WO2011062191A1 - 車両用駆動装置 - Google Patents
車両用駆動装置 Download PDFInfo
- Publication number
- WO2011062191A1 WO2011062191A1 PCT/JP2010/070485 JP2010070485W WO2011062191A1 WO 2011062191 A1 WO2011062191 A1 WO 2011062191A1 JP 2010070485 W JP2010070485 W JP 2010070485W WO 2011062191 A1 WO2011062191 A1 WO 2011062191A1
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- Prior art keywords
- clutch
- drum
- pressure chamber
- liquid
- chamber
- Prior art date
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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
- F16D25/00—Fluid-actuated clutches
- F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
- 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
- F16D25/0638—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 with more than two discs, e.g. multiple lamellae
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
- B60K6/40—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the assembly or relative disposition of components
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
- B60K6/48—Parallel type
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
- B60L15/00—Methods, circuits, or devices for controlling the traction-motor speed of electrically-propelled vehicles
- B60L15/20—Methods, circuits, or devices for controlling the traction-motor speed of electrically-propelled vehicles for control of the vehicle or its driving motor to achieve a desired performance, e.g. speed, torque, programmed variation of speed
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
- B60L50/00—Electric propulsion with power supplied within the vehicle
- B60L50/10—Electric propulsion with power supplied within the vehicle using propulsion power supplied by engine-driven generators, e.g. generators driven by combustion engines
- B60L50/16—Electric propulsion with power supplied within the vehicle using propulsion power supplied by engine-driven generators, e.g. generators driven by combustion engines with provision for separate direct mechanical propulsion
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- 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
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
- F16D48/04—Control by fluid pressure providing power assistance
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
- B60K6/48—Parallel type
- B60K2006/4825—Electric machine connected or connectable to gearbox input shaft
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
- B60L2240/00—Control parameters of input or output; Target parameters
- B60L2240/40—Drive Train control parameters
- B60L2240/48—Drive Train control parameters related to transmissions
- B60L2240/486—Operating parameters
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
- B60L2240/00—Control parameters of input or output; Target parameters
- B60L2240/40—Drive Train control parameters
- B60L2240/50—Drive Train control parameters related to clutches
- B60L2240/507—Operating parameters
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- 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
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
- F16D2048/0257—Hydraulic circuit layouts, i.e. details of hydraulic circuit elements or the arrangement thereof
- F16D2048/0263—Passive valves between pressure source and actuating cylinder, e.g. check valves or throttle valves
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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
- F16D2500/10—System to be controlled
- F16D2500/102—Actuator
- F16D2500/1021—Electrical type
- F16D2500/1023—Electric motor
- F16D2500/1024—Electric motor combined with hydraulic actuation
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/62—Hybrid vehicles
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/64—Electric machine technologies in electromobility
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/70—Energy storage systems for electromobility, e.g. batteries
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/7072—Electromobility specific charging systems or methods for batteries, ultracapacitors, supercapacitors or double-layer capacitors
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/72—Electric energy management in electromobility
Definitions
- the present invention relates to a drive device for a vehicle.
- the present invention is applicable to, for example, a hybrid vehicle having an engine and a traveling motor as a vehicle drive source, or a vehicle not having a traveling motor but having an engine but not the traveling motor.
- Patent Documents 1 and 2 are for vehicles having an engine, a transmission to which driving force of an output shaft of the engine is transmitted, and a clutch device provided between the output shaft of the engine and an input shaft of the transmission.
- a drive is disclosed.
- the clutch device has a first clutch portion provided on the output shaft side of the engine and a second clutch portion provided on the input shaft side of the transmission. The clutch device engages the first clutch portion and the second clutch portion to transmit the driving force of the engine to the transmission, and releases the engagement of the first clutch portion and the second clutch portion to drive power. It is possible to switch to a blocking state in which the transmission of the
- the present invention has been made in view of the above-described circumstances, and an object of the present invention is to provide a vehicle drive device that is advantageous for downsizing of the device in the axial direction.
- the drive device for vehicles concerning mode 1 is an engine with an output axis, A transmission having an input shaft having an axis and transmitting a driving force of the output shaft of the engine and connected to wheels; It has a first clutch portion provided between the output shaft of the engine and the input shaft of the transmission and provided on the output shaft side of the engine, and a second clutch portion provided on the input shaft side of the transmission.
- a clutch device that can be switched to a disconnection state that shuts off the And a clutch operating mechanism that switches the connection state and the disconnection state of the clutch device by supplying and discharging a liquid.
- the clutch operating mechanism includes (i) a clutch drum fixed to the input shaft and supporting the second clutch portion and having a drum chamber, and (ii) the clutch being surrounded by the clutch drum and closing the opening of the drum chamber A fixed plate fixed to the drum, and (iii) a hydraulic pressure chamber which is surrounded by the clutch drum and generates a fluid pressure for switching the clutch device from the connection state to the disconnection state, and the spring chamber; A movable piston, and (iv) a biasing element provided inside the spring chamber to be surrounded by the clutch drum and biasing the piston to switch the clutch device from the disconnected state to the connected state .
- the biasing element, the piston and the fixed plate are incorporated in this order in the space surrounded by the clutch drum as the axis extends toward the clutch device along the extending direction It is done.
- the clutch drum is (i) a cylindrical fixing portion fixed to the outer peripheral portion of the input shaft; and (ii) radially outward from the fixing portion (Iii) extending radially outward from the inner cylindrical portion; and (iv) extending from the first cylindrical portion along the axis of the input shaft.
- a second extending portion provided, and an outer cylinder portion formed along the axis of the input shaft from the second extending portion and holding the second clutch portion, (Iv)
- the outer cylindrical portion, the inner cylindrical portion, and the second extending portion partition the drum chamber, and (v) the fixed cylindrical portion, the inner cylindrical portion, and the first extending portion rotatably support the clutch drum (Iv)
- the drum chamber and the bearing chamber are arranged in parallel in the radial direction of the input shaft, and the bearing chamber extends in the radial direction of the input shaft more than the drum chamber. It is arranged on the inner circumference side.
- the case further including the case for accommodating the clutch drum is provided, and the case extends radially inward toward the input shaft And a fixed cylindrical portion provided on the wall and extended along the axis of the input shaft, the fixed cylindrical portion rotatably supporting the clutch drum, and the liquid supply It has a flow path connected to the source to supply liquid to the fluid pressure chamber.
- the fixed plate has a check valve facing the clutch device, and the check valve establishes communication between the fluid pressure chamber and the outside and clutches the liquid It has a valve port for discharging to the device and a valve body capable of opening and closing the valve port.
- the liquid supplied to the clutch operating mechanism is further leaked to supply the liquid to at least one of the first clutch portion and the second clutch portion. Liquid supply unit.
- the liquid supply portion when the liquid is supplied to the fluid pressure chamber and pressurized, causes the liquid to leak from the fluid pressure chamber and / or the flow path. It supplies to at least one of the 1st clutch part and the 2nd clutch part.
- a driving motor that can also serve as a generator is provided in the driving force transmission path that connects the clutch device and the transmission.
- the stator has a rotor that rotates with respect to the stator and is connected to the input shaft of the transmission, and the stator and the rotor are coaxially disposed on the outer peripheral side of the clutch device. The liquid supplied to at least one of the two clutch parts splashes toward the stator and the rotor.
- the seal member formed of the seal material for sealing the liquid in the fluid pressure chamber or the flow passage is provided, and the seal member is an increase in the fluid pressure chamber. It has a passage which allows supply of at least one of the first clutch portion and the second clutch portion of a portion of the liquid supplied to the fluid pressure chamber and / or the flow passage with pressure.
- the liquid storage portion for storing liquid is provided, and when the rotor of the traveling motor rotates, the rotor is stored in the liquid storage portion The liquid is splashed to at least one of the first clutch and the second clutch portion.
- the vehicle drive device includes: an input member rotatably coupled to the drive source; An axial member disposed coaxially with the input member and connected to the transmission; A first clutch portion movably engaged along the axis with one of the input member and the axial member; A second clutch portion, which is disposed so as to be alternately in contact with and separated from the first clutch portion, and movably engaged with the other of the input member and the other axial member along the axis; A clutch drum fixed to the shaft-like member and movably supporting the second clutch portion along the axis and having a bottom portion; A plate fixed to the clutch drum; A piston which is movably supported along the axis by the clutch drum and presses the first clutch portion and the second clutch portion; A spring chamber defined between one end of the piston and the bottom of the clutch drum; An urging member provided in the spring chamber for urging the piston toward the first clutch portion and the second clutch portion; A hydraulic pressure chamber defined between the other end of the piston and the plate; The pressing of the piston biased by the biasing
- the clutch drum includes a drum chamber surrounded by the clutch drum, and a fixed plate surrounded by the clutch drum and fixed to the clutch drum so as to close the opening of the drum chamber.
- a piston which is surrounded by a clutch drum and which divides the drum chamber into a hydraulic pressure chamber for generating a fluid pressure for switching the clutch device from the connection state to the disengagement state and a spring chamber, and which can move along the axis;
- a biasing element provided within the spring chamber for biasing the piston in a direction to bring the clutch device into the disengaged state.
- the fixed plate, the piston and the biasing element are assembled inside the clutch drum so as to be surrounded by the clutch drum in this manner. For this reason, it is advantageous to the miniaturization of the present device in the axial direction. In particular, it is advantageous to miniaturize the device in the axial direction as compared to the case where the biasing element is assembled in series outside the clutch drum.
- the biasing element, the piston and the fixed plate are built in this order in the space surrounded by the clutch drum as the axis extends toward the clutch device.
- the clutch drum incorporates the biasing element, the piston, and the fixed plate, which is advantageous for downsizing the present device in the axial direction.
- the springs are assembled in series outside the clutch drum, it is advantageous to miniaturize the device in the axial direction.
- the clutch drum includes the cylindrical fixing portion fixed to the outer peripheral portion of the input shaft, and the first extending portion extending radially outward from the fixing portion.
- An inner cylindrical portion formed from the first extending portion along the axis of the input shaft; a second extending portion extending radially outward from the inner cylindrical portion; and a second extending portion And an outer cylinder formed along the axis of the input shaft.
- the outer cylindrical portion, the inner cylindrical portion, and the second extending portion define a ring-shaped drum chamber.
- the fixed cylindrical portion, the inner cylindrical portion, and the first extension portion define a ring-shaped bearing chamber in which a bearing for rotatably supporting the clutch drum is disposed.
- the drum chamber and the bearing chamber are juxtaposed in the radial direction of the input shaft, which is advantageous for the miniaturization of the device in the axial direction. Furthermore, the bearing chamber is disposed radially inward of the drum chamber in the radial direction of the input shaft, and the drum chamber is disposed radially outward of the bearing chamber in the radial direction of the input shaft. As a result, the distance from the axis can be increased for the hydraulic chamber of the drum chamber, the volume of the hydraulic chamber can be increased, and it is advantageous to increase the hydraulic pressure of the hydraulic chamber which can operate the clutch device in the closing direction.
- the vehicle drive device further includes a case that is housed so as to surround the clutch drum.
- the case has a wall extending radially inward toward the input shaft, and a fixed cylindrical portion provided on the wall and extending along the axis of the input shaft.
- the fixed cylindrical portion rotatably supports the clutch drum, and has a flow path that is connected to the liquid supply source and supplies the liquid to the fluid pressure chamber.
- the clutch drum has the function of supporting the clutch drum on the case and the function of forming the flow path, which is advantageous for downsizing of the device.
- the fixed plate has a check valve that faces the clutch device, and the check valve causes the fluid pressure chamber to communicate with the outside and the fluid that has centrifugal pressure. It has a valve port which makes it discharge to a clutch apparatus, and a valve element which can open and close a valve port.
- the centrifugal fluid pressure in the fluid pressure chamber is increased.
- the biasing force that biases the piston in the direction in which the clutch device is connected is influenced. As a result, the response of switching the clutch device from the disconnected state to the connected state may be reduced.
- the liquid present in the fluid pressure chamber from the valve port and to minimize the influence of the centrifugal fluid pressure in the fluid pressure chamber. Therefore, the liquid that becomes the centrifugal fluid pressure in the fluid pressure chamber is discharged from the valve port of the check valve, and the centrifugal fluid pressure in the fluid pressure chamber is suppressed as much as possible. In this case, the biasing force for biasing the piston in the direction in which the clutch device is connected is favorably maintained. Further, when the pressure in the fluid pressure chamber is increased to switch the clutch device from the connection state to the disconnection state, the valve body of the check valve closes the valve port due to the pressure increase in the fluid pressure chamber.
- the pressure increase speed of the fluid pressure chamber can be secured, and the clutch device can be rapidly switched from the connected state to the disconnected state.
- the present device when the present device is applied to a hybrid car having both an engine and a motor, the engine serving as a load at the time of power regeneration can be quickly disconnected from the transmission, so that the regeneration efficiency can be improved.
- the liquid supplied to the clutch operation mechanism is further leaked and supplied to at least one of the first clutch portion and the second clutch portion for lubrication or cooling. It has a liquid supply unit. For this reason, a lubricating or cooling liquid can be interposed between the frictional engagement surface of the first clutch portion and the frictional engagement surface of the second clutch portion. As a result, seizing of the frictional engagement surface of the first clutch portion and the frictional engagement surface of the second clutch portion is suppressed. As a result, the durability and the life of the clutch can be further improved.
- the liquid supply portion when the liquid is supplied to the fluid pressure chamber and pressurized, the liquid supply portion causes the liquid to leak from the fluid pressure chamber and / or the flow path. It supplies to at least one of the 1st clutch part and the 2nd clutch part.
- the liquid supply unit supplies the lubricating or cooling liquid to at least one of the first clutch unit and the second clutch unit at the time of pressure increase. For this reason, a lubricating or cooling liquid can be interposed between the frictional engagement surface of the first clutch portion and the frictional engagement surface of the second clutch portion. As a result, seizing of the frictional engagement surface of the first clutch portion and the frictional engagement surface of the second clutch portion is suppressed. As a result, the durability and the life of the clutch can be further improved.
- the driving motor capable of double use as a generator is provided in the driving force transmission path connecting the clutch device and the transmission, and the driving motor includes the stator, the stator And a rotor connected to the input shaft of the transmission, and the stator and the rotor are coaxially disposed on the outer peripheral side of the clutch device, and the first clutch portion and the second clutch portion The liquid supplied to at least one of them splashes toward the stator and the rotor.
- a driving motor capable of double use as a generator is provided in a driving force transmission path connecting the clutch device and the transmission.
- the driving force of the traveling motor is transmitted to the input shaft of the transmission to input the input shaft. It can be rotated. In this case, it is possible to cause the vehicle to travel by the rotational drive force of the traveling motor while stopping the driving of the engine. Furthermore, since the stator and the rotor are coaxially arranged on the outer peripheral side of the clutch device, the liquid supplied to at least one of the first clutch portion and the second clutch portion scatters toward the stator and the rotor can do. Therefore, the stator and the rotor can be cooled, and the durability can be improved.
- the seal member formed of the seal material for sealing the liquid in the fluid pressure chamber or the flow passage is provided, and the seal member causes pressure increase in the fluid pressure chamber.
- a passage is provided to supply a portion of the liquid supplied to the fluid pressure chamber and / or the flow path toward at least one of the first clutch portion and the second clutch portion.
- a part of the liquid supplied to the fluid pressure chamber and / or the flow passage along with the pressure increase in the fluid pressure chamber is transmitted to at least one of the first clutch portion and the second clutch portion via the passage of the seal member. It can be supplied toward one side.
- Such a simple configuration can prevent seizing of the clutch device.
- the liquid storage unit for storing the liquid is provided, and when the rotor of the traveling motor rotates, the rotor at least holds the liquid stored in the liquid storage unit. 1 Bounce on one of the clutch and the second clutch.
- the liquid reservoir can store the liquid.
- the rotor can splash the liquid stored in the liquid reservoir flow portion onto at least one of the first clutch portion and the second clutch portion. For this reason, the burn-in of the first clutch portion and the second clutch portion is further suppressed.
- the lubricity can be enhanced by bouncing on bearings and the like.
- the first clutch portion and the clutch portion are brought into pressure contact with each other by the pressing of the piston biased by the biasing member.
- the pressure of the oil supplied into the fluid pressure chamber causes the piston to move away from the first clutch portion and the second clutch portion against the biasing force of the biasing member.
- FIG. 1 is a cross-sectional view of an upper half of a vehicle drive device according to a first embodiment.
- FIG. 2 is a cross-sectional view of the lower half of the vehicle drive device according to the first embodiment.
- FIG. 2 is a partial cross-sectional view showing the vicinity of a fluid pressure chamber of a vehicle drive device according to a first embodiment.
- 1 is a system diagram of a drive system for a vehicle according to a first embodiment. It is a fragmentary sectional view which concerns on Embodiment 1 and shows oil supply part vicinity.
- FIG. 7 is a plan view of the first seal member according to the first embodiment. It is a figure which concerns on Embodiment 2, and expands and shows recessed part vicinity of a 1st sealing member.
- Embodiment 3 It is a figure which concerns on Embodiment 3 and expands and shows recessed part vicinity of a 1st sealing member. It is a figure which concerns on Embodiment 4 and expands and shows recessed part vicinity of a 1st sealing member. It is a fragmentary sectional view which concerns on Embodiment 5, and shows oil supply part vicinity.
- FIG. 1 shows a cross-sectional view of the upper half of the vehicle drive system
- FIG. 2 shows a cross-sectional view of the lower half
- FIG. 3 shows an enlarged main part of the lower half
- FIG. 4 shows a block diagram representing a vehicle drive system.
- the vehicle drive system includes a driving motor formed of an engine 1 functioning as a first drive source, a clutch device 2 and an electric motor functioning as a second drive source (hereinafter also referred to as a motor). 8), a transmission 6, and a control device 7.
- the control device 7 controls the engine 1, the motor 8, the transmission 6, the control valve 70, and the oil pump 78.
- the motor 8 can also function as a generator that regenerates electrical energy at the time of deceleration of the vehicle or the like.
- various structures are adopted to enhance the regeneration efficiency. Since the oil pump 78 is electrically driven, it can exert a pump action of supplying oil (lubricating oil) even if the engine 1 is not driven.
- the solid arrows indicate the hydraulic pressure passages connected to the oil pump 78, and the broken lines indicate signal lines connected to the control device 7.
- the engine 1 has an output shaft 10 rotated about the axis P1 by the engine 1, and a ring-shaped flywheel 14 coaxially connected to the output shaft 10 by a fixture 10w. .
- a ring gear 12 formed on an outer peripheral portion of the flywheel 14 meshes with a drive shaft of a starter motor (not shown).
- the torque converter 61 provided in the transmission 6 has an input shaft 60 (axial member) rotated by the driving force of the output shaft 10 of the engine 1.
- the input shaft 60 has an axis P1 and is connected to a traveling wheel via a transmission gear mechanism (not shown) of the transmission 6 to rotate the traveling wheel (not shown). Description of the clutch device 2 will be added.
- the clutch device 2 constitutes a wet multi-plate clutch, and is held by an input member 20, a clutch drum 22, a friction plate 23 functioning as a first clutch portion held by the input member 20, and the clutch drum 22. It has the separate plate 24 which functions as a 2nd clutch part.
- the friction plate 23 and the separate plate 24 are alternately disposed facing each other, and can be crimped to each other to be in an engaged state (connected state) in a crimped state, and disengaged from each other in a crimped state. Can be shut off).
- Each of the friction plate 23, the separate plate 24, the input member 20, and the clutch drum 22 is coaxially disposed so as to make one rotation around the axis P1 of the input shaft 60.
- the input member 20 is connected to the flywheel 14 via a damper 13.
- the output shaft 10, the flywheel 14, the damper 13, the input member 20, and the friction plate 23 integrally rotate around the axis P1.
- the input member 20 extends radially outward from the shaft end of the shaft portion 201 on the transmission 6 side of the shaft portion 201 coaxially arranged with the output shaft 10 and the shaft portion 201.
- the ring-shaped extending portion 202 and the ring-shaped holding portion 203 which holds the friction plate 23 and is formed along the axis P1.
- a plurality of friction plates 23 are fitted to the outer peripheral portion of the holding portion 203 so as to be relatively movable along the axis P1 while restricting relative rotation.
- the clutch drum 22 is spline fitted to the outer peripheral portion of the input shaft 60 of the transmission 6 and rotates integrally with the input shaft 60.
- an outer cylindrical portion 224 is an outer cylindrical portion 224.
- a plurality of separate plates 24 are fitted to the distal end portion of the outer cylindrical portion 224 so as to be relatively movable along the axis P1 while restricting relative rotation.
- the inner cylindrical portion 222, the second extending portion 223 and the outer cylindrical portion 224 form a drum chamber 230.
- the fixed cylindrical portion 220, the inner cylindrical portion 222, the outer cylindrical portion 224, and the drum chamber 230, which constitute the clutch drum 22, are formed so as to make one rotation around the axis P1.
- the inner cylindrical portion 222 has a piston stopper 229.
- the first extension 221 of the clutch drum 22 is applied close to the extension 202 of the input member 20 of the clutch device 2 via the thrust bearing 209. This is advantageous for shortening the axial length size of this device.
- the spring 33, the piston 32, the fixed plate 31, and the separate plate 24 are disposed in a space surrounded by the outer cylinder portion 224 of the clutch drum 22 as it goes to the clutch device 2 along the direction in which the axis P1 extends. ) Are housed and housed in this order. That is, the spring 33, the piston 32, the fixed plate 31, and the separate plate 24 are accommodated in the axial length dimension of the clutch drum 22.
- the clutch device 2 is switchable between a connected state in which the driving force of the engine 1 is transmitted to the input shaft 60 of the transmission 6 and a shut-off state in which the transmission of the driving force of the engine 1 is shut off.
- a connected state in which the driving force of the engine 1 is transmitted to the input shaft 60 of the transmission 6
- a shut-off state in which the transmission of the driving force of the engine 1 is shut off.
- the friction plate 23 and the separate plate 24 adjacent to each other are crimped and engaged with each other, and the driving force of the engine 1 can be transmitted to the input shaft 60 of the transmission 6.
- the shutoff state the friction plates 23 and the separate plates 24 adjacent to each other are disengaged, and the transmission of the driving force from the engine 1 to the transmission 6 is shut off.
- the clutch device 2 is a normally closed type, and in a normal state in which the driving force of the engine 1 is transmitted to the transmission 6, the connection state where the friction plate 23 and the separate plate 24 are crimped by the spring force of the spring 33 is maintained. There is. For this reason, in a normal state, oil pressure for pressing adjacent friction plates 23 and separate plates 24 to each other is not particularly required, and energy saving can be achieved. Furthermore, even when a failure occurs in the hydraulic system, the friction plate 23 and the separate plate 24 that make up the clutch device 2 are crimped and connected, so the driving force of the engine 1 is changed. The advantage of being able to be transmitted to the aircraft 6 and having the vehicle travel is obtained.
- the clutch operating mechanism 3 for operating the clutch device 2 will be further described.
- the clutch operating mechanism 3 includes a fixing plate 31 fixed to a retaining groove on the outer peripheral side of the inner cylindrical portion 222 of the clutch drum 22 via a retaining member 31 x such as a C ring, and a drum chamber 230.
- a spring 33 formed by a coil spring that functions as a biasing element disposed between the piston 32 and the second extending portion 223 of the clutch drum 22 so as to be movable along the axis P1.
- a fluid pressure chamber 34 formed between the surface 310 of the fixed plate 31 on the side opposite to the clutch device 2 and the pressure surface 325 of the piston 32 on the clutch device 2 side, And 35 (see FIG. 3).
- the fixed plate 31 closes the space on the side of the clutch device 2 in the drum chamber 230.
- a piston 32 is provided in the drum chamber 230. Therefore, the drum chamber 230 is divided into a fluid pressure chamber 34 to which a fluid pressure for switching the clutch device 2 from the connection state to the disconnection state is supplied, and a spring chamber 39 in which the spring 33 is accommodated.
- the piston 32 has a movable inner cylindrical portion 321 and a movable outer cylindrical portion 322 coaxially formed with each other, and a pressing portion 323 connecting the both in the radial direction.
- the movable outer cylinder 322 of the piston 32 moves the separate plate 24 of the clutch device 2 toward the friction plate 23 Let it be crimped.
- the piston 32 moves in the direction of the arrow F2 (see FIG. 3, the release direction for releasing the engagement of the clutch device 2)
- the movable outer cylinder 322 of the piston 32 separates from the separate plate 24 of the clutch device 2. Then, the pressure contact between the separator plate 24 and the friction plate 23 is released.
- the fluid pressure chamber 34, the piston 32, and the drum chamber 230 are formed in a ring shape around the axis P1 on the outer peripheral side of the axis P1.
- the plurality of springs 33 are arranged at substantially equal intervals in the circumferential direction around the axis P1. As shown in FIG. 3, one end of the spring 33 is seated on the second extending portion 223 of the clutch drum 22, and the other end is seated on the spring receiving recess 36 formed on the back surface of the piston 32. Detachment is suppressed. As can be understood from FIG. 3, the spring 33 biases the piston 32 toward the fixed plate 31 along the direction of the arrow F1.
- the clutch device 2 can be switched from the connected state to the disconnected state, power transmission between the engine 1 and the transmission 6 can be cut off, and the regeneration efficiency can be enhanced.
- the friction plate 23 and the separate plate 24 of the clutch device 2 are crimped to each other, and the clutch device 2 is maintained in the connected or semi-connected state.
- the driving force of the output shaft 10 of the engine 1 is transmitted to the input shaft 60 of the transmission 6 via the clutch device 2.
- the flow path 35 includes a first flow path 351 formed inside the fixed cylindrical portion 94 of the second case 92, which is a part of the case 9 described later, and the outer peripheral surface of the fixed cylindrical portion 94.
- the inner cylindrical portion 222 of the clutch drum 22 is formed by an annular groove 352 which is annularly formed so as to open at the front end, and a through hole 353 which penetrates in the thickness direction of the inner cylinder portion 222 and opens in the annular groove 352.
- the first channel 351 is formed by using the fixed cylindrical portion 94 which is a part of the case 9 (see FIG. 3).
- the other end of the first flow path 351 is connected to the oil pump 78 via the control valve 70.
- the control valve 70 is switched between the first position 71 and the second position 72 by a solenoid and a spring.
- the first position 71 has a passage 73a for communicating the flow passage 35 and the oil pump 78, and a passage 73b for communicating the flow passage 35 and the oil reservoir 79 and having a throttle 73k.
- the second position 72 includes a passage 73 c communicating the flow passage 35 and the oil pump 78, and a passage 73 e communicating the flow passage 35 and the oil reservoir 79.
- the fluid pressure chamber 34 communicates with the oil reservoir 79 via the first flow path 351.
- the oil in the pressure chamber 34 is returned to the oil reservoir 79 via the through hole 353, the annular groove 352, the first flow passage 351, and the passage 73e. Since the passage 73e is not provided with a throttle, the rate of oil discharge from the fluid pressure chamber 34 can be increased. In this case, the responsiveness of switching the clutch device 2 from the disconnected state to the connected state can be enhanced, so that the driving force of the engine 1 can be rapidly transmitted to the transmission 6. Since the oil pump 78 is electrically driven as described above, oil can be supplied regardless of the drive of the engine 1.
- the control valve 70 and the oil pump 78 are fixed to the outer peripheral side of the case 9 and mounted.
- the clutch device 2 described above is a normally closed type, and normally, the fluid pressure chamber 34 is not filled with oil, and the friction plate 23 and the separate plate 24 adjacent to each other are crimped to each other by the biasing force of the spring 33 As a result, the output shaft 10 of the engine 1 and the input shaft 60 of the transmission 6 are connected via the clutch device 2.
- the output shaft 10 rotates, so the input member 20 rotates, and the friction plate 23 and the separate plate 24 in the crimped state rotate around the axis P1, and the clutch drum 22 Rotating with 82, the input shaft 60 of the transmission 6 is rotated, which in turn rotates the traveling wheels.
- the responsiveness of switching the clutch device 2 from the connected state to the disconnected state can be enhanced, and the responsiveness of regeneration control can be enhanced. It can contribute to increasing the amount of electricity stored in the fuel and can contribute to the improvement of the fuel efficiency of the vehicle.
- the spring 33 for biasing the piston 32 it may be considered to be a plate spring or a disc spring instead of a coil spring.
- the spring load is likely to change substantially in a quadratic curve with respect to deflection, and has a high change rate.
- the torque capacity of the clutch device 2 can not be secured when the friction plate 23 and the separate plate 24 constituting the clutch device 2 change over time or wear. If the spring load changes rapidly, it becomes difficult to control the transmission torque by supplying oil to the fluid pressure chamber 34 to control the hydraulic pressure of the fluid pressure chamber 34.
- the spring 33 is a coil spring as in the present embodiment
- the spring load changes substantially linearly with respect to the deflection as compared with a plate spring or a disc spring.
- the hydraulic control of the hydraulic pressure chamber 34 has the advantage of being able to accurately control the transmission torque of the clutch device 2.
- the coil springs are advantageous for being disposed in a narrow space, can be disposed in large numbers, can increase the total spring load, and can contribute to maintaining the clutch device 2 in the connected state with a large spring load.
- the spring 33 is not limited to a coil spring, and may be a plate spring or a disc spring.
- a motor 8 is provided in a driving force transmission path connecting the clutch device 2 and the transmission 6.
- the motor 8 has a stator 80 and a rotor 82.
- the stator 80 is fixed to the inner peripheral side of the second case 92, and has an excitation winding 80c wound around an iron core.
- the rotor 82 is coaxially disposed on the inner peripheral side of the stator 80 with a gap 80x.
- the rotor 82 is connected to the outer peripheral side of the outer cylindrical portion 224 of the clutch drum 22, so the rotor 82 and the clutch drum 22 integrally rotate around the axis P1.
- the case 9 encloses the clutch device 2, the clutch operating mechanism 3, the motor 8, the torque converter 61, and the like.
- the case 9 includes, from the engine 1 side, a first case 91, a second case 92 connected to the first case 91, and a third case 93 connected to the second case 92.
- the first case 91 has a first wall 910 extending radially inward.
- the second case 92 has a second wall 920 extending radially inward.
- the inner circumferential portion of the second wall 920 has a fixed cylindrical portion 94 extending along the axis P1.
- the stator 80 of the motor 8 is fixed to the inside of the outer wall cylindrical portion 92 x of the second case 92.
- the first wall 910 and the second wall 920 face each other.
- a bearing 96 a is interposed between the fixed cylindrical portion 94 of the second wall 920 and the input member 60 of the transmission 6. Therefore, the clutch drum 22 and the input shaft 60 can integrally rotate around the axis P1 with respect to the fixed cylindrical portion 94 of the second case 92.
- the bearing 96a is engaged with the fixed cylindrical portion 94 on the case 9 side by the engaging member 96x.
- a bearing 96 c is interposed between the inner circumferential portion of the first wall 910 of the first case 91 and the input member 20. Therefore, the input member 20 can rotate integrally with the first case 91 about the axis P1.
- a bearing 96 e is interposed between the output shaft 10 and the shaft portion 201.
- the clutch device 2 and the clutch operating mechanism 3 are coaxially disposed on the inner peripheral side of the motor 8. Therefore, the clutch device 2 and the clutch operating mechanism 3 can be disposed on the inner peripheral side of the motor 8 while effectively utilizing the width D in the axial direction of the motor 8 (see FIG. 1). In this case, the size can be reduced along the direction of the axis P1.
- the electric oil pump 78 powered by the battery operates to supply hydraulic pressure to the hydraulic pressure chamber 34 and clutch While the device 2 is in the disconnected state, a current flows through the excitation winding 80c of the motor 8 to rotate the rotor 82.
- the clutch drum 22 connected to the rotor 82 rotates about the axis P1
- the traveling wheels rotate via the transmission 6, and the vehicle starts moving.
- the engine 1 may not start and may be stopped. In this case, the vehicle is started only by the driving force of the motor 8.
- the oil pump 78 is operated by the command from the control device 7 to generate the hydraulic pressure, and the control valve 70 is switched to the first position 71.
- the fluid is supplied to the flow passage 35 and the fluid pressure chamber 34 via the passage 73 a at the 1 position 71.
- the hydraulic pressure in the fluid pressure chamber 34 rises, the piston 32 moves in the direction of the arrow F2, and the normally closed type clutch device 2 is switched from the connected state to the disconnected state.
- the engine 1, the flywheel 14 and the like serving as loads are separated from the motor 8 and the transmission 6, and the startability of the vehicle is enhanced.
- the engine 1 when the vehicle accelerates or climbs, the engine 1 is preferably driven.
- the accelerator pedal when the accelerator pedal is depressed to accelerate or climb the throttle and the throttle is opened more than a predetermined opening degree, the fuel injection device is activated and the not-illustrated spark plug is ignited. Further, a drive shaft of a starter motor (not shown) is driven. As a result, the ring gear 12 of the flywheel 14 engaged with the drive shaft of the starter motor is rotated together with the flywheel 14 and the output shaft 10 to start the engine 1.
- the clutch device 2 is maintained in the connected state.
- control valve 70 is switched to the second position 72, and the oil in the fluid pressure chamber 34 is discharged to the oil reservoir 79 via the flow path 35 and the passage 73e at the second position 72 of the control valve 70.
- the biasing force of the coil spring 33 overcomes the hydraulic pressure of the fluid pressure chamber 34, and the piston 32 moves in the direction of the arrow F1 together with the separate plate 24, and adjacent friction plates 23 and separate plates 24 constituting the clutch device 2 They are crimped into engagement with one another.
- the rotational driving force of the output shaft 10 of the engine 1 is transmitted to the input shaft 60 of the transmission 6 via the clutch device 2.
- the driving forces of both the engine 1 and the motor 8 are added, and the vehicle travels with a large driving force.
- Adjacent friction plates 23 and separate plates 24 that make up the two are separated from each other and brought into a non-engaged state where they are in a non-crimped state.
- the motor 8 functions as a generator to generate the electric energy.
- the generated electrical energy is stored in the battery.
- the clutch drum 22 is rotated around the axis P1 together with the rotor 82 during traveling of the vehicle and receives a centrifugal force, so even in the hydraulic pressure chamber 34 even when the clutch device 2 is in the connected state. Oil may be left behind. In this case, when oil is excessively left in the fluid pressure chamber 34, centrifugal oil pressure is generated in the fluid pressure chamber 34 by the centrifugal force, and a pressing force may be generated to press the piston 32 in the arrow F2 direction. In this case, the clutch device 2 which should be maintained in the connected state may be in the disconnected state depending on the conditions.
- the fixed plate 31 which comprises the wall which forms the liquid pressure chamber 34 is provided with the single or several check valve 37.
- the check valve 37 has a valve port 370 communicating the fluid pressure chamber 34 with the outside thereof, and a valve body 371 capable of opening and closing the valve port 370.
- the valve port 370 is formed in a tapered shape in which the hydraulic pressure chamber 34 side has a large diameter, and the falling off of the valve body 371 is suppressed.
- oil is supplied to the fluid pressure chamber 34 in order to block the connection between the output shaft 10 of the engine 1 and the input shaft 60 of the transmission 6.
- the valve body 371 closes the valve port 370 and the pressure increase speed of the fluid pressure in the fluid pressure chamber 34 is increased.
- the piston 32 can be pressed by the arrow F2, and the clutch device 2 can be quickly switched to the disengaged state. In this case, the regeneration efficiency can be increased.
- the oil present in the fluid pressure chamber 34 is discharged from the fluid pressure chamber 34 and the centrifugal fluid pressure in the fluid pressure chamber 34 is dissipated as much as possible. Is preferred. This is because the centrifugal oil pressure reduces the biasing force of the spring 33. In this case, since the oil in the fluid pressure chamber 34 is discharged to the oil reservoir 79 via the flow passage 35 by the operation of the control valve 70, the closing force of the valve 371 for closing the valve port 370 is reduced.
- valve body 371 of the check valve 37 moves to the large diameter side of the tapered valve port 370 by centrifugal force to open the valve port 370, and the oil in the fluid pressure chamber 34 is transferred from the valve port 370 to the fluid pressure chamber 34. Can be discharged outward.
- the valve port 370 of the check valve 37 is opposed to the clutch device 2 so that oil can be discharged from the valve port 370 toward the clutch device 2 and the cooling and lubricating properties of the clutch device 2 can be improved. It can be further improved.
- the check valve 37 is disposed on the outer peripheral side in the hydraulic pressure chamber 34 than the intermediate position in the direction perpendicular to the axis P1.
- the clutch drum 22 is fixed to the drum chamber 230 surrounded by the clutch drum 22 and the clutch drum 22 so as to be surrounded by the clutch drum 22.
- the piston 32 which is surrounded by the clutch drum 22 and divides the drum chamber 230 into the hydraulic pressure chamber 34 and the spring chamber 39, and It has a spring 33 (biasing element) which biases the piston 32 in a direction in which the clutch device 2 is brought into the connection state from the disconnected state.
- the fixed plate 31, the piston 32, and the spring 33 are incorporated.
- the spring 33 and the piston 32 are provided in the space surrounded by the outer cylindrical portion 224 of the clutch drum 22 as it goes to the clutch device 2 along the direction in which the axis P1 extends.
- the fixed plate 31 and the separate plate 24 (second clutch portion) are built in this order.
- the clutch drum 22 is a cylindrical fixed cylindrical portion 220, an inner cylindrical portion 222, and an outer portion coaxial with each other from the inside to the outside in the radial direction (direction perpendicular to the axis P1). It has a tube portion 224.
- a ring-shaped bearing chamber 2 s is divided by the fixed cylindrical portion 220, the first extending portion 221, and the inner cylindrical portion 222.
- a ring-shaped bearing 96a and a ring-shaped fixed cylindrical portion 94 are coaxially fitted in the bearing chamber 2s.
- the clutch drum 22 is rotatably supported by the fixed cylindrical portion 94 of the case 9. Furthermore, as shown in FIG.
- a spring 33, a piston 32, and a fixing plate 31 are disposed in the ring-shaped drum chamber 230 partitioned by the inner cylindrical portion 222 and the outer cylindrical portion 224.
- bearing chambers 2 s and drum chambers 230 having different roles are juxtaposed in the radial direction. Therefore, the size of the clutch drum 22 in the axial direction can be shortened. In this case, it is advantageous for shortening the size in the axial direction of the present device.
- the bearing chamber 2s is disposed on the inner peripheral side of the drum chamber 230 in the radial direction of the input shaft 60
- the drum chamber 230 is disposed on the outer peripheral side of the bearing chamber 2s in the radial direction of the input shaft 60.
- the distance from the axis P1 can be increased for the fluid pressure chamber 34 of the drum chamber 230, the volume of the fluid pressure chamber 34 can be increased, and the fluid pressure of the fluid pressure chamber 34 that can operate the clutch device 2 in the closing direction is increased. It is advantageous to As described above, if the responsiveness for interrupting the clutch device 2 is enhanced, the engine serving as a load at the time of power regeneration can be quickly disconnected from the input shaft 60, and the regeneration efficiency can be enhanced.
- the friction plate 23 is And an oil supply unit 100 functioning as a liquid supply unit for supplying oil, which is a liquid for lubrication or cooling, to at least one of the separation plate 24 and the separation plate 24.
- the oil supply unit 100 is configured such that the oil supplied to the annular groove 352 of the flow passage 35 when the fluid pressure chamber 34 and the flow passage 35 are pressurized, and the friction plate 23 of the clutch device 2 switched to the blocking state. It has a function of supplying the separate plate 24.
- FIG. 5 is an enlarged view of FIG.
- the oil supply portion 100 has a minute gap existing between the outer peripheral surface 94 p of the fixed cylindrical portion 94 of the second case 92 and the inner peripheral surface 222 i of the inner cylindrical portion 222 of the clutch drum 22. It is formed. Since the oil supply unit 100 exists around the axis P1, the oil can be discharged as evenly as possible in the circumferential direction. As described above, when the clutch device 2 is switched from the connected state to the disconnected state, oil is supplied to the fluid pressure chamber 34 and the flow passage 35, and the fluid pressure chamber 34 and the flow passage 35 are pressurized.
- the oil supplied to the fluid pressure chamber 34 and the flow path 35 leaks from the oil supply portion 100, and further, radially outward through the guide passage 260 which also serves to reduce the weight of the clutch drum 22 It moves in the A1 direction (see FIG. 3), and further moves in the directions of arrows A2 and A3 (see FIG. 3), and is supplied to the friction plate 23 and the separate plate 24.
- the clutch device 2 is switched to the disengaged state, and the adjacent friction plate 23 and the separate plate 24 slide on each other, but the oil on the friction engagement surface of the friction plate 23 and the friction engagement surface of the separation plate 24 Can be attached, and the friction engagement surface of the friction plate 23 and the friction engagement surface of the separate plate 24 are cooled by oil to prevent seizure.
- the frictional engagement surface of the frictional plate 23 and the frictional engagement surface of the separate plate 24 partially intervene through the minute gap. Slide. In this way, while the plates 23 and 24 facing each other are separated from each other, there is no possibility that the frictional engagement surfaces of the plates 23 and 24 partially contact and slide to cause seizure on the frictional engagement surfaces. I can not say.
- oil lubricant oil supplied to the fluid pressure chamber 34 and the flow passage 35 is The oil leaks in the direction of arrow A1 from the oil supply portion 100, moves radially outward through the guide passage 260 of the clutch drum 22 in the direction of arrows A2 and A3, and further, the frictional engagement surface and separation of the friction plate 23 It can be supplied to the friction engagement surface of the plate 24.
- the clutch device 2 is shut off due to the pressure increase in the hydraulic pressure chamber 34, oil is supplied to the frictional engagement surface of the friction plate 23 and the separate plate 24 adjacent to each other, and oil is applied to the frictional engagement surface. It can be attached well.
- the frictional engagement surface can be cooled by the oil, but even when the frictional engagement surfaces are partially in contact and slide, the lubricity of the frictional engagement surface is good due to the oil lubricity. And the seizure of the frictional engagement surface is suppressed.
- the extension portion 202 of the input member 20 of the clutch device 2 is formed with a guide passage 262 which penetrates the same in the thickness direction and also serves to reduce the weight.
- a plurality of guide passages 262 are formed at intervals in the circumferential direction around the axis P1 of the extending portion 202, and the fixed plate 31 side and the first wall 910 side are communicated.
- the holding portion 203 is formed with a plurality of guide passages 263 penetrating the same in the thickness direction.
- the guide passages 262 and 263 have a function of guiding the oil from the oil supply unit 100 to the plates 23 and 24 of the clutch device 2.
- Oil can be supplied to the friction engagement surfaces of the friction plate 23 and the separate plate 24.
- the clutch device 2 is maintained in the connected state, oil is not actively supplied to the fluid pressure chamber 34 and the flow passage 35, so the fluid pressure chamber 34 and the flow passage 35 are not pressurized. Therefore, there is no supply of oil from the oil supply unit 100 to the clutch device 2.
- the rotor 82 and the stator 80 are coaxially arranged on the outer peripheral side of the friction plate 23 and the separate plate 24. Therefore, the oil that has cooled the friction plate 23 and the separate plate 24 splashes outward by centrifugal force or gravity, and can contact the rotor 82 to improve the cooling performance of the rotor 82. Furthermore, the cooling property of the stator 80 can be enhanced by contacting the stator 80 as well. Since the outer cylindrical portion 224 of the clutch drum 22 is formed at intervals in the circumferential direction of the clutch drum 22 and has engaging groove holes 224p (see FIG. 3) engaged with the separate plate 24, oil is applied to the rotor 82 and the winding 80c. Easy to move towards.
- the gap-like oil supply unit 100 includes the inner peripheral surface 222i of the inner cylindrical portion 222 of the metal clutch drum 22 and the outer peripheral surface of the metal fixed cylindrical portion 94. It is formed between 94p.
- oil from the flow path 35 exists for lubrication, and further, first seal members 11f and 11s are provided.
- the first seal member 11 f and the first seal member 11 s are provided at positions sandwiching the annular groove 352 of the flow path 35. Specifically, the first seal member 11 f is formed closer to the clutch device 2 than the annular groove 352, and the first seal member 11 s is formed at a position farther away from the clutch device 2 than the annular groove 352.
- the first seal members 11f and 11s are formed of a seal material (resin, rubber, sintered material or the like), and are formed in a C ring shape around the axis P1. Therefore, although oil leaks appropriately from the annular groove 352 into the gap-like oil supply unit 100, excessive leakage is suppressed. In this case, the pressure increase in the fluid pressure chamber 34 is not disturbed, and hence the clutch device 2 can be rapidly switched to the disengaged state, and the regeneration efficiency is not impaired.
- a seal material resin, rubber, sintered material or the like
- the first seal members 11 f and 11 s have the same shape and the same material, and have one end 11 e and the other end 11 h so as to form the notch passage 111. It is in the shape of a ring. For this reason, the notch passage 111 serves as a mark, and assembly errors of the first seal members 11 f and 11 s can be suppressed. Furthermore, while sealing the oil, the first seal member 11f allows a portion of the oil to pass through the notch passage 111 and efficiently supplies the frictional engagement surface of the frictional plate 23 and the frictional engagement surface of the separate plate 24. It can be done.
- the first seal members 11 f and 11 s provided in the gap are the same type, and the assembly error is suppressed.
- the first seal member 11f disposed on the side closer to the clutch device 2 is configured to have a C ring shape to enhance oil leakage
- the first seal member 11s disposed on the side farther from the clutch device 2 may be such that the oil leaks little, for example, an O-ring shape.
- the pressure increasing property of the fluid pressure chamber 34 can be enhanced while ensuring the oil supplying property from the oil supplying unit 100 to the clutch device 2.
- the second seal member 12 is interposed between the inner peripheral surface of the fixed plate 31 and the outer peripheral surface of the inner cylindrical portion 222 of the clutch drum 22.
- the third seal member 13 is interposed between the outer peripheral surface of the fixed plate 31 and the inner peripheral surface of the piston 32.
- a fourth seal member 14 is provided between the inner peripheral surface of the piston 32 and the outer peripheral surface of the inner cylindrical portion 222 of the clutch drum 22.
- the fluid pressure chamber 34 is sealed.
- the second seal member 12 positioned closer to the clutch device 2 than the hydraulic pressure chamber 34 in the direction in which the axis P1 extends may be C-ring shaped instead of O-ring shaped. In this case, oil is supplied to the clutch device 2 in the direction of arrow E (see FIG. 5) from the gap 120 formed between the inner peripheral surface 310i of the fixed plate 31 and the outer peripheral surface 222p of the inner cylindrical portion 222 of the clutch drum 22. You can expect to be
- an oil reservoir 79 functioning as a liquid reservoir for storing oil is formed at the bottom of the first case 91 and the second case 92.
- the oil reservoir 79 functions as a reservoir for storing the oil of the oil pump 78.
- the oil level is shown as 79x (see FIG. 2).
- the lower part of the stator 80, the lower part of the winding 80c, and the lower part of the rotor 82 are respectively immersed in oil below the oil level 79x of the oil reservoir 79, and the stator 80, the winding 80c and the rotor 82 are cooled by oil. It can be done. In this case, motor efficiency or power generation efficiency can be enhanced.
- FIG. 1 motor efficiency or power generation efficiency can be enhanced.
- the oil surface 79 x of the oil stored in the oil storage portion 79 is located at a level slightly closer to the inner peripheral side than the outer slide of the rotor 82 in the radial direction. Therefore, excessive immersion of the rotor 82 in oil is suppressed, and excessive rotation resistance of the rotor 82 is suppressed when the rotor 82 rotates, which can contribute to improvement in fuel consumption.
- the rotor 82 rotates so that the rotor 82 is a part of the oil stored in the oil storage portion 79 of the case 9, the friction plate 23 and the separation of the clutch device 2 in the connected state and the disconnected state.
- the plate 24 can be splashed, and further elements such as bearings 96 can be splashed. In this case, it can further contribute to the improvement of cooling, lubrication and durability of the elements such as the friction plate 23, the separate plate 24, the bearings 96a, 96c, 96e etc., and can contribute to the improvement of the motor efficiency or the power generation efficiency.
- the oil supply unit 100 supplies the oil to the friction engagement surface of the friction plate 23 and the friction engagement surface of the separate plate 24.
- oil can be interposed between the frictional engagement surfaces of the friction plate 23 and the separate plate 24.
- the fluid pressure chamber 34 when the fluid pressure chamber 34 is supplied with oil to switch the clutch device 2 from the connection state to the disconnection state, the fluid pressure chamber 34 and the flow passage 35 are pressurized. As a result, the oil supplied to the fluid pressure chamber 34 and the flow path 35 can be effectively supplied to the frictional engagement surface of the friction plate 23 of the clutch device 2 and the frictional engagement surface of the separate plate 24.
- a part of the oil supplied to the hydraulic pressure chamber 34 or the flow passage 35 along with the pressure increase of the hydraulic pressure chamber 34 or the flow passage 35 is set to the notch passage 111 of the first seal member 11f. It is possible to effectively flow out toward the frictional engagement surface of the friction plate 23 and the frictional engagement surface of the separate plate 24.
- the pressure in the fluid pressure chamber 34 and the flow path 35 can be increased by the sealing action of the first seal member 11f, and the oil is made to pass through the notch passage 111 of the first seal member 11f. It can be made to flow effectively towards the frictional engagement surface of separate plate 24.
- the oil supply unit 100 can supply the oil to the friction plate 23 and the separate plate 24 and the friction plate 23.
- the oil can be supplied to the friction plate 23 and the separate plate 24 also when the separate plate 24 is in the half engaged state.
- FIG. 7 shows a second embodiment.
- the present embodiment basically has the same effects as the first embodiment. The following description will focus on the differences.
- the first seal member 11 f that leaks the oil from the gap has a notch passage 111 b.
- the notch passage 111b is formed by the inclined surfaces 111m and 111k that are inclined with respect to the virtual line W.
- the outer peripheral surface 11p of the one end portion 11e is displaced radially inward, it is easy to secure the leakage amount of oil on the outer peripheral surface 11p side. Furthermore, when hydraulic pressure acts on the inclined surfaces 111m and 111k, the passage width of the notch passage 111b is likely to increase. Therefore, it is possible to obtain an advantage that the first seal member 11 f can easily pass a portion of the oil from the notch passage 111 b toward the clutch device 2 while sealing the oil.
- FIG. 8 shows a third embodiment.
- the present embodiment basically has the same effects as the first and second embodiments.
- the following description will focus on the differences.
- the first seal member 11 f has a recess 111 c through which oil can pass.
- the one end 11 e has a protrusion 112 projecting in the circumferential direction.
- the other end 11 h has a slit 113 in which the protrusion 112 is fitted. Even when the pressure in the fluid pressure chamber 34 is increased, the protrusion 112 is fitted in the slit 113, so that the shape of the recess 111c is prevented from being broken, and it is easy to secure the amount of oil leakage from the recess 111c.
- FIG. 9 shows a fourth embodiment.
- This embodiment basically has the same function and effect as the above embodiment. The following description will focus on the differences.
- the first seal member 11f has an O-ring shape.
- a recess 111 d which can leak a part of the oil is formed.
- FIG. 10 shows a fifth embodiment.
- This embodiment basically has the same function and effect as the above embodiment. The following description will focus on the differences.
- the first seal member 11s is provided between the outer peripheral surface 94p of the fixed cylindrical portion 94 of the second case 92 and the inner peripheral surface 222i of the inner cylindrical portion 222 of the clutch drum 22.
- the gap-like oil supply unit 100 is not provided with the first seal member. In this case, the gap can be set appropriately to ensure the oil supply performance from the oil supply unit 100 in the direction of the arrow A1.
- a fourth seal member 14 is provided in a gap between the piston 32 and the inner cylindrical portion 222 of the clutch drum 22.
- the second seal member is not provided in the region WT between the inner cylindrical portion 222 of the clutch drum 22 and the fixed plate 31.
- the seal members 11f and 12 on the clutch device 2 side are not provided. Therefore, while the oil is supplied to the clutch device 2 from both the oil supply unit 100 and the region WT, the sealability of the fluid pressure chamber 34 can be secured by the seal members 11s and 14, and the pressure in the fluid pressure chamber 34 can be increased. , And the clutch device 2 can be switched to the disengaged state.
- the guide passage 260B formed in the clutch drum 22 is formed to be inclined radially outward as it goes to the clutch device 2 side (left direction in FIG. 10) There is. For this reason, the oil on which the centrifugal force acts can be made to pass through the guide passage 260 B and be directed to the clutch device 2.
- the first embodiment described above is applied to a hybrid vehicle having the engine 1 and the motor 8 at the same time, but may be applied to a vehicle equipped with the engine 1 but not the motor 8.
- the structure of the clutch operating mechanism 3 is not limited to the above-described structure. In short, any structure may be used as long as the clutch device 2 can be switched between the connected state and the disconnected state.
- the first clutch portion and the second clutch portion of the clutch device 2 are not limited to the plate shape, and may be any structure as long as the power transmission between the engine 1 and the transmission 6 is shut off and connected. Thus, although the friction plate 23 and the separate plate 24 are formed, the present invention is not limited to this.
- the oil pump 78 is electrically driven, but is not limited to this, and may be a mechanical type operated by the engine 1 or the like.
- the clutch device 2 is switched from the connected state to the disconnected state, and the vehicle is started by the driving force of the motor 8.
- the invention is not limited thereto.
- the flow passage 35 is a passage which performs both supply and discharge of oil to and from the fluid pressure chamber 34.
- the flow passage is not limited to this, and is a flow passage for supplying oil to the fluid pressure chamber 34; It is good also as a structure which has a flow path which discharges oil from room 34 independently.
- the spring 33 is not limited to a coil spring, and may be a leaf spring or a disc spring.
- the clutch device 2 side of the clutch drum 22 is open, and the opening portion is closed by the fixed plate 31.
- the drum chamber 230 is not limited to this.
- the opposite side is open, and this opening may be closed by the fixing plate 31.
- the oil pressure is supplied to the fluid pressure chamber 34 of the clutch operating mechanism 3 by the oil pump 78 to connect the clutch device 2
- the hydraulic pressure chamber 34 may be connected to the oil reservoir 79 so that the clutch device 2 is in the closed state.
- An engine having an output shaft, a transmission having an input shaft to which the driving force of the output shaft of the engine is transmitted and connected to wheels, the output shaft of the engine and the input of the transmission
- a first clutch portion provided between the shaft and the output shaft side of the engine and a second clutch portion provided on the input shaft side of the transmission;
- Unit and the second clutch unit are engaged to transmit the driving force of the engine to the transmission, and the first clutch unit and the second clutch unit are disengaged to transmit the driving force.
- a clutch device switchable to a blocking state for blocking transmission, a clutch operating mechanism for switching a connection state and a blocking state of the clutch device by supplying and discharging a liquid, and supplied to the clutch operating mechanism
- the vehicle drive device having a liquid supply portion for supplying a lubricating or cooling in at least one of said first clutch section and the second clutch portion.
- a lubricating or cooling liquid can be interposed between the frictional engagement surface of the first clutch portion and the frictional engagement surface of the second clutch portion.
- the clutch operating mechanism is connected to a hydraulic pressure chamber that generates a fluid pressure that is pressurized to switch the clutch device from the connected state to the disconnected state, and the fluid is connected to the fluid supply source. And a flow path for supplying liquid to the pressure chamber, and the liquid supply unit is configured to supply pressure from the liquid pressure chamber when the liquid is supplied to the liquid pressure chamber and the pressure is increased.
- a lubricating or cooling liquid can be interposed between the frictional engagement surface of the first clutch portion and the frictional engagement surface of the second clutch portion.
- the present invention can be applied to a hybrid vehicle having an engine and a traveling motor as a vehicle drive source, or a vehicle drive device having an engine but not having a traveling motor.
- 1 is an engine, 10 is an output shaft, 2 is a clutch device, 20 is an input member, 22 is a clutch drum, 222 is an inner cylinder portion, 224 is an outer cylinder portion, 23 is a friction plate (first clutch portion), 24 is a separate Plate (second clutch portion) 260 is a guide passage, 3 is a clutch operating mechanism, 31 is a fixed plate, 32 is a piston, 33 is a spring, 34 is a hydraulic pressure chamber, 35 is a flow passage, 351 is a first flow passage, An annular groove 352, a through hole 353, a check valve 37, a valve port 370, a valve body 371, a valve body 100, an oil supply portion (liquid supply portion) 100, a first seal member 11f, and a first seal member 11s.
- Reference numeral 111 denotes a notched passage (passage), 70 denotes a control valve, 78 denotes an oil pump (liquid supply source), 79 denotes an oil reservoir (liquid reservoir), 8 denotes a traveling motor, 80 denotes a stator, 82 denotes a rotor, 96a , 96c are bearings, 00 shows the oil supply portion (liquid supply portion).
Abstract
Description
エンジンの前記出力軸の駆動力が伝達されると共に軸線を有する入力軸をもち且つ車輪に繋がる変速機と、
エンジンの出力軸と変速機の入力軸との間に設けられ、エンジンの出力軸側に設けられた第1クラッチ部と、変速機の入力軸側に設けられた第2クラッチ部とを有し、第1クラッチ部および第2クラッチ部を係合させてエンジンの駆動力を変速機に伝達させる接続状態と、第1クラッチ部および第2クラッチ部の係合を解除させて前記駆動力の伝達を遮断させる遮断状態とに切替可能なクラッチ装置と、
液体が給排されることによりクラッチ装置の接続状態および遮断状態を切り替えるクラッチ作動機構と、を具備しており、
クラッチ作動機構は、(i)入力軸に固定され且つ第2クラッチ部を支持すると共にドラム室を有するクラッチドラムと、(ii)クラッチドラムで包囲され且つドラム室の開口を閉鎖するように前記クラッチドラムに固定された固定プレートと、(iii)クラッチドラムで包囲され、ドラム室を、クラッチ装置を接続状態から遮断状態に切り替える液圧力を発生させる液圧室とバネ室とに仕切り且つ軸線に沿って移動可能なピストンと、(iv)クラッチドラムで包囲されるようにバネ室の内部に設けられ且つクラッチ装置を遮断状態から接続状態に切り替えるようにピストンを付勢する付勢要素とを具備する。
(iv)外筒部と内筒部と第2延設部とはドラム室を区画し、(v)固定筒部と内筒部と第1延設部とは、クラッチドラムを回転可能に支持させる軸受を配置させるリング状の軸受室を区画しており、(vi)ドラム室および軸受室は入力軸の半径方向に並設されており、軸受室は入力軸の半径方向においてドラム室よりも内周側に配置されている。
前記入力部材と同一軸線上に配置され変速機に繋がる軸状部材と、
前記入力部材および前記軸状部材の一方に対して、前記軸線に沿って、移動可能に係合された第1クラッチ部と、
前記第1クラッチ部と交互に接離可能に配置され、前記入力部材および前記軸状部材の他方に対して、前記軸線に沿って、移動可能に係合された第2クラッチ部と、
前記軸状部材に固定され、且つ前記第2クラッチ部を前記軸線に沿って、移動可能に支持し、底部を有するクラッチドラムと、
前記クラッチドラムに固定されるプレートと、
前記クラッチドラムに前記軸線に沿って移動可能に支持され、前記1クラッチ部および第2クラッチ部を押圧するピストンと、
前記ピストンの一端部と前記クラッチドラムの底部との間に区画形成されるバネ室と、
前記バネ室内に設けられ、前記第1クラッチ部および第2クラッチ部に向かって前記ピストンを付勢する付勢部材と、
前記ピストンの他端部と前記プレートとの間に区画形成される液圧室と
を備え、
前記付勢部材により付勢される前記ピストンの押圧によって前記第1クラッチ部および第2クラッチ部が圧接され、
前記液圧室内に供給されるオイルの圧力によって、前記ピストンは、前記付勢部材の付勢力に抗して前記第1クラッチ部および第2クラッチ部から離間することと
を備える。
本発明の実施形態は、乗用車、大型車両等のハイブリッド車両に適用したものである。図面は実施形態の概念を示す。図1は車両駆動装置の上半分の断面図を示し、図2は下半分の断面図を示し、図3は下半分の要部を拡大して示す。図4は車両駆動システムを表すブロック図を示す。図4に示すように、車両駆動システムは、第1駆動源として機能するエンジン1と、クラッチ装置2と、第2駆動源として機能する電動モータで形成された走行用モータ(以下、モータともいう)8と、変速機6と、制御装置7とを有する。制御装置7は、エンジン1と、モータ8と、変速機6と、制御弁70と、オイルポンプ78とを制御する。モータ8は、車両の減速時等に電気エネルギの回生を行う発電機としても機能できる。本実施形態によれば、回生効率を高める種々の構造が採用されている。オイルポンプ78は電動式であるため、エンジン1が駆動していなくても油(潤滑油)を供給するポンプ作用を発揮できる。図4において、実線の矢印はオイルポンプ78に繋がる油圧通路を示し、破線は制御装置7に繋がる信号線を示す。
クラッチ装置2について説明を加える。クラッチ装置2は湿式多板クラッチを構成しており、入力部材20と、クラッチドラム22と、入力部材20に保持された第1クラッチ部として機能する摩擦プレート23と、クラッチドラム22に保持された第2クラッチ部として機能するセパレートプレート24とをもつ。摩擦プレート23およびセパレートプレート24は対面しつつ交互に配置されており、互いに圧着させて圧着状態である係合状態(接続状態)にでき、且つ、互いに離間して圧着解除である係合解除(遮断状態)にできる。
図7は実施形態2を示す。本実施形態は実施形態1と基本的には同様の作用効果を有する。以下、相違する部分を中心として説明する。図7に示すように、隙間から油を漏出させる第1シール部材11fは切欠き通路111bを有する。第1シール部材11fの中心を通過するように放射方向にのびる仮想線をWとすると、仮想線Wに対して傾斜する傾斜面111m,111kで切欠き通路111bは形成されている。切欠き通路111bに油が通過するとき、油圧が傾斜面111mに作用すると、傾斜面111mを有する一端部11eを径内側(矢印Di方向)に変位させることができる。この場合、一端部11eの外周面11pが径内側に変位するため、外周面11p側における油の漏出量を確保させ易い。更に傾斜面111m,111kに油圧が作用すると、切欠き通路111bの通路幅が増加し易い。このため、第1シール部材11fは、油をシールさせつつも、油の一部を切欠き通路111bからクラッチ装置2に向けて通過させ易い利点が得られる。
図8は実施形態3を示す。本実施形態は実施形態1,2と基本的には同様の作用効果を有する。以下、相違する部分を中心として説明する。図8に示すように、第1シール部材11fは、油を通過させ得る凹部111cを有する。一端部11eは周方向に突出する突起112を有する。他端部11hは突起112を嵌合するスリット113を有する。液圧室34の増圧時においても、突起112がスリット113に嵌合するため、凹部111cの形状が崩れることが抑えられ、凹部111cからの油の漏出量を確保させ易い。
図9は実施形態4を示す。本実施形態は上記実施形態と基本的には同様の作用効果を有する。以下、相違する部分を中心として説明する。図9に示すように、第1シール部材11fはOリング状をなしている。その外周部の一部には、油の一部を漏出できる凹部111dが形成されている。
図10は実施形態5を示す。本実施形態は上記実施形態と基本的には同様の作用効果を有する。以下、相違する部分を中心として説明する。図10に示すように、第2ケース92の固定筒部94の外周面94pとクラッチドラム22の内筒部222の内周面222iとの間には第1シール部材11sが設けられているものの、隙間状の油供給部100には第1シール部材が設けられていない。この場合、隙間を適度に設定して油供給部100から矢印A1方向への油供給性を確保できる。更に、ピストン32とクラッチドラム22の内筒部222との間の隙間には、第4シール部材14が設けられている。しかしクラッチドラム22の内筒部222と固定プレート31との間の領域WTには、第2シール部材が設けられていない。このように図5に比較すると、クラッチ装置2側のシール部材11f,12が設けられていない。このため油供給部100および領域WTの双方からクラッチ装置2へ油を供給させつつも、シール部材11s,14により液圧室34のシール性を確保し、液圧室34を増圧することができ、クラッチ装置2を遮断状態に切り替えることができる。更に図10に示すように、クラッチドラム22に形成されている案内通路260Bは、クラッチ装置2側(図10の左方向)に向かうにつれて、半径方向外方に向かうように傾斜して形成されている。このため遠心力が作用する油を案内通路260Bに通過させてクラッチ装置2に向かわせることができる。
上記した実施形態1はエンジン1およびモータ8を併有するハイブリッド車両に適用しているが、エンジン1を搭載するもののモータ8を搭載しない車両に適用しても良い。クラッチ作動機構3の構造は上記構造に限定されるものではなく、要するに、クラッチ装置2を接続状態と遮断状態とに切り替え得る構造であれば良い。クラッチ装置2の第1クラッチ部および第2クラッチ部はプレート状に限定されるものではなく、エンジン1と変速機6との間の動力伝達の遮断および接続を切り替える構造であれば良い。よって摩擦プレート23とセパレートプレート24とで形成されているが、これに限られるものではない。オイルポンプ78は電動式とされているが、これに限らず、エンジン1等で作動する機械式でも良い。車両が始動するときには、クラッチ装置2は接続状態から遮断状態に切り替えられ、モータ8の駆動力によって車両は発進するが、これに限らず、モータ8の他にエンジン1の駆動力を利用することにしても良い。流路35は、液圧室34に対して油の供給および排出の双方を行う通路であるが、これに限らず、流路は、液圧室34に油を供給させる流路と、液圧室34から油を排出させる流路とを独立して有する構造としても良い。バネ33は、コイルバネに限らず、板バネ、皿バネとしてもよい。ドラム室230はクラッチドラム22のうちクラッチ装置2側が開口しており、この開口部分を固定プレート31で閉鎖しているが、これに限らず、ドラム室230はクラッチドラム22のうちクラッチ装置2と反対側が開口しており、この開口部分を固定プレート31で閉鎖することにしても良い。本発明は上記し且つ図面に示した実施形態のみに限定されるものではなく、要旨を逸脱しない範囲内で適宜変更して実施できる。本明細書の記載から次の技術的思想として把握できる。
(付記項1)出力軸をもつエンジンと、前記エンジンの前記出力軸の駆動力が伝達される入力軸をもち且つ車輪に繋がる変速機と、前記エンジンの前記出力軸と前記変速機の前記入力軸との間に設けられ、前記エンジンの前記出力軸側に設けられた第1クラッチ部と、前記変速機の前記入力軸側に設けられた第2クラッチ部とを有し、前記第1クラッチ部および前記第2クラッチ部を係合させて前記エンジンの駆動力を前記変速機に伝達させる接続状態と、前記第1クラッチ部および前記第2クラッチ部の係合を解除させて前記駆動力の伝達を遮断させる遮断状態とに切替可能なクラッチ装置と、液体が給排されることにより前記クラッチ装置の接続状態および遮断状態を切り替えるクラッチ作動機構と、前記クラッチ作動機構に供給される液体を漏出させて、前記第1クラッチ部および前記第2クラッチ部のうちの少なくとも一方に潤滑用または冷却用として供給させる液体供給部とを具備する車両用駆動装置。この場合、第1クラッチ部の摩擦係合面と第2クラッチ部の摩擦係合面との間に潤滑用または冷却用の液体を介在させることができる。これにより第1クラッチ部の摩擦係合面および第2クラッチ部の摩擦係合面における焼き付きが抑制される。これによりクラッチ部のさらなる耐久性の向上、長寿命化が図られる。
Claims (11)
- 出力軸をもつエンジンと、
前記エンジンの前記出力軸の駆動力が伝達されると共に軸線を有する入力軸をもち且つ車輪に繋がる変速機と、
前記エンジンの前記出力軸と前記変速機の前記入力軸との間に設けられ、前記エンジンの前記出力軸側に設けられた第1クラッチ部と、前記変速機の前記入力軸側に設けられた第2クラッチ部とを有し、前記第1クラッチ部および前記第2クラッチ部を係合させて前記エンジンの駆動力を前記変速機に伝達させる接続状態と、前記第1クラッチ部および前記第2クラッチ部の係合を解除させて前記駆動力の伝達を遮断させる遮断状態とに切替可能なクラッチ装置と、
液体が給排されることにより前記クラッチ装置の接続状態および遮断状態を切り替えるクラッチ作動機構と、を具備しており、
前記クラッチ作動機構は、前記入力軸に固定され且つ前記第2クラッチ部を支持すると共にドラム室を有するクラッチドラムと、前記クラッチドラムで包囲され且つ前記ドラム室の開口を閉鎖するように前記クラッチドラムに固定された固定プレートと、前記クラッチドラムで包囲され、前記ドラム室を、前記クラッチ装置を前記接続状態から前記遮断状態に切り替える液圧力を発生させる液圧室とバネ室とに仕切り且つ前記軸線に沿って移動可能なピストンと、前記クラッチドラムで包囲されるように前記バネ室の内部に設けられ且つ前記クラッチ装置を前記遮断状態から前記接続状態に切り替えるように前記ピストンを付勢する付勢要素とを具備する車両用駆動装置。 - 請求項1において、前記軸線が延びる方向に沿って前記クラッチ装置に向かうにつれて、前記クラッチドラムで包囲される空間に、前記付勢要素、前記ピストンおよび前記固定プレートがこの順に内蔵されている車両用駆動装置。
- 請求項1または2において、前記クラッチドラムは、前記入力軸の外周部に固定された筒状の固定部と、前記固定部から半径方向外方に延設された第1延設部と、前記第1延設部から前記入力軸の前記軸線に沿って形成された内筒部と、前記内筒部から半径方向外方に沿って延設された第2延設部と、前記第2延設部から前記入力軸の前記軸線に沿って形成され且つ前記第2クラッチ部を保持する外筒部とを具備しており、
前記外筒部と前記内筒部と前記第2延設部とはリング状の前記ドラム室を区画し、
前記固定筒部と前記内筒部と前記第1延設部とは、前記クラッチドラムを回転可能に支持させる軸受を配置させるリング状の軸受室を区画しており、前記ドラム室および前記軸受室は前記入力軸の半径方向に並設されており、前記軸受室は前記入力軸の半径方向において前記ドラム室よりも内周側に配置されている車両用駆動装置。 - 請求項1~3のうちの一項において、更に、前記クラッチドラムを包囲するように収容するケースを具備しており、
前記ケースは、前記入力軸に向けて半径方向内方に延設された壁と、前記壁に設けられ前記入力軸の前記軸線に沿って延設された固定筒部とを有しており、前記固定筒部は、前記クラッチドラムを回転可能に支持しており、且つ、液体供給源に繋がり前記液圧室に液体を供給させる流路を有する車両用駆動装置。 - 請求項1~4のうちの一項において、前記固定プレートは前記クラッチ装置に対向するチェック弁を有しており、前記チェック弁は、前記液圧室と外方とを連通させ且つ液体を前記クラッチ装置に向けて排出させる弁口と、前記弁口を開閉可能な弁体とを有する車両用駆動装置。
- 請求項1~5のうちの一項において、更に、前記クラッチ作動機構に供給される液体を漏出させて、前記第1クラッチ部および前記第2クラッチ部のうちの少なくとも一方に前記液体を供給する液体供給部を具備する車両用駆動装置。
- 請求項1~6のうちの一項において、前記液体供給部は、前記液圧室に液体が供給されて増圧されるとき、前記液圧室および/または前記流路から前記液体を漏出させて前記第1クラッチ部および前記第2クラッチ部のうちの少なくとも一方に供給する車両用駆動装置。
- 請求項1~7のうちの一項において、前記クラッチ装置と前記変速機とをつなぐ駆動力伝達経路に、発電機を兼用できる走行用モータが設けられており、前記走行用モータは、ステータと、前記ステータに対して回転すると共に前記変速機の前記入力軸に繋がるロータとを有しており、
前記ステータおよび前記ロータは、前記クラッチ装置の外周側に同軸的に配置されており、前記第1クラッチ部および前記第2クラッチ部のうちの少なくとも一方に供給された前記液体は、前記ステータおよび前記ロータに向けて飛散する車両用駆動装置。 - 請求項1~8のうちの一項において、前記液圧室または前記流路の液体をシールするシール材料で形成されたシール部材が設けられており、前記シール部材は、前記液圧室の増圧に伴い、前記液圧室および/または前記流路に供給された前記液体の一部の前記第1クラッチ部および前記第2クラッチ部のうちの少なくとも一方への供給を許容する通路を有する車両用駆動装置。
- 請求項8または9において、前記液体を貯留させる液体貯留部が設けられており、前記走行用モータの前記ロータが回転するとき、前記ロータは、前記液体貯留部に貯留されている前記液体を少なくとも前記第1クラッチおよび前記第2クラッチ部のうちの一方に跳ねかける車両用駆動装置。
- 駆動源に回転可能に連結される入力部材と、
前記入力部材と同一軸線上に配置され変速機に繋がる軸状部材と、
前記入力部材および前記軸状部材の一方に対して、前記軸線に沿って、移動可能に係合された第1クラッチ部と、
前記第1クラッチ部と交互に接離可能に配置され、前記入力部材および前記軸状部材の他方に対して、前記軸線に沿って、移動可能に係合された第2クラッチ部と、
前記軸状部材に固定され、且つ前記第2クラッチ部を前記軸線に沿って、移動可能に支持し、底部を有するクラッチドラムと、
前記クラッチドラムに固定されるプレートと、
前記クラッチドラムに前記軸線に沿って移動可能に支持され、前記1クラッチ部および第2クラッチ部を押圧するピストンと、
前記ピストンの一端部と前記クラッチドラムの底部との間に区画形成されるバネ室と、
前記バネ室内に設けられ、前記第1クラッチ部および第2クラッチ部に向かって前記ピストンを付勢する付勢部材と、
前記ピストンの他端部と前記プレートとの間に区画形成される液圧室と
を備え、
前記付勢部材により付勢される前記ピストンの押圧によって前記第1クラッチ部および第2クラッチ部が圧接され、
前記液圧室内に供給されるオイルの圧力によって、前記ピストンは、前記付勢部材の付勢力に抗して前記第1クラッチ部および第2クラッチ部から離間することと
を備える車両用駆動装置。
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DE102013015693A1 (de) | 2012-09-24 | 2014-03-27 | Aisin Seiki Kabushiki Kaisha | Kupplungssteuerungssystem einer Kupplungsvorrichtung für ein Hybridfahrzeug |
US8899397B2 (en) | 2012-09-24 | 2014-12-02 | Aisin Seiki Kabushiki Kaisha | Clutch control system of clutch apparatus for hybrid vehicle |
CN105235494A (zh) * | 2014-05-30 | 2016-01-13 | 舍弗勒技术股份两合公司 | 具有鼓式离合器的p2型动力模块 |
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JP4973812B2 (ja) | 2012-07-11 |
US8561775B2 (en) | 2013-10-22 |
JPWO2011062191A1 (ja) | 2013-04-04 |
US20120193187A1 (en) | 2012-08-02 |
DE112010004510T5 (de) | 2013-03-14 |
DE112010004510B4 (de) | 2013-08-01 |
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