
- the second servo hydraulic control valve 119 a linear solenoid valve that is a hydraulic control valve having the functions of a solenoid and a pressure regulating valve (pressure reducing valve) is used as in the first servo hydraulic control valve 109.
- the second servo oil pressure control valve 119 generates a second servo oil pressure 126 by controlling the pressure reduction amount of the supplied second line pressure 141 according to the driving force of the solenoid.
- the second servo hydraulic control valve 119 is not shown in the figure, but by the pressing force that presses the spool by the driving force of the spring and solenoid, and the second servo hydraulic pressure 126 supplied to the feedback pressure chamber 119b.
- the oil supply amount of the second line pressure 141 supplied from the input port 119i and the oil drain amount of the second servo oil pressure 126 discharged from the discharge port 119d are adjusted by the balance with the pressing force for pressing the spool.
- the second servo pressure 126 is regulated by further reducing the second line pressure 141.
- a duty solenoid valve and a pressure regulating valve (pressure reducing valve) in which a solenoid function and a pressure regulating valve (pressure reducing valve) function are separated may be used.
- the hydraulic pressure supplied to the second oil chamber 112 and the second servo oil chamber 118 of the second engagement device C2 is regulated by reducing the second line pressure 141, as described above.
- the second oil chamber oil pressure 113 and the second servo oil pressure 126 can be generated using the second line pressure 141 that is more stable than the first line pressure 131. Accordingly, the back pressure of the second hydraulic servo mechanism 110 can be stably generated, and the hydraulic pressure supplied to the second servo oil chamber 118 can be controlled stably, and the operating accuracy of the first engagement device C1 can be controlled. Can be secured stably.
- the hydraulic pump OP is driven as in the first engagement device C1. Since it is not necessary to release the engagement of the second engagement device C2 by the biasing mechanism after the start, even if the second line pressure 141 is used, the second engagement device C2 is stabilized after the drive of the hydraulic pump OP is started. Can be activated.
- FIG. 3 is a partially enlarged view of the cross-sectional view of FIG.
- the case 3 schematically includes a cylindrical peripheral wall 4 and an end support wall 5 provided on the left side (internal combustion engine IE side) of the rotating electrical machine MG in FIG. 3 in the axial direction.
- the rotating electrical machine MG, the first engagement device C1, and the torque converter TC are accommodated in the space between the end support wall 5 and the intermediate partition wall 6 in the case 3.
- the transmission TM is accommodated in the space on the right side in FIG.
- An internal combustion engine IE is provided on the left side in FIG. 3 with respect to the end support wall 5.
- the end support wall 5 has a shape extending at least in the radial direction, and here is a substantially flat disk-shaped wall portion extending in the radial direction and the circumferential direction.
- a cylindrical projecting portion 11 that projects in the axial direction toward the torque converter TC is provided at the radial center of the end support wall 5.
- the cylindrical protrusion 11 is a cylindrical boss protruding from the radially inner end of the end support wall 5 toward the torque converter TC.
- a through hole penetrating in the axial direction is formed in the central portion in the radial direction of the cylindrical protruding portion 11, and the internal combustion engine connecting shaft EC is inserted through the through hole.
- a third bearing 73 is disposed between the inner peripheral surface of the cylindrical protrusion 11 and the internal combustion engine connecting shaft EC.
- the internal combustion engine connecting shaft EC is supported by the third bearing 73 so as to be rotatable with respect to the case 3.
- a needle bearing is used as the third bearing 73.
- the space between the inner peripheral surface of the cylindrical projecting portion 11 and the internal combustion engine connecting shaft EC is closed in an oil-tight state by an oil seal 68 on the internal combustion engine IE side.
- the cylindrical protruding portion 11 is formed with a plurality of oil passages. Specifically, as shown in FIG. 3 and FIG. 4, the second oil passage that feeds the oil regulated by the first hydraulic control valve 104 to the first oil chamber 102 is provided in the cylindrical protrusion 11. L2 and a third oil passage L3 for sending the oil discharged from the first oil chamber 102 to the oil reservoir OT or the suction port of the hydraulic pump OP are formed.
- the cylinder projecting portion 11 is supplied with oil regulated by the first servo hydraulic control valve 109 (see FIG. 2) to the first servo oil chamber 108 and also with the first servo oil.
- a first oil passage is formed through which oil discharged from the chamber 108 is sent to the first servo hydraulic control valve 109.
- the intermediate partition wall 6 has a shape extending at least in the radial direction, and is a substantially flat disk-shaped wall portion extending in the radial direction and the circumferential direction here. Moreover, in this embodiment, the intermediate partition 6 is comprised as a member different from the surrounding wall 4, and is fastened and fixed to the level
- the intermediate partition wall 6 is provided with a hydraulic pump OP.
- the hydraulic pump cover 7 is attached to the surface of the intermediate partition wall 6 on the torque converter TC side. A hydraulic pump chamber that houses the hydraulic pump rotor is formed between the intermediate partition wall 6 and the hydraulic pump cover 7.
- the hydraulic pump OP is constituted by the hydraulic pump rotor and the hydraulic pump chamber.
- the hydraulic pump cover 7 is fastened and fixed to the intermediate partition wall 6 by a fastening member such as a bolt while being in contact with the intermediate partition wall 6 from the torque converter TC side.
- a through hole penetrating in the axial direction is formed at the radial center of the intermediate partition wall 6 and the hydraulic pump cover 7, and the intermediate shaft M is inserted through the through hole.
- the hydraulic pump drive shaft 47 and the stator support shaft 58 are also inserted through the through hole.
- the hydraulic pump drive shaft 47 is a cylindrical shaft portion that rotates integrally with the cover portion 42 of the torque converter TC.
- the hydraulic pump drive shaft 47 is disposed radially outside the intermediate shaft M and is drivingly connected to the hydraulic pump rotor.
- the stator support shaft 58 is a cylindrical shaft portion that is fixed to the intermediate partition wall 6 and supports the stator 56 of the torque converter TC, and is disposed between the intermediate shaft M and the hydraulic pump drive shaft 47 in the radial direction. Yes.
- the intermediate partition wall 6 and the hydraulic pump cover 7 are formed with a first suction oil passage L8 and a first discharge oil passage L9 of the hydraulic pump OP. Further, as shown in part in FIG. 3, there are oil passages for supplying such oil in the peripheral wall 4, the end support wall 5, the intermediate partition wall 6 and the shafts of the case 3. Is provided.
- the hydraulic pump rotor of the hydraulic pump OP is drivingly connected to the hydraulic pump drive shaft 47 by spline engagement or the like. Therefore, the hydraulic pump rotor is configured to rotate integrally with the pump impeller 41 of the torque converter TC and the rotor Ro of the rotating electrical machine MG.
- the hydraulic pump OP is an inscribed gear pump having an inner rotor and an outer rotor as hydraulic pump rotors.
- the hydraulic pump OP is arranged coaxially with the rotating electrical machine MG, the torque converter TC, and the transmission TM, and is connected so that the inner rotor rotates integrally with the pump impeller 41 of the torque converter TC at the center in the radial direction. Has been. Accordingly, as the pump impeller 41 rotates, the hydraulic pump OP discharges oil to generate hydraulic pressure and supplies the hydraulic pressure control device.
- the hydraulic pump OP sucks oil from the oil reservoir OT via a strainer (not shown) and the first suction oil passage L8, and discharges it to the first discharge oil passage L9.
- the oil discharged from the hydraulic pump OP is sent to the first line pressure control valve 130 via the first discharge oil passage L9.
- the first line pressure control valve 130 regulates the output pressure of the hydraulic pump OP as the first line pressure 131. Therefore, the hydraulic pressure of each oil passage such as the first discharge oil passage L9 communicating with the discharge port of the hydraulic pump OP is regulated as the first line pressure 131 by the first line pressure control valve 130.
- the oil at the first line pressure 131 is supplied to the first hydraulic control valve 104 and the first servo hydraulic control valve 109.
- the rotating electric machine MG is disposed closer to the internal combustion engine IE (the left side in FIG. 3) than the torque converter TC.
- the rotating electrical machine MG is disposed between the end support wall 5 and the torque converter TC in the axial direction. Further, the rotating electrical machine MG is disposed on the radially outer side with respect to the internal combustion engine coupling shaft EC and the first engagement device C1.
- the stator St of the rotating electrical machine MG is fixed to the case 3.
- the rotor Ro is supported by the case 3 in a rotatable state.
- the rotor Ro is connected to the pump impeller 41 and the cover portion 42 of the torque converter TC via the rotor support member 22 so as to rotate integrally.
- the rotor support member 22 is a member provided so as to extend at least in the radial direction and support the rotor Ro.
- a cylindrical boss portion 22 a is provided at the radially inner end portion of the rotor support member 22, and the second portion is formed between the inner peripheral surface of the boss portion 22 a and the cylindrical protrusion 11 of the case 3.
- One bearing 71 is disposed.
- the rotor Ro and the rotor support member 22 are supported by the first bearing 71 so as to be rotatable with respect to the case 3.
- a ball bearing is used as the first bearing 71.
- the rotation sensor 13 is disposed between the rotor support member 22 and the end support wall 5 in the axial direction and outside the boss portion 22a in the radial direction.
- the rotation sensor 13 is a sensor that detects the rotational position of the rotor Ro of the rotating electrical machine MG, and a resolver or the like can be suitably used.
- the sensor stator 13a of the rotation sensor 13 is fixed to the end support wall 5, and the sensor rotor 13b of the rotation sensor 13 is fixed to the boss 22a of the rotor support member 22 (see FIG. 4).
- the first engaging device C ⁇ b> 1 is located radially inside the rotating electrical machine MG and has a portion that overlaps the rotating electrical machine MG when viewed in the radial direction of the rotating electrical machine MG. Is arranged.
- the first engagement device C ⁇ b> 1 is disposed on the torque converter TC side in the axial direction with respect to the rotor support member 22.
- the first engagement device C1 is an engagement device for selectively drivingly connecting the internal combustion engine connecting shaft EC, the rotary electric machine MG, and the pump impeller 41 of the torque converter TC.
- the first engagement device C1 is a friction engagement device.
- the first clutch hub 31 which is an input side member of the first engagement device C1, is provided integrally with the internal combustion engine connecting shaft EC. Specifically, the first clutch hub 31 is formed integrally with the internal combustion engine connecting shaft EC and is a disk-like member extending radially outward from the transmission device TM side end portion of the internal combustion engine connecting shaft EC. Yes.
- the first engagement device drum 32 which is the output side member of the first engagement device C1, is connected to rotate integrally with the cover portion 42 of the torque converter TC and the rotor support member 22 of the rotating electrical machine MG. Yes.
- the first engagement device drum 32 is joined to the inner peripheral surface of the boss portion 22a of the rotor support member 22, and the step formed at the radial intermediate portion of the cover portion 42 of the torque converter TC. It is joined to the outer peripheral surface of the portion 43b.
- the first engagement device drum 32 also serves as a housing and a cylinder of the first engagement device C1, and houses the first clutch hub 31, the first piston 106, the first friction member 101, and the like inside.
- the first engagement device drum 32 is sealed at the joint with other members so that the internal oil does not leak to the outside, and the inside is in an oil-tight state.
- the first servo oil chamber 108 provided in the first hydraulic servo mechanism 100 of the first engagement device C ⁇ b> 1 includes a first engagement device drum 32 that functions as the first cylinder 105, It is surrounded by one piston 106.
- the first servo oil chamber 108 is formed in an oil-tight manner by a sealing material.
- the first oil chamber 102 of the first engagement device C1 houses the first friction member 101 and the like of the first engagement device C1, and is formed in an oil-tight manner.
- the first oil chamber 102 generates a back pressure of the first hydraulic servo mechanism 100.
- the end surface of the first piston 106 on the internal combustion engine IE side is the piston inner surface (inner surface) of the first servo oil chamber 108.
- the end face of the first piston 106 on the transmission device TM side is the inner surface of the first oil chamber 102 and the piston outer surface (back surface) of the first servo oil chamber 108.
- the hydraulic pressure in the first oil chamber 102 becomes the back pressure of the first piston 106, and the first piston 106 is moved by the force obtained by multiplying the hydraulic pressure in the first oil chamber 102 and the cross-sectional area of the first cylinder 105. It pushes to the internal combustion engine IE side, that is, the release side of the first engagement device C1.
- a first urging mechanism 107 is provided between the first cylinder 105 and the first engagement device drum 32 serving as the first piston 106, and the first urging mechanism 107 moves the first piston 106.
- the pressure is applied to the transmission TM side, that is, the engagement side of the first engagement device C1.
- the first biasing mechanism 107 is a disc spring.
- the first biasing mechanism 107 may be a spring other than a disc spring, for example, a coil spring.
- the hydraulic pressure in the first servo oil chamber 108 is a force obtained by multiplying the hydraulic pressure in the first servo oil chamber 108 and the cross-sectional area of the first cylinder 105 so that the first piston 106 is moved to the transmission device TM side, that is, the first Press toward the engagement side of one engagement device C1. Therefore, the balance between the hydraulic pressure in the first servo oil chamber 108 and the pressing force of the first piston 106 by the first urging mechanism 107 and the pressing force of the first piston 106 by the hydraulic pressure in the first oil chamber 102 gives One engagement device C1 is engaged or released.
- the oil supplied to the first supply port 122 of the first oil chamber 102 flows through a predetermined path (circulation path) in the first oil chamber 102, circulates, and
- the oil chamber 102 is configured to be discharged from the first discharge port 123.
- the first supply port 122 of the first oil chamber 102 is formed by a gap between the first clutch hub 31 and the radially inner end of the first engagement device drum 32.
- the oil regulated by the first hydraulic control valve 104 is sent through the second oil passage L2 provided in the peripheral wall 4 of the case 3, the end support wall 5 and the wall surface of the cylindrical protrusion 11, and the The oil is supplied from the one supply port 122 to the first oil chamber 102.
- the oil supplied to the first supply port 122 flows in a radially outward space (circulation path) formed between the first piston 106 and the first clutch hub 31 in the radial direction.
- the oil that has flowed outward in the radial direction flows through gaps (circulation paths) formed along the plurality of first friction members 101.
- the first friction member 101 is cooled.
- the oil flowing along the first friction member 101 passes through a radially extending space (circulation path) formed between the first clutch hub 31 and the first cover member 43 of the torque converter TC in the radial direction. It flows inward.
- oil is discharged from the first discharge port 123 of the first oil chamber 102.
- the first discharge port 123 is a radially inner portion in a space formed between the first clutch hub 31 and the first cover member 43.
- a gap narrowed (squeezed) in the space formed between the first clutch hub 31 and the first cover member 43 is the first throttle portion 120 and functions as an orifice. Since the first oil chamber 102 is throttled on the discharge side, the hydraulic pressure in the first oil chamber 102 is made uniform as described above.
- the oil discharged from the first discharge port 123 of the first oil chamber 102 is an oil-tight space between the internal combustion engine connecting shaft EC and the first cover member 43, a fifth oil provided in the internal combustion engine connecting shaft EC.
- the path L5, the oil-tight gap between the internal combustion engine connecting shaft EC and the cylindrical projection 11 of the case 3, the third oil path L3 provided in the cylindrical projection 11 and the end support wall 5 of the case 3 Then, it flows in order through the tubular member 96c and the eleventh oil passage L11 provided in the peripheral wall 4, and is sent from the first oil chamber 102 to the oil reservoir OT or the suction port of the hydraulic pump OP (see FIG. 3).
- the oil regulated by the first servo hydraulic control valve 109 is sent through a supply oil passage (not shown) provided in the peripheral wall 4 of the case 3, the end support wall 5, and the wall surface of the cylindrical protrusion 11.
- the first servo oil chamber 108 is supplied from the first supply / discharge port 124 (see FIG. 2).
- the torque converter TC is disposed between the rotating electrical machine MG and the transmission TM in the axial direction.
- the torque converter TC includes a pump impeller 41, a turbine runner 51, a stator 56, and a cover portion 42 that accommodates them.
- the second engagement device C2 and the damper 54 are also accommodated in the cover portion 42.
- the cover part 42 is configured to rotate integrally with the pump impeller 41.
- the pump impeller 41 is integrally provided inside the cover portion 42.
- the cover portion 42 is configured by joining a first cover member 43 on the rotating electrical machine MG side and a second cover member 44 on the transmission device TM side.
- the first cover member 43 is a cylindrical member formed so as to cover the rotating electrical machine MG side of the torque converter TC.
- the first cover member 43 is a stepped cylindrical member in which a stepped portion 43b is formed in a radially intermediate portion. ing.
- the outer peripheral surface of the stepped portion 43b is joined to the inner peripheral surface of the first engagement device drum 32, whereby the cover portion 42 is integrated with the first engagement device drum 32 of the first engagement device C1. It is connected so as to rotate.
- a second engagement device C2 is housed inside the stepped portion 43b in the radial direction.
- the second cover member 44 is a cover member formed so as to cover the transmission device TM side of the torque converter TC, and in this example, the radial intermediate portion faces the transmission device TM side.
- the annular member has a bulging arc-shaped cross-sectional shape.
- a hydraulic pump drive shaft 47 extending in the axial direction toward the transmission device TM is integrally provided at the radially inner end of the second cover member 44.
- the hydraulic pump drive shaft 47 is a cylindrical shaft portion that rotates integrally with the cover portion 42 of the torque converter TC, and is disposed coaxially with the intermediate shaft M on the radially outer side of the intermediate shaft M.
- a second bearing 72 is disposed between the outer peripheral surface of the hydraulic pump drive shaft 47 and the inner peripheral surface of the through hole of the hydraulic pump cover 7.
- the hydraulic pump drive shaft 47 and the cover portion 42 of the torque converter TC are supported by the second bearing 72 so as to be rotatable with respect to the case 3.
- a needle bearing is used as the second bearing 72.
- An end of the hydraulic pump drive shaft 47 on the transmission device TM side is connected to rotate integrally with a hydraulic pump rotor of the hydraulic pump OP.
- the connection between the hydraulic pump drive shaft 47 and the hydraulic pump rotor is performed by spline engagement.
- the first cover member 43 and the second cover member 44 are integrally joined by welding or the like. Further, when viewed as the drive device 1 as a whole, the cover portion 42 of the torque converter TC, the rotor support member 22, and the first engagement device drum 32 of the first engagement device C1 are connected to rotate integrally. It is a connecting body of a plurality of members, and this connecting body constitutes the input shaft I.
- the input shaft I is rotatably supported by the case 3 via the first bearing 71 on the internal combustion engine connecting shaft EC side, and is rotatably supported by the case 3 via the second bearing 72 on the transmission device TM side. Yes.
- the input shaft I is joined so as to rotate integrally with the rotor Ro of the rotating electrical machine MG and the pump impeller 41.
- the turbine runner 51 of the torque converter TC is disposed opposite to the pump impeller 41 on the rotating electrical machine MG side with respect to the pump impeller 41 inside the cover portion 42.
- the turbine runner 51 is connected so as to rotate integrally with the input shaft I.
- the radially inner end of the turbine runner 51 is spline-engaged with the intermediate shaft M.
- the stator 56 of the torque converter TC is disposed between the pump impeller 41 and the turbine runner 51 in the axial direction.
- the stator 56 is supported on a stator support shaft 58 via a one-way clutch 57.
- the stator support shaft 58 is a cylindrical shaft portion and is fixed to the intermediate partition wall 6 on the transmission device TM side.
- the torque converter TC can transmit torque between the drive-side pump impeller 41 and the driven-side turbine runner 51 via oil filled in the cover portion 42.
- the damper 54 is disposed between the second engagement device C2 and the turbine runner 51 in the axial direction.
- the damper 54 is provided to absorb the vibration of the driving force transmitted between the pump impeller 41 and the turbine runner 51 in the engaged state of the second engagement device C2.
- the damper 54 is for vibration absorption provided between the input side member 54a and the output side member 54b configured to be relatively movable in the circumferential direction, and between the input side member 54a and the output side member 54b. Spring 54c and the like.
- the input side member 54a of the damper 54 is connected to rotate integrally with the second engagement device drum 62 of the second engagement device C2.
- the output side member 54b of the damper 54 is connected so as to rotate integrally with the turbine runner 51 and the intermediate shaft M.
- the second engagement device C ⁇ b> 2 is arranged on the inner side in the radial direction of the stepped portion 43 b of the cover portion 42 and on the rotating electrical machine MG side in the axial direction with respect to the turbine runner 51.
- the second engagement device C2 engages the pump impeller 41 and the turbine runner 51, thereby stopping the transmission of the driving force via the oil and bringing them into a directly connected state (lock-up state). It is.
- the second engagement device C2 is a friction engagement device.
- the second clutch hub 61 which is an input side member of the second engagement device C2, is provided so as to rotate integrally with the cover portion.
- the second clutch hub 61 is connected to the support cylindrical portion 43a of the first cover member 43 of the cover portion 42 by spline engagement on the radially inner side.
- the second engagement device drum 62 that is an output side member of the second engagement device C ⁇ b> 2 is drivingly connected to the turbine runner 51 and the intermediate shaft M via the damper 54.
- the second engagement device drum 62 is formed integrally with the input side member 54 a of the damper 54.
- the second piston 116, the second friction member 111, and the like of the second engagement device C2 are also accommodated in a space radially inward of the stepped portion 43b.
- the second engagement device C2 is disposed adjacent to the first engagement device C1 in the axial direction with the first cover member 43 interposed therebetween.
- the first cover member 43 also serves as a housing and a cylinder of the second engagement device C2, and houses the second clutch hub 61, the second piston 116, the second friction member 111, and the like inside.
- the second servo oil chamber 118 provided in the second hydraulic servo mechanism 110 of the second engagement device C2 includes a first cover member 43 that functions as a second cylinder 115, and a second piston. 116.
- the second servo oil chamber 118 is formed in an oil-tight manner by a sealing material.
- the second oil chamber 112 of the second engagement device C2 houses the second friction member 111 and the like of the second engagement device C2, and is formed in an oil-tight manner.
- the second oil chamber 112 generates a back pressure of the second hydraulic servo mechanism 110.
- the end surface of the second piston 116 on the internal combustion engine IE side is the piston inner surface of the second servo oil chamber 118.
- the end face of the second piston 116 on the transmission device TM side is the inner surface of the second oil chamber 112 and the piston outer surface of the second servo oil chamber 118.
- the hydraulic pressure in the second oil chamber 112 becomes the back pressure of the second piston 116, and the second piston 116 is moved by the force obtained by multiplying the hydraulic pressure in the second oil chamber 112 and the cross-sectional area of the second cylinder 115. Press toward the internal combustion engine IE, that is, the release side of the second engagement device C2.
- a second urging mechanism 117 is provided between the second cylinder 115 and the second clutch hub 61, and the second urging mechanism 117 moves the second piston 116 to the internal combustion engine IE side, that is, the second urging mechanism 117. Press toward the release side of the engagement device C2.
- the second urging mechanism 117 is a coil spring.
- the second urging mechanism 117 may be a spring other than the coil spring, for example, a disc spring.
- the hydraulic pressure in the second servo oil chamber 118 is a force obtained by multiplying the hydraulic pressure in the second servo oil chamber 118 and the cross-sectional area of the second cylinder 115 so that the second piston 116 is moved to the transmission TM side, that is, the first.
- the oil supplied to the second supply port 127 of the second oil chamber 112 circulates through a predetermined path (circulation path) in the second oil chamber 112,
- the second oil chamber 112 is configured to be discharged from the second discharge port 128 (see FIG. 3).
- the second supply port 127 of the second oil chamber 112 is formed in a support cylindrical portion 43 a provided on the radially inner side of the first cover member 43.
- the support cylindrical portion 43a is a cylindrical portion that is arranged coaxially with respect to the axis X and is formed so as to extend in the axial direction toward the transmission device TM.
- the outer peripheral surface of the support cylindrical portion 43 a constitutes the radially inner side surface of the second cylinder 115 and is splined to the second clutch hub 61.
- An intermediate shaft M is arranged on the radially inner side of the support cylindrical portion 43a, and an end portion of the intermediate shaft M on the internal combustion engine IE side is rotatably supported by the inner peripheral surface of the support cylindrical portion 43a.
- the oil regulated by the second hydraulic control valve 114 is sent through a sixth oil passage L6 provided in the intermediate shaft M and is supplied from the second supply port 127 to the second oil chamber 112.
- the oil supplied to the second supply port 127 flows in a radially outward space (circulation path) formed between the second piston 116 and the second clutch hub 61 in the radial direction.
- the oil that has flowed outward in the radial direction flows through gaps (circulation paths) formed along the plurality of second friction members 111. At this time, the second friction member 111 is cooled.
- the oil that has flowed along the second friction member 111 passes a radially extending space (circulation path) formed between the first cover member 43 and the second engagement device drum 62 outward in the radial direction. It flows toward. And after circulating through the inside of the cover part 42 in which the pump impeller 41 and the turbine runner 51 are arranged, as shown in FIG. 3, the oil is discharged from the second discharge port 128 of the second oil chamber 112. The oil discharged from the second discharge port 128 of the second oil chamber 112 flows through the oil passage provided around the intermediate shaft M and is sent to the oil storage unit OT or the suction port of the hydraulic pump OP.
- the oil regulated by the second servo hydraulic control valve 119 is sent through a seventh oil passage L7 provided in the intermediate shaft M, and is supplied from the second supply / discharge port 129 to the second servo oil chamber 118. .
- the transmission TM is arranged on the output shaft O side of the intermediate partition wall 6, that is, on the side opposite to the torque converter TC (right side in FIG. 3) across the intermediate partition wall 6.
- the transmission apparatus TM is a stepped automatic transmission apparatus having a plurality of shift stages having different speed ratios.
- the hydraulic pump OP is configured by a mechanical pump driven by the driving force transmitted to the input shaft I.
- the embodiment of the present invention is not limited to this. That is, the hydraulic pump OP is an electric pump driven by a pump driving motor different from the internal combustion engine IE and the rotating electrical machine MG, or is configured by a combination of such an electric pump and a mechanical pump. May be.
- the drive device 1 includes the pump impeller 41, the turbine runner 51, and the second engagement device C2 that directly connects the pump impeller 41 and the turbine runner 51 as the torque converter TC.
- the drive device 1 is not provided with the torque converter TC, and instead of the torque converter TC, a friction engagement device that selectively drives and connects the input shaft I and the intermediate shaft M is used as the second engagement device C2. May be provided.
- the second engagement device C2 includes a second oil chamber 112 that generates the back pressure of the second hydraulic servo mechanism 110 and accommodates the second friction member 111 of the second engagement device C2.
- the second oil chamber hydraulic pressure 113 is controlled independently of the first oil chamber oil pressure 103.
- the second hydraulic servomechanism 110 of the second engagement device C2 is surrounded by the first cover member 43 functioning as the second cylinder 115 and the second piston 116 so as to be oil-tight.
- the case where the configured second servo oil chamber 118 is provided has been described as an example.
- the embodiment of the present invention is not limited to this. That is, the second servo oil chamber 118 may not be provided in an oil-tight manner, but may be configured integrally with the second oil chamber 112.
- the second piston 116 presses the second friction member 111 by controlling the hydraulic pressure supplied to the second servo oil chamber 118 side or the opposite side of the second servo oil chamber 118 of the second piston 116.
- the second oil chamber 112 integrally includes a second servo oil chamber 118 provided in communication with the second oil chamber 112, and the engagement state of the second engagement device C2 is the second It is controlled by the hydraulic pressure supplied to the second oil chamber 112 on the servo oil chamber 118 side or the hydraulic pressure supplied to the second oil chamber 112 other than the second servo oil chamber 118.
- the first hydraulic control valve 104 receives the oil of the first line pressure 131 controlled by the first line pressure control valve 130 and supplies the oil of the first oil chamber hydraulic pressure 103 to the first oil pressure.
- the second oil pressure control valve 114 is supplied to the first oil chamber 102, and receives the oil of the second oil pressure 113 controlled by the second line pressure control valve 140.
- the case where the oil chamber 112 is supplied has been described as an example.
- the embodiment of the present invention is not limited to this. That is, the first hydraulic control valve 104 may be configured to receive the supply of the oil of the second line pressure 141 and supply the oil of the first oil chamber hydraulic pressure 103 to the first oil chamber 102.
- the second hydraulic control valve 114 is configured to receive the supply of the oil of the second line pressure 141 or the first line pressure 131 and supply the oil of the second oil chamber oil pressure 113 to the second oil chamber 112. May be.
- the first hydraulic control valve 104 is configured to receive the supply of the oil of the first line pressure 131 and supply the oil of the first oil chamber oil pressure 103 to the first oil chamber 102
- the two hydraulic control valve 114 may be configured to receive the supply of the oil of the first line pressure 131 and supply the oil of the second oil chamber oil pressure 113 to the second oil chamber 112.
- the transmission TM is a stepped automatic transmission
- the embodiment of the present invention is not limited to this. That is, when the transmission apparatus TM is a transmission apparatus other than the stepped automatic transmission apparatus, such as a continuously variable automatic transmission apparatus capable of continuously changing the transmission gear ratio, one preferred embodiment of the present invention. One.
- the driving device 1 is described as an example in which the first throttle unit 120 as the throttle unit that throttles the flow rate is provided in the oil discharge passage for the oil discharged from the first oil chamber 102. did.
- the embodiment of the present invention is not limited to this. That is, the drive device 1 may be configured not to include a throttle portion that restricts the flow rate in the oil discharge oil passage discharged from the first oil chamber 102, or a place other than the discharge oil passage, for example,
- the first oil chamber 102 or the supply oil passage of the first oil chamber 102 may be provided with a throttle portion for reducing the flow rate.
- the first engagement device C1 biases the first piston 106 with a predetermined initial engagement load so as to press the first friction member 101 toward the engagement side.
- the case where the biasing mechanism 107 is provided has been described as an example.
- the embodiment of the present invention is not limited to this. That is, the first engagement device C1 may include a first biasing mechanism 107 that biases the first piston 106 with a predetermined initial engagement load so as to press the first friction member 101 toward the release side. Good.
- the first hydraulic control valve 104 generates a back pressure in the first oil chamber 102 that presses the first piston 106 toward the disengagement side with a load larger than the initial engagement load.
- the case where the first oil chamber oil pressure 103 is controlled has been described as an example. However, the embodiment of the present invention is not limited to this. In other words, the first hydraulic control valve 104 generates the first oil chamber hydraulic pressure 103 so as to generate a back pressure in the first oil chamber 102 that presses the first piston 106 toward the disengagement side with a load smaller than the initial engagement load. May be controlled.
- the present invention includes an input member that is drivingly connected to a rotating electrical machine, an output member that is drivingly connected to a wheel, a first engagement device that selectively drives and connects the input member to an internal combustion engine, the input member, and the
- the present invention can be suitably used for a vehicle drive device including a fluid coupling provided in a power transmission path that connects the output member.
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Abstract
Description
特許文献2の技術では、第一係合装置の摩擦部材に油を供給するために、流体継手のカバー内に、流体継手の継手入力側部材と継手出力側部材とを直結(ロックアップ)する第二係合装置に加えて、第一係合装置を収容している。詳細には、流体継手のカバー内に、流体継手の本体部を収容する本体部収容室と、第一係合装置の摩擦部材が収容されると共に第一係合装置のピストンにおける作動油の油圧が作用する側とは反対側に油圧を作用させるように形成された差圧形成室とが、連通(共用)して備えられている。また、本体部収容室と差圧形成室とが連通して備えられる場合には、通常、これらに油圧を供給する油圧供給系統も共用されると考えられる。
しかしながら、特許文献2の技術では、本体部収容室と差圧形成室とが連通(共用)されているため、第一及び第二係合装置の一方の制御中には、一方の油室内に生じる油圧変動や、一方の油圧供給系統の作動が、他方に影響し、他方又は双方の制御性が悪化する恐れがある。また、双方の制御が同時に行なわれる場合には、各油室内に生じる油圧変動や、各油圧供給系統の作動が、互いに干渉し、双方の制御性が悪化する恐れがある。
前記第一油室に供給する油圧である第一油室油圧を制御する第一油圧制御弁と、前記第二油室に供給する油圧である第二油室油圧を前記第一油室油圧とは独立して制御する第二油圧制御弁と、を備える点にある。
また、本願において「駆動連結」とは、2つの回転要素が駆動力を伝達可能に連結された状態を指し、当該2つの回転要素が一体的に回転するように連結された状態、或いは当該2つの回転要素が一又は二以上の伝動部材を介して駆動力を伝達可能に連結された状態を含む概念として用いている。このような伝動部材としては、回転を同速で又は変速して伝達する各種の部材が含まれ、例えば、軸、歯車機構、ベルト、チェーン等が含まれる。また、このような伝動部材として、回転及び駆動力を選択的に伝達する係合要素、例えば摩擦クラッチや噛み合い式クラッチ等が含まれていてもよい。
なお、本願において「流体継手」は、トルク増幅機能を有するトルクコンバータ、及びトルク増幅機能を有さない通常の流体継手のいずれをも含む概念として用いている。
本発明に係る車両用駆動装置1(以下、駆動装置1と称す)の実施形態について、図面を参照して説明する。図1は、本実施形態に係る駆動装置1の概略構成を示す模式図である。この図に示すように、本実施形態に係る駆動装置1は、概略的には、内燃機関IE及び回転電機MGを駆動力源として備え、これらの駆動力源の駆動力を、動力伝達機構を介して車輪Wへ伝達する構成となっている。駆動装置1は、回転電機MGに駆動連結される入力軸Iと、車輪Wに駆動連結される出力軸Oと、入力軸Iを内燃機関IEに選択的に駆動連結する第一係合装置C1と、入力軸Iと出力軸Oとを結ぶ動力伝達経路に設けられた流体継手としてのトルクコンバータTCと、を備えている。本実施形態では、駆動装置1は、トルクコンバータTCと出力軸Oとの間の動力伝達経路に、変速装置TMを備えている。なお、入力軸Iが、本発明における「入力部材」に相当し、出力軸Oが、本発明における「出力部材」に相当する。
トルクコンバータTCは、当該トルクコンバータTCの本体部を収容する本体部収容室137に、入力軸I側に駆動連結されるポンプインペラ41と出力軸O側に駆動連結されるタービンランナ51とを直結する第二係合装置C2の係合状態を油圧により制御するための第二油室112を備えている。なお、ポンプインペラ41が、本発明における「継手入力側部材」であり、タービンランナ51が、本発明における「継手出力側部材」である。
まず、本実施形態に係る駆動装置1の駆動伝達系の構成について説明する。図1に示すように、駆動装置1は、車両駆動用の駆動力源として内燃機関IE及び回転電機MGを備え、これらの内燃機関IEと回転電機MGとが直列に駆動連結されるパラレル方式のハイブリッド車両用の駆動装置1となっている。本実施形態では、駆動装置1は、動力伝達機構として、トルクコンバータTCと変速装置TMとを備えており、当該トルクコンバータTC及び変速装置TMにより、駆動力源としての内燃機関IE及び回転電機MGの回転速度を変速すると共にトルクを変換して出力軸Oに伝達する。本実施形態に係わる駆動装置1では、内燃機関IEと回転電機MGとトルクコンバータTCと変速装置TMとが同軸上に配置されていると共に、内燃機関IE側から軸方向に沿って出力軸Oへ向かって回転電機MG、トルクコンバータTC、変速装置TMの順に配列されている。また、内燃機関連結軸EC、入力軸I、中間軸M、及び出力軸Oも、これと同軸上に配置されている。ここでは、これらの同軸上に配置された駆動装置1の各部材の軸心を装置軸心X1とする。また、実施形態の説明において、単に軸方向、径方向、周方向という場合には、この装置軸心X1を基準とした方向を指すものとする。
次に、第一係合装置C1及び第二係合装置C2に係わる油圧制御系の構成について図2を参照して説明する。
上記したように、第一係合装置C1は、第一ピストン106を含む第一油圧サーボ機構100と、第一摩擦部材101と、当該第一摩擦部材101を押圧する第一ピストン106と、第一摩擦部材101が収容されるとともに、油圧が供給されて第一ピストン106における作動用の油圧が作用する側とは反対側である背圧側に油圧を作用させるように形成された第一油室102と、を備えている。
本実施形態では、トルクコンバータTCは、図2に示すように、第二係合装置C2を含んで構成されており、この第二係合装置C2は、第二ピストン116を含む第二油圧サーボ機構110と、第二摩擦部材111と、当該第二摩擦部材111を押圧する第二ピストン116と、を備えている。また、第二油室112には、第二係合装置C2の第二摩擦部材111及びトルクコンバータTCのポンプインペラ41及びタービンランナ51が収容されるとともに、油圧が供給されて第二ピストン116における作動用の油圧が作用する側とは反対側である背圧側に油圧を作用させるように形成されている。
次に、図2に示す油圧制御系の各構成の詳細について説明する。
本実施形態では、油圧ポンプOPの出力圧を第一ライン圧131として制御(調圧)する第一ライン圧制御弁130として、スプール130p及び当該スプール130pを付勢するばね130s等からなる調圧弁の一種であるプレッシャーレギュレータバルブが用いられている。すなわち、第一ライン圧制御弁130は、基準圧室130aに供給された基準圧136及びばね130sによりスプール130pを第一方向(図2における下向き)に押圧する押圧力と、フィードバック圧室130bに供給された第一ライン圧131によりスプール130pを第二方向(図2における上向き)に押圧する押圧力と、のバランスにより、油圧ポンプOPから吐出された油のドレイン量を調節することにより、第一ライン圧131を調圧する。具体的には、第一ライン圧131による第二方向側への押圧力が、基準圧136及びばね130sによる第一方向側への押圧力を上回った場合に、スプール130pが第二方向側へ移動して、第一ライン圧131が供給されている調圧ポート130cと排出ポート130dとの連通開口量が大きくなり、油圧ポンプOPから吐出された油を排出ポート130dからドレインする量が増加し、第一ライン圧131が低下する。逆に、第一ライン圧131による第二方向側への押圧力が、基準圧136及びばね130sによる第一方向側への押圧力を下回った場合に、スプール130pが第一方向側へ移動して、調圧ポート130cと排出ポート130dとの連通開口量が小さくなり、排出ポート130dからのドレイン量が減少し、第一ライン圧131が上昇する。よって、第一ライン圧制御弁130は、第一ライン圧131による第二方向側への押圧力と、基準圧136及びばね130sによる第一方向側への押圧力と、がバランスするように、スプール130pが移動して排出ポート130dへの連通開口量を増減することにより、フィードバック的に第一ライン圧131を調圧する。図2に示す油圧制御系では、第一ライン圧131の油は、第一係合装置C1に供給する油圧を制御する第一油圧制御弁104及び第一サーボ油圧制御弁109等に送られる。また、排出ポート130dからドレインされた油は、油貯留部OT又は油圧ポンプOPの吸入口に送られる。
本実施形態では、基準圧制御弁135により制御(調圧)された基準圧136は、第二ライン圧制御弁140にも供給される。第二ライン圧制御弁140として、第一ライン圧制御弁130と同様に、スプール140p及び当該スプール140pを付勢するばね140s等からなる調圧弁の一種であるプレッシャーレギュレータバルブが用いられる。すなわち、第二ライン圧制御弁140は、第一ライン圧制御弁130と同様に、基準圧室140aに供給された基準圧136及びばね140sによりスプール140pを第二方向(図2における上向き)に押圧する押圧力と、フィードバック圧室140bに供給された第二ライン圧141によりスプール140pを第一方向(図2における下向き)に押圧する押圧力と、のバランスにより、第一ライン圧制御弁130の出力ポート130eから供給された油のドレイン量を調節することにより、第一ライン圧131を更に減圧して第二ライン圧141を調圧する。図2に示す油圧制御系では、第二ライン圧141の油は、第二係合装置C2に供給する油圧を制御する第二油圧制御弁114及び第二サーボ油圧制御弁119等に送られる。また、排出ポート140dからドレインされた油は、油貯留部OT又は油圧ポンプOPの吸入口に送られる。
本実施形態では、第一ライン圧制御弁130により制御(調圧)された第一ライン圧131は、第一油圧制御弁104に供給される。本例では、第一油圧制御弁104として、スプール104p及び当該スプール104pを付勢するばね104s等から構成され、元圧からの油路の開閉とドレインへの油路の開閉とを同時に行うタイプの調圧弁(減圧弁)が用いられる。すなわち、第一油圧制御弁104は、ばね104sによりスプール104pを第二方向(図2における上向き)に押圧する押圧力と、フィードバック圧室104bに供給された第一油室油圧103によりスプール104pを第一方向(図2における下向き)に押圧する押圧力と、のバランスにより、第一ライン圧131の油の供給量及び第一油室油圧103の油のドレイン量を調節することにより、第一ライン圧131を更に減圧して第一油室油圧103を調圧する。
第一油圧制御弁104により調圧された第一油室油圧103の油は、第一油室102に供給される。第一油室102は、第一油圧サーボ機構100の背圧を生成すると共に当該第一係合装置C1の第一摩擦部材101を収容している、油密状の油室である。本実施形態では、第一油圧サーボ機構100は、第一シリンダ105、第一ピストン106、及び第一シリンダ105と第一ピストン106とに囲まれた第一サーボ油室108により構成されている。第一ピストン106の背面が、第一油室102の壁面となっており、第一油室油圧103が、第一ピストン106の背圧となっている。また、第一油室102は、第一油室102の第一供給口122に供給された油が、第一油室102内の所定経路(循環路)を流れて循環し、第一油室102の第一排出口123から排出されるように構成されている。第一油室102の循環路は、第一ピストン106の背面及び第一摩擦部材101に沿って油が流れるように構成されている。この第一油室102に供給された油は、第一油室102内を循環して、第一ピストン106の背圧を生成するとともに、第一摩擦部材101を冷却する。第一油室102内を循環して、第一油室102の第一排出口123から排出された油は、第一絞り部120を介して、油貯留部OT又は油圧ポンプOPの吸入口に送られる。
本実施形態では、第二ライン圧制御弁140により制御(調圧)された第二ライン圧141は、第二絞り部125を介して、第二油圧制御弁114に供給される。この第二絞り部125により、第二油室油圧113側に供給される第二ライン圧141の油量が規制されている。そして、第二油圧制御弁114により、供給された第二ライン圧141の油のドレイン量が調節されて、第二油室油圧113が調圧される。本例では、第二油圧制御弁114として、スプール114p及び当該スプール114pを付勢するばね114s等から構成され、ドレインへの油路の開閉のみを行うタイプの調圧弁(減圧弁)が用いられる。すなわち、第二油圧制御弁114は、ばね114sによりスプール114pを第二方向(図2における上向き)に押圧する押圧力と、入力ポート114aに供給された第二油室油圧113によりスプール114pを第一方向(図2における下向き)に押圧する押圧力と、のバランスにより、油のドレイン量を調節することにより、第二ライン圧141を更に減圧して第二油室油圧113を調圧する。
第二油圧制御弁114により調圧された第二油室油圧113の油は、第二油室112に供給される。第二油室112は、第二油圧サーボ機構110の背圧を生成する油密状の油室である。この第二油室112には、第二係合装置C2の第二摩擦部材111及びトルクコンバータTCのポンプインペラ41及びタービンランナ51が収容されている。本実施形態では、第二油圧サーボ機構110は、第二シリンダ115、第二ピストン116、及び第二シリンダ115と第二ピストン116とに囲まれた第二サーボ油室118により構成されている。第二ピストン116の背面が、第二油室112の壁面となっており、第二油室油圧113が、第二ピストン116の背圧となっている。また、第二油室112は、第二油室112の第二供給口127に供給された油が、第二油室112内の所定経路(循環路)を流れて循環し、第二油室112の第二排出口128から排出されるように構成されている。第二油室112の循環路は、第二ピストン116の背面、第二摩擦部材111、ポンプインペラ41、及びタービンランナ51に沿って油が流れるように構成されている。この第二油室112に供給された油は、第二油室112内を循環して、第二ピストン116の背圧を生成し、第二摩擦部材111を冷却すると共に、ポンプインペラ41及びタービンランナ51の作動油として供給される。第二油室112内を循環して、第二油室112の第二排出口128から排出された油は、油貯留部OT又は油圧ポンプOPの吸入口に送られる。
本実施形態では、第一ライン圧制御弁130により制御(調圧)された第一ライン圧131は、第一サーボ油圧制御弁109に供給される。第一サーボ油圧制御弁109として、ソレノイドと調圧弁(減圧弁)との機能を合わせ持った油圧制御弁であるリニアソレノイド弁が用いられている。第一ライン圧制御弁130は、ソレノイドの駆動力に応じて、供給された第一ライン圧131の減圧量を制御して、第一サーボ油圧121を生成する。具体的には、第一サーボ油圧制御弁109は、図示はしていないが、ばね及びソレノイドの駆動力によりスプールを押圧する押圧力と、フィードバック圧室109bに供給された第一サーボ油圧121によりスプールを押圧する押圧力と、のバランスにより、入力ポート109iから供給される第一ライン圧131の油の供給量、及び排出ポート109dから排出される第一サーボ油圧121の油のドレイン量を調節することにより、第一ライン圧131を更に減圧して第一サーボ油圧121を調圧する。なお、第一サーボ油圧制御弁109として、ソレノイドの機能と調圧弁(減圧弁)の機能とが分離された、デューティソレノイド弁と調圧弁(減圧弁)とが用いられるようにしてもよい。
本実施形態では、第二ライン圧制御弁140により制御(調圧)された第二ライン圧141は、第二サーボ油圧制御弁119に供給される。第二サーボ油圧制御弁119として、第一サーボ油圧制御弁109と同様に、ソレノイドと調圧弁(減圧弁)との機能を合わせ持った油圧制御弁であるリニアソレノイド弁が用いられている。第二サーボ油圧制御弁119は、ソレノイドの駆動力に応じて、供給された第二ライン圧141の減圧量を制御して、第二サーボ油圧126を生成する。具体的には、第二サーボ油圧制御弁119は、図示はしていないが、ばね及びソレノイドの駆動力によりスプールを押圧する押圧力と、フィードバック圧室119bに供給された第二サーボ油圧126によりスプールを押圧する押圧力と、のバランスにより、入力ポート119iから供給される第二ライン圧141の油の供給量、及び排出ポート119dから排出される第二サーボ油圧126の油のドレイン量を調節することにより、第二ライン圧141を更に減圧して第二サーボ油圧126を調圧する。なお、第二サーボ油圧制御弁119として、ソレノイドの機能と調圧弁(減圧弁)の機能とが分離された、デューティソレノイド弁と調圧弁(減圧弁)とが用いられるようにしてもよい。
次に、本実施形態に係る駆動装置1の各部の詳細な構成について、図3及び図4を参照して説明する。図4は、図3の断面図の部分拡大図である。
図3に示すように、ケース3は、概略的に、円筒状の周壁4と、軸方向における回転電機MGの図3における左側(内燃機関IE側)に設けられた端部支持壁5と、端部支持壁5の径方向中心部から軸方向に突出する筒状突出部11と、軸方向におけるトルクコンバータTCの図3における右側(変速装置TM側)に設けられた中間隔壁6と、を有している。ケース3内における端部支持壁5と中間隔壁6との間の空間に、回転電機MG、第一係合装置C1、及びトルクコンバータTCが収容されている。また、図示は省略しているが、中間隔壁6よりも図3における右側の空間に、変速装置TMが収容されている。なお、端部支持壁5よりも図3における左側には、内燃機関IEが備えられている。
図3に示すように、回転電機MGは、トルクコンバータTCよりも内燃機関IE側(図3における左側)に配置されている。本実施形態では、回転電機MGは、軸方向における端部支持壁5とトルクコンバータTCとの間に配置されている。また、回転電機MGは、内燃機関連結軸EC及び第一係合装置C1に対して径方向外側に配置されている。回転電機MGのステータStは、ケース3に固定されている。ロータRoは、回転可能な状態でケース3に支持されている。また、ロータRoは、ロータ支持部材22を介してトルクコンバータTCのポンプインペラ41及びカバー部42と一体回転するように連結されている。ロータ支持部材22は、少なくとも径方向に延びてロータRoを支持するように設けられた部材である。本実施形態では、ロータ支持部材22の径方向内側端部に円筒状のボス部22aが設けられており、当該ボス部22aの内周面とケース3の筒状突出部11との間に第一軸受71が配置されている。ロータRo及びロータ支持部材22は、この第一軸受71により、ケース3に対して回転可能に支持されている。本実施形態では、第一軸受71としてボールベアリングを用いている。また、軸方向におけるロータ支持部材22と端部支持壁5との間であって、ボス部22aの径方向外側に、回転センサ13が配置されている。この回転センサ13は、回転電機MGのロータRoの回転位置を検出するセンサであり、レゾルバ等を好適に用いることができる。ここでは、端部支持壁5に回転センサ13のセンサステータ13aが固定され、ロータ支持部材22のボス部22aに回転センサ13のセンサロータ13bが固定されている(図4参照)。
図3に示すように、第一係合装置C1は、回転電機MGの径方向内側であって、回転電機MGの径方向に見て回転電機MGと重複する部分を有する位置に配置されている。また、第一係合装置C1は、ロータ支持部材22に対して軸方向でトルクコンバータTC側に配置されている。第一係合装置C1は、内燃機関連結軸ECと回転電機MG及びトルクコンバータTCのポンプインペラ41とを選択的に駆動連結するための係合装置である。本実施形態では、第一係合装置C1は、摩擦係合装置とされている。第一係合装置C1の入力側部材である第一クラッチハブ31は、内燃機関連結軸ECと一体的に設けられている。具体的には、第一クラッチハブ31は、内燃機関連結軸ECと一体的に形成され、当該内燃機関連結軸ECの変速装置TM側端部から径方向外側に延びる円板状部材とされている。また、第一係合装置C1の出力側部材である第一係合装置ドラム32は、トルクコンバータTCのカバー部42及び回転電機MGのロータ支持部材22と一体的に回転するように連結されている。具体的には、第一係合装置ドラム32は、ロータ支持部材22のボス部22aの内周面に接合されているとともに、トルクコンバータTCのカバー部42における径方向中間部分に形成された段差部43bの外周面に接合されている。第一係合装置ドラム32は、第一係合装置C1のハウジング及びシリンダを兼ねており、内側に第一クラッチハブ31、第一ピストン106、及び第一摩擦部材101等を収容している。そして、第一係合装置ドラム32は、内部のオイルが外に漏れないように他の部材との接合部が密閉され、内部を油密状態としている。
図3に示すように、トルクコンバータTCは、軸方向における回転電機MGと変速装置TMとの間に配置されている。トルクコンバータTCは、ポンプインペラ41、タービンランナ51、ステータ56、及びこれらを収容するカバー部42を備えている。また、本実施形態では、カバー部42内に、第二係合装置C2及びダンパ54も収容されている。カバー部42は、ポンプインペラ41と一体回転するように構成されている。ここでは、ポンプインペラ41は、カバー部42の内側に一体的に設けられている。
図3に示すように、第二係合装置C2は、カバー部42の段差部43bの径方向内側であって、タービンランナ51に対して軸方向で回転電機MG側に配置されている。第二係合装置C2は、ポンプインペラ41とタービンランナ51とを係合することにより、オイルを介した駆動力の伝達を止めてこれらを直結状態(ロックアップ状態)とするための係合装置である。本実施形態では、第二係合装置C2は、摩擦係合装置とされている。第二係合装置C2の入力側部材である第二クラッチハブ61は、カバー部42と一体回転するように設けられている。具体的には、第二クラッチハブ61は、径方向内側においてカバー部42の第一カバー部材43が有する支持円筒状部43aにスプライン係合して連結されている。また、第二係合装置C2の出力側部材である第二係合装置ドラム62は、ダンパ54を介してタービンランナ51及び中間軸Mに駆動連結されている。具体的には、第二係合装置ドラム62は、ダンパ54の入力側部材54aと一体的に形成されている。なお、第二係合装置C2の第二ピストン116及び第二摩擦部材111等も、段差部43bの径方向内側の空間に収容されている。また、本実施形態では、第二係合装置C2は、第一カバー部材43を挟んで第一係合装置C1と軸方向に隣接して配置されている。
図4に示すように、第二係合装置C2の第二油圧サーボ機構110に設けられている第二サーボ油室118は、第二シリンダ115として機能する第一カバー部材43と、第二ピストン116とにより囲まれて構成されている。第二サーボ油室118は、シール材により油密状に形成されている。また、第二係合装置C2の第二油室112は、当該第二係合装置C2の第二摩擦部材111等を収容し、油密状に形成されている。そして、第二油室112は、第二油圧サーボ機構110の背圧を生成する。
ここで、支持円筒状部43aは、軸心Xに対して同軸状に配置され、軸方向に変速装置TM側に延在するように形成された円筒状部である。支持円筒状部43aの外周面は、第二シリンダ115の径方向内側側面を構成すると共に、第二クラッチハブ61にスプライン連結している。支持円筒状部43aの径方向内側には中間軸Mが配置されており、支持円筒状部43aの内周面により中間軸Mの内燃機関IE側端部が回転可能に支持されている。
図3では省略しているが、中間隔壁6の出力軸O側、すなわち中間隔壁6を挟んでトルクコンバータTCとは反対側(図3における右側)に、変速装置TMが配置されている。本実施形態では、変速装置TMは、変速比の異なる複数の変速段を有する有段の自動変速装置である。
最後に、本発明のその他の実施形態について説明する。なお、以下に説明する各実施形態の構成は、それぞれ単独で適用されるものに限られず、矛盾が生じない限り、他の実施形態の構成と組み合わせて適用することも可能である。
IE:内燃機関
TC:トルクコンバータ(流体継手)
TM:変速装置TM
C1:第一係合装置
C2:第二係合装置
I:入力軸(入力部材)
M:中間軸
O:出力軸(出力部材)
W:車輪
1:駆動装置(車両用駆動装置)
41:ポンプインペラ(継手入力側部材)
51:タービンランナ(継手出力側部材)
100:第一油圧サーボ機構
101:第一摩擦部材
102:第一油室
103:第一油室油圧
104:第一油圧制御弁
105:第一シリンダ
106:第一ピストン
107:第一付勢機構(付勢機構)
108:第一サーボ油室
109:第一サーボ油圧制御弁
110:第二油圧サーボ機構
111:第二摩擦部材
112:第二油室
113:第二油室油圧
114:第二油圧制御弁
115:第二シリンダ
116:第二ピストン
117:第二付勢機構
118:第二サーボ油室
119:第二サーボ油圧制御弁
120:第一絞り部(絞り部)
121:第一サーボ油圧
122:第一供給口
123:第一排出口
124:第一給排口
125:第二絞り部
126:第二サーボ油圧
127:第二供給口
128:第二排出口
129:第二給排口
130:第一ライン圧制御弁
131:第一ライン圧
135:基準圧制御弁
136:基準圧
137:本体部収容室(第二油室)
140:第二ライン圧制御弁
141:第二ライン圧
EX:排出(ドレイン)
Claims (5)
- 回転電機に駆動連結される入力部材と、車輪に駆動連結される出力部材と、前記入力部材を内燃機関に選択的に駆動連結する第一係合装置と、前記入力部材と前記出力部材とを結ぶ動力伝達経路に設けられた流体継手と、を備えた車両用駆動装置であって、
前記第一係合装置は、第一摩擦部材と、当該第一摩擦部材を押圧する第一ピストンと、前記第一摩擦部材が収容されるとともに、油圧が供給されて前記第一ピストンにおける作動用の油圧が作用する側とは反対側に油圧を作用させるように形成された第一油室と、を備え、
前記流体継手は、当該流体継手の本体部を収容する本体部収容室に、前記入力部材側に駆動連結される継手入力側部材と前記出力部材側に駆動連結される継手出力側部材とを直結する第二係合装置の係合状態を油圧により制御するための第二油室を備え、
前記第一油室に供給する油圧である第一油室油圧を制御する第一油圧制御弁と、前記第二油室に供給する油圧である第二油室油圧を前記第一油室油圧とは独立して制御する第二油圧制御弁と、を備える車両用駆動装置。 - 前記第一油圧制御弁から前記第一油室へ供給された油圧を、当該第一油室から排出するための排出油路に、流量を絞る絞り部を備える請求項1に記載の車両用駆動装置。
- 前記第一係合装置は、前記第一ピストンが前記第一摩擦部材を係合側に押圧するように所定の初期係合荷重で前記第一ピストンを付勢する付勢機構を備え、
前記第一油圧制御弁は、前記初期係合荷重より大きい荷重で前記第一ピストンを係合解除側に押圧する油圧を前記第一油室に発生させるように、前記第一油室油圧を制御する請求項1又は2に記載の車両用駆動装置。 - 油圧ポンプの出力圧を第一ライン圧として制御する第一ライン圧制御弁と、前記第一ライン圧を更に減圧し、第二ライン圧として制御する第二ライン圧制御弁と、を備え、
前記第一油圧制御弁は、前記第一ライン圧制御弁により制御された前記第一ライン圧の油の供給を受けて前記第一油室油圧の油を前記第一油室に供給し、
前記第二油圧制御弁は、前記第二ライン圧制御弁により制御された前記第二ライン圧の油の供給を受けて前記第二油室油圧の油を前記第二油室に供給する請求項1から3のいずれか一項に記載の車両用駆動装置。 - 前記第二係合装置は、第二摩擦部材と、当該第二摩擦部材を押圧する第二ピストンとを備え、
前記第二油室は、その中に前記第二摩擦部材及び前記流体継手の前記継手入力側部材及び前記継手出力側部材が収容されるとともに、油圧が供給されて前記第二ピストンにおける作動用の油圧が作用する側とは反対側に油圧を作用させるように形成されている請求項1から4のいずれか一項に記載の車両用駆動装置。
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US8845484B2 (en) | 2014-09-30 |
JP2012171372A (ja) | 2012-09-10 |
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DE112012000391B4 (de) | 2016-03-10 |
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CN103347725A (zh) | 2013-10-09 |
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