WO2011074662A1 - 車両用駆動装置 - Google Patents
車両用駆動装置 Download PDFInfo
- Publication number
- WO2011074662A1 WO2011074662A1 PCT/JP2010/072754 JP2010072754W WO2011074662A1 WO 2011074662 A1 WO2011074662 A1 WO 2011074662A1 JP 2010072754 W JP2010072754 W JP 2010072754W WO 2011074662 A1 WO2011074662 A1 WO 2011074662A1
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- protrusion
- axial direction
- rotor
- support
- drive device
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
- H02K7/006—Structural association of a motor or generator with the drive train of a motor vehicle
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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
- 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
- F16D21/00—Systems comprising a plurality of actuated clutches
- F16D21/08—Serially-arranged clutches interconnecting two shafts only when all the clutches are engaged
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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
- B60K6/42—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
- 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
- B60K2006/4833—Step up or reduction gearing driving generator, e.g. to operate generator in most efficient speed range
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
- B60L2220/00—Electrical machine types; Structures or applications thereof
- B60L2220/50—Structural details of electrical machines
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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
Definitions
- a driving force output from the rotating electrical machine is output via a power transmission device such as a torque converter. It is related with the comprised drive device.
- a vehicle equipped with a rotating electric machine as a second driving force source has been developed.
- the rotating electrical machine is used as a motor / generator.
- the rotating electrical machine outputs a driving force together with the engine or alone, and the driving force is transmitted to the power transmission device to drive the vehicle.
- the rotating electrical machine receives a driving force from a power transmission device or an engine and functions as a generator.
- the rotating electrical machine needs to be connected to the power transmission device or the engine so that the driving force can be transmitted to each other.
- the rotating electrical machine needs to be supported in a state of being rotatable around the axis, similarly to a power transmission device and the like.
- the transmission force that is, the shaft torque that can be transmitted is preferably connected so as to be sufficiently large, and the shaft center accuracy is preferably sufficiently high.
- the shaft center is defined based on a case that is a non-rotating member that accommodates the power transmission device, each rotating member rotates around the shaft center via a support bearing or the like with respect to a support portion formed on the case. Needs to be supported rotatably.
- the input shaft that transmits the driving force of the engine to the power transmission device and the front cover of the power transmission device are connected to rotate integrally, and the input shaft A hub is provided in the vicinity of the connecting portion, and a support member of the rotor is connected to the hub so as to be able to transmit torque, and the shaft is aligned.
- the shaft center of the input shaft is defined by a support portion formed in the case via a support bearing, and the vehicle drive device and the rotor connected to the input shaft are connected to the shaft of the input shaft at each connection portion. Axis is aligned to match the heart.
- the vehicle drive device in addition to the engine and the power transmission device, in order to increase the mountability of the vehicle drive device on the vehicle when the rotating electrical machines are arranged in series on the same axis, the vehicle drive It is required to keep the axial length of the entire apparatus short.
- the rotating electrical machine in the vehicle drive device described in Patent Document 1, is housed in the case together with the power transmission device, and is formed between the support wall extending inward in the radial direction of the case and the front cover of the power transmission device. A connecting portion between the hub of the input shaft and the support member of the rotor is disposed in the space.
- the support member of the rotor is connected so as to be able to transmit torque and is aligned with the shaft center at one connection portion between the hub of the input shaft and the rotor support member. It has been difficult to improve the shaft support accuracy and torque transmission capability of the rotor at the same time. That is, in order to improve the torque transmission capability, it is preferable to increase the thickness of the connecting portion and dispose the connecting portion at a position away from the axis. On the other hand, in order to improve the shaft support accuracy of the rotor, it is preferable to reduce the member thickness of the connecting portion and to reduce the circumference to be processed by arranging the connecting portion at a position close to the shaft center.
- Patent Document 1 does not disclose the arrangement of the connecting members in the case of simultaneously improving the rotor shaft support accuracy and the torque transmission capability.
- the present invention has been made in view of the above problems, and its purpose is to connect a rotating electrical machine and a power transmission device so that the shaft support accuracy and torque transmission capability of the rotor can be improved at the same time, and the case and the rotation. It is in the point which restrains the axial direction length as a whole of the vehicle drive device by making effective use of the space in the radial outside of the rotation support portion with the electric machine or the power transmission device.
- a rotating electrical machine having a rotor that rotates about an axis, a power transmission device to which driving force from the rotating electrical machine and the engine is transmitted, and the rotating electrical machine and the power transmission device
- the case has a support wall that extends at least inward in the radial direction, and is formed integrally with the support wall in the axial direction from the support wall.
- the power transmission device includes a cylindrical first protrusion that protrudes toward the power transmission device, and the power transmission device includes a front cover member that extends at least in the radial direction and has a cylindrical first protrusion that protrudes toward the support wall in the axial direction.
- the second protrusion is rotatably supported with respect to the first protrusion via a support bearing, and the rotor extends at least radially inward to support the rotor.
- a positioning fitting portion for fitting the rotor supporting member to the front cover member and positioning the radial direction on the radially outer side of the second projecting portion, and having a diameter of the positioning fitting portion.
- a torque transmission connecting portion that connects the rotor support member and the front cover member so as to be able to transmit torque is provided on the outer side in the direction apart from the positioning fitting portion, the first protruding portion, the second protruding portion, The positioning fitting portion and the torque transmission connecting portion are arranged so as to overlap each other in the axial direction with respect to the rotation support portion constituted by the support bearing.
- the “axial direction” means the direction of the rotational axis of the rotor. Therefore, the “radial direction” refers to a direction orthogonal to the rotation axis of the rotor, and the “circumferential direction” refers to a rotation direction around the rotation axis of the rotor. Further, in the present application, regarding the arrangement of two members, “overlap” in a certain direction means that each of the two members has at least a portion at the same position with respect to the arrangement in the direction. Further, the “rotary electric machine” is used as a concept including a motor (electric motor), a generator (generator), and a motor / generator that performs both functions of the motor and the generator as necessary.
- the positioning fitting portion and the torque transmission connecting portion are formed apart from each other, the positioning fitting portion is arranged on the radially inner side, and the torque transmission connecting portion is arranged on the radially outer side.
- the shaft support accuracy and torque transmission capability of the rotor can be improved at the same time. That is, since the positioning fitting portion does not need to transmit torque, the member thickness near the positioning fitting portion of the rotor support member or the front cover member can be formed thin. For this reason, the processing of the positioning fitting portion is facilitated, the processing accuracy of the fitting surface for radial positioning can be improved, and the axial length near the positioning fitting portion can be kept short.
- the positioning fitting portion is disposed radially inward of the torque transmission portion, the circumference to be processed can be reduced, and the processing accuracy of the positioning fitting portion can be further improved.
- the torque transmission connecting portion is arranged on the radially outer side with respect to the positioning fitting portion, the torque torque that can be transmitted by the torque transmitting connecting portion can be increased by the lever principle. It becomes easy.
- each of the positioning fitting portion and the torque transmission connecting portion is arranged overlapping in the axial direction with respect to the rotation support portion configured by the first protrusion portion, the second protrusion portion, and the support bearing, The positioning fitting portion and the torque transmission connecting portion can be arranged by effectively using the space on the radially outer side of the rotation support portion. Therefore, the axial length of the entire vehicle drive device can be kept short.
- the vehicle drive device includes the first protrusion, the second protrusion, the support bearing, the rotor support member, the positioning fitting portion, and the torque transmission connecting portion with respect to the rotor. It is preferable to adopt a configuration in which each is overlapped in the axial direction.
- the first projecting portion, the second projecting portion, the support bearing, the rotor support member, the positioning fitting portion, and the torque transmission can be made by effectively using the radially inner space of the rotor.
- a connection part can be arrange
- the rotor support member has an offset portion formed on the radially inner side of the torque transmission connecting portion and offset in the axial direction toward the front cover member, and the rotor support member and the rotor support member It is preferable that the rotation sensor is arranged at a position that overlaps with the offset portion of the rotor support member in the radial direction.
- the front cover member is formed with a connecting portion constituting the torque transmission connecting portion protruding in the axial direction for flattening processing, etc. In the axial direction, it is retracted to the opposite side to the rotor support member.
- the rotor support member is formed by being offset in the axial direction toward the front cover member on the radially inner side of the torque transmission connecting portion, so that the space between the rotor support member and the support wall is axially formed. Can be spread. Therefore, while being able to arrange
- the rotation sensor is arranged so as to overlap with the rotation support portion in the axial direction.
- the rotation sensor is arranged to overlap with the rotor in the axial direction.
- the rotation sensor can be arranged by effectively using the space inside the rotor in the radial direction, and the axial length of the entire vehicle drive device can be kept short.
- the front cover member includes a third projecting portion that projects in the axial direction toward the support wall on the radially outer side of the second projecting portion, and the radially outer surface of the third projecting portion is positioned on the positioning surface. It is preferable that the fitting surface on the front cover member side of the fitting portion is configured, and the rotor support member is fitted to the radially outer surface of the third protruding portion.
- the third projecting portion is formed to project from the front cover member in the axial direction toward the support wall, so that the space between the front cover member and the support wall is effectively used to perform positioning fitting.
- a fitting surface on the front cover member side that constitutes the joint portion can be formed.
- the third projecting portion is an axial projecting portion, a radially outer surface of the third projecting portion is processed with high accuracy, and a fitting surface for the radial positioning of the rotor support member is provided. can do. Therefore, the processing accuracy for positioning the positioning fitting portion can be improved, and the radial positioning accuracy of the rotor is improved.
- the third projecting portion is overlapped in the axial direction with respect to the rotation support portion.
- the third projecting portion can be disposed by effectively using the space on the outer side in the radial direction of the rotation support portion, and the axial length of the vehicle drive device as a whole can be kept short. .
- the third protrusion is overlapped in the axial direction with respect to the rotor.
- the support bearing is attached between a radially inner surface of the first protrusion and a radially outer surface of the second protrusion, and the rotor support member is disposed radially inward of the torque transmission connecting portion.
- a cylindrical fourth projecting portion projecting in the axial direction toward the support wall is provided on a radially outer side of the first projecting portion, and the fourth projecting portion extends axially with the first projecting portion. It is preferable that the rotation sensor is arranged in an overlapping manner, and the rotation sensor is arranged between the radially inner side surface of the fourth protrusion and the radially outer surface of the first protrusion.
- the rotation sensor since the fourth projecting portion is formed to project from the rotor support member in the axial direction toward the support wall, the rotation sensor effectively utilizes the space between the rotor support member and the support wall. Can be formed on the rotor side.
- the fourth projecting portion since the fourth projecting portion is disposed on the radially inner side of the torque transmission connecting portion, the fourth projecting portion can be disposed while avoiding the torque transmitting connecting portion in the radial direction, and the rotation sensor is arranged with the offset portion and the diameter.
- a 4th protrusion part can be arrange
- a rotation sensor can be arrange
- the rotation sensor can be arranged by effectively using the space between the rotor support member and the support wall in the radial direction, and the axial length of the entire vehicle drive device is prevented from being increased. it can.
- the rotation sensor since the rotation sensor is attached to the radially outer surface of the first protrusion and the support bearing is attached to the radially inner surface of the first protrusion, both the radially inner surface and the outer surface of the first protrusion are attached.
- the support bearing and the rotation sensor can be attached effectively. Therefore, it is not necessary to newly form a protrusion for mounting the rotation sensor on the support wall, and the protrusion can be shared. Therefore, the space between the front cover member and the support wall can be effectively used in the radial direction to arrange each component, and the overall axial length of the vehicle drive device can be kept short. .
- the fourth projecting portion is overlapped in the axial direction with respect to the rotation support portion.
- the fourth projecting portion can be arranged by effectively using the space on the radially outer side of the rotation support portion, and the axial length of the entire vehicle drive device can be kept short. .
- the fourth projecting portion is overlapped in the axial direction with respect to the rotor.
- the support bearing is attached between a radially outer surface of the first protrusion and a radially inner surface of the second protrusion, and the rotor support member is disposed radially inward of the torque transmission connecting portion.
- a cylindrical fourth projecting portion projecting in the axial direction toward the support wall, and the support wall is disposed radially outside the rotation support portion and radially inward of the fourth projecting portion.
- a fourth cylindrical projecting portion projecting toward the rotor support member in the direction, and the fourth projecting portion and the fifth projecting portion are arranged so as to overlap each other in the axial direction. It is preferable that the rotation sensor is arranged between a radially inner side surface and a radially outer side surface of the fifth protrusion.
- the fourth protrusion is formed to protrude from the rotor support member in the axial direction toward the support wall
- the fifth protrusion is formed to protrude from the support wall in the axial direction toward the rotor support member. Therefore, the protrusion for attaching the rotation sensor to the rotor side and the support wall side can be formed by effectively utilizing the space between the rotor support member and the support wall.
- the fourth projecting portion is disposed on the radially inner side of the torque transmission connecting portion, the fourth projecting portion can be disposed while avoiding the torque transmitting connecting portion in the radial direction, and the rotation sensor is arranged with the offset portion and the diameter.
- a 4th protrusion part can be arrange
- a rotation sensor can be arrange
- the 5th protrusion part is formed in the radial direction outer side of the rotation support part, a rotation support part and attachment of a rotation sensor can be designed separately, and each design freedom improves. Therefore, it is possible to attach a support bearing between the radially outer surface of the first protrusion and the radially inner surface of the second protrusion.
- the fourth projecting portion and the fifth projecting portion are arranged to overlap each other in the axial direction with respect to the rotation support portion.
- the fourth projecting portion and the fifth projecting portion can be arranged by effectively using the space on the radially outer side of the rotation support portion, and the axial length of the vehicle drive device as a whole is reduced. It can suppress becoming longer.
- the fourth projecting portion and the fifth projecting portion are overlapped in the axial direction with respect to the rotor.
- the fourth projecting portion and the fifth projecting portion can be arranged by effectively using the space inside the rotor in the radial direction, and the overall axial length of the vehicle drive device is increased. This can be suppressed.
- the hybrid drive device 1 is a drive device for a hybrid vehicle that uses one or both of the engine E and the rotating electrical machine MG as a drive force source of the vehicle. As shown in FIG. 3, the hybrid drive device 1 includes a rotating electrical machine MG having a rotor 22 that rotates about an axis X, and torque as a power transmission device to which driving power from the engine E and the rotating electrical machine MG is transmitted.
- a converter TC and a drive device case 2 (hereinafter simply referred to as “case 2”) that accommodates the rotating electrical machine MG and the torque converter TC are provided.
- case 2 a drive device case 2
- the axial direction, the circumferential direction, and the radial direction are defined based on the axis X unless otherwise specified.
- the hybrid drive device 1 has the following features as shown in FIGS. That is, when connecting the rotor support member 23 that extends radially inward of the rotor 22 and supports the rotor 22 to the front cover member 32 of the torque converter TC, the rotor support member 23 is fitted to the front cover member 32 to radially And a torque transmission connecting portion 13 that connects the rotor support member 23 and the front cover member 32 so that torque can be transmitted.
- the torque transmission connecting portion 13 has a diameter of the positioning fitting portion 12. It is on the outer side in the direction and is spaced apart from the positioning fitting portion 12.
- the second projecting portion 6 of the front cover member 32 is rotatably supported by the first projecting portion 5 of the case 2 via a support bearing 71.
- the positioning fitting portion 12 and the torque transmission connecting portion 13 are disposed so as to overlap each other in the axial direction with respect to the rotation support portion 11 configured by the first protrusion portion 5, the second protrusion portion 6, and the support bearing 71. ing.
- the rotating electrical machine MG and the torque converter TC can be coupled so as to improve the shaft support accuracy and torque transmission capability of the rotor 22 at the same time, and the radial direction of the rotation support portion 11 between the case 2 and the torque converter TC.
- the hybrid drive device 1 that can effectively reduce the axial length of the hybrid drive device 1 as a whole by using the outer space effectively is realized.
- the hybrid drive device 1 according to the present embodiment will be described in detail.
- the hybrid drive device 1 includes an input shaft I that is drivingly connected to an engine E as a first driving force source, and a second driving force source that is drivingly connected to a torque converter TC.
- an output shaft O that is drivingly connected to the wheel W, and these are accommodated in the case 2.
- Engine E is an internal combustion engine that is driven by the combustion of fuel.
- various known engines such as a gasoline engine and a diesel engine can be used.
- an engine output shaft such as a crankshaft of the engine E is drivingly connected to the input shaft I via a damper DP.
- the engine E and the input shaft I are selectively connected to the torque converter TC and the rotating electrical machine MG via the first clutch C1.
- the first clutch C1 In the engaged state of the first clutch C1, the engine E, the torque converter TC, and the rotating electrical machine MG are drivingly connected via the input shaft I.
- the released state of the first clutch C1 the engine E, the torque converter TC, and the rotating electrical machine are connected. MG is separated.
- the first clutch C1 is provided so that the engine E, the rotating electrical machine MG, and the torque converter TC can be separated.
- the vehicle In the released state (separated state) of the first clutch C1, the vehicle can be driven through the torque converter TC, the transmission device TM, and the like by only the driving force of the rotating electrical machine MG without being affected by the engine E. Further, it is possible to generate electric power by transmitting the driving force transmitted from the wheels W only when the vehicle is decelerated to only the rotating electrical machine MG. Therefore, the rotating electrical machine MG is drivingly connected to the torque converter TC. Further, since the input shaft I and the torque converter TC are separated by the first clutch C1, the input shaft I and the torque converter TC are supported so as to be rotatable with respect to the case 2, respectively.
- the rotating electrical machine MG includes a stator 21 and a rotor 22, and functions as a motor (electric motor) that generates power by receiving power and a generator (power generation) that generates power by receiving power. Function). Therefore, rotating electrical machine MG is electrically connected to a power storage device (not shown). In this example, a battery is used as the power storage device. Note that it is also preferable to use a capacitor or the like as the power storage device.
- the rotating electrical machine MG is powered by receiving electric power from the battery, or supplies the electric power generated by the driving force transmitted from the wheel W or the engine E to the battery for storage.
- the rotor 22 of the rotating electrical machine MG is drivingly connected to the torque converter TC so as to rotate integrally with the pump impeller 31 of the torque converter TC.
- this drive connection is realized by connecting the rotor support member 23 of the rotor 22 and the front cover member 32 of the torque converter TC by the torque transmission connection portion 13 and the positioning fitting portion 12.
- the stator 21 is attached to the case 2 which is a non-rotating member.
- the torque converter TC is a device that converts the torque of one or both of the engine E and the rotating electrical machine MG and transmits it to the transmission TM.
- the torque converter TC includes a pump impeller 31 that is drivingly connected to rotate integrally with the front cover member 32 and the rotor 22 of the rotating electrical machine MG, a turbine runner 41 that is drivingly connected to rotate integrally with the intermediate shaft M, these And a stator 46 provided therebetween.
- the torque converter TC can transmit torque between the drive-side pump impeller 31 and the driven-side turbine runner 41 via oil filled therein.
- the torque converter TC includes a second clutch C2.
- the second clutch C2 functions as a friction engagement device for locking up the torque converter TC.
- the second clutch C2 drives and connects the pump impeller 31 and the turbine runner 41 so as to rotate together in order to eliminate the differential rotational speed between the pump impeller 31 and the turbine runner 41 and increase power transmission efficiency. That is, in the engaged state of the second clutch C2, the torque converter TC directly transmits the torque of the engine E and the rotating electrical machine MG or the torque of the rotating electrical machine MG via the intermediate shaft M without using internal oil. Communicate to TM. Further, in the engaged state of the second clutch C2, the torque converter TC transmits the torque transmitted from the wheel W via the transmission device TM to the rotating electrical machine MG side without passing through the internal oil.
- the front cover member 32 of the torque converter TC is a member that forms a part of the outer shell support member 30 of the torque converter TC, and is drivingly connected so as to rotate integrally with the pump impeller 31 and the rotor 22 of the rotating electrical machine MG. Is done. Further, the front cover member 32 is provided with a first clutch C1 for connecting / disconnecting a driving force to / from the input shaft I and a second clutch C2 for locking up the torque converter TC. Further, as will be described later, the front cover member 32 has a second protrusion 6, and the second protrusion 6 is rotatable with respect to the first protrusion 5 of the case 2 via a support bearing 71. Supported.
- the case 2 is a substantially cylindrical member that accommodates the torque converter TC and the rotating electrical machine MG therein, and is a non-rotating member that is fixed to the chassis. Further, the case 2 is configured such that the rotating members such as the input shaft I, the intermediate shaft M, the torque converter TC, and the rotor 22 of the rotating electrical machine MG can be rotated by the support portions on the engine E side and the transmission device TM side of the case 2. To support. As will be described later, the case 2 has a first protruding portion 5 formed on the support wall 4 of the case 2, and the first protruding portion 5 supports the second protruding portion 6 of the front cover member 32 as a support bearing 71. It is supported rotatably via Further, the stator 2 of the rotating electrical machine MG is attached to the case 2.
- the transmission TM is a device that shifts the rotation speed of the intermediate shaft M at a predetermined gear ratio and transmits it to the output shaft O.
- Examples of such a transmission TM include an automatic or manual stepped transmission that can switch between a plurality of shift stages having different transmission ratios, an automatic continuously variable transmission that can change the transmission ratio steplessly, and the like. Can be used.
- the transmission TM shifts the rotational speed of the intermediate shaft M at a predetermined gear ratio at each time point, converts torque, and transmits the torque to the output shaft O.
- the torque transmitted from the transmission device TM to the output shaft O is distributed and transmitted to the two left and right wheels W via the differential device D.
- the input shaft I, the intermediate shaft M, and the output shaft O are uniaxially arranged coaxially.
- the hybrid drive device 1 includes the input shaft I, the intermediate shaft M, the output shaft O, the rotating electrical machine MG, the torque converter TC, the transmission device TM, the first clutch C1, the case 2, and the like.
- the configuration of each part of the hybrid drive device 1 will be described in detail.
- a flywheel 81 is connected to the engine E.
- the flywheel 81 is a disk-shaped member having a large rotational inertia moment, and is for suppressing torque fluctuations of the engine E, similarly to those attached to various conventional engines.
- the flywheel 81 is connected to a damper DP which is a vibration damping mechanism.
- This damper DP is a mechanism that attenuates the vibration or fluctuation of the torque input from the flywheel 81 and smoothes and outputs the amplitude of the vibration, and various configurations can be used as necessary. .
- an elastic body such as a spring is interposed between an input side member and an output side member that can be relatively rotated, and a mechanism that attenuates vibration by expansion and contraction of the elastic body is used. it can. Since the member on the input side of the damper DP is connected to the flywheel 81 and the member on the output side is connected to the input shaft I, the driving force of the engine E is input to the hybrid drive device 1.
- the flywheel 81 or the damper DP is a member that can be selectively employed, and one or both of them may be omitted to connect the engine E and the input shaft I.
- the drive device case 2 is a substantially cylindrical member that accommodates each accommodating component such as the torque converter TC and the rotating electrical machine MG, and is a non-rotating member. Further, the case 2 is configured such that the rotating members such as the input shaft I, the intermediate shaft M, the torque converter TC, and the rotor 22 of the rotating electrical machine MG are connected to the engine E side (one axial direction side) and the transmission TM side ( The support portions formed on the other side in the axial direction are rotatably supported around the axis X and are positioned in the radial direction. As shown in FIG.
- the case 2 closes the case peripheral wall 3 that covers the outer periphery of each housing component and the opening on one side in the axial direction of the case 2 (left side in FIG. 3), and each rotating member on one side in the axial direction A support wall 4 is rotatably supported. Further, the case 2 is disposed between the torque converter TC and the transmission device TM on the other axial side (the right side in FIG. 3), and supports the rotating members rotatably on the other axial side. 90 (see FIG. 2). In the present embodiment, the case 2 is configured to be divided into a first case 2a and a second case 2b attached to the other side in the axial direction of the first case 2a.
- a part of one side of the case peripheral wall 3 in the axial direction and the support wall 4 are integrally formed in the first case 2a.
- the second case 2b is formed with a remaining portion on the other side in the axial direction of the case peripheral wall 3, and attached with an intermediate support wall 90.
- a torque converter TC, a rotating electrical machine MG, a first clutch C ⁇ b> 1, and the like are accommodated in a space defined between the case peripheral wall 2, the support wall 4, and the intermediate support wall 90.
- the transmission TM is accommodated on the other axial side of the intermediate support wall 90 in the case 2.
- the support wall 4 has a shape extending at least in the radial direction.
- the support wall 4 has an annular plate shape extending in the radial direction and the circumferential direction.
- the support wall 4 includes a cylindrical first protrusion 5 that is formed integrally with the support wall 4 and protrudes from the support wall 4 in the axial direction toward the torque converter TC (the other side in the axial direction). Since the first projecting portion 5 is formed so as to project inside the support wall 4, the outer surface of the support wall 4 can be prevented from projecting, and the axial direction between the support wall 4 and the damper DP can be prevented.
- the distance can be shortened and the rotor 22 and the rotation sensor 27 can be attached and the rotating members can be rotated by effectively using the radial space of the first protrusion 5 protruding inside the support wall 4 as will be described later. Support and radial positioning.
- the first protruding portion 5 has a cylindrical shape that protrudes from the vicinity of the radially inner peripheral end of the support wall 4 to the other side in the axial direction.
- the circular center of the cylindrical first protrusion 5 becomes the axis X, and the first protrusion 5 rotates the rotating members of the hybrid drive device 1 around the axis X on one axial side of the hybrid drive device 1.
- an axial through hole that penetrates the inner side and the outer side of the case 2 in the axial direction on one axial side is formed on the radially inner side of the first protrusion 5.
- the input shaft I passes through the through hole formed in the support wall 4 of the case 2, and the input shaft I enables transmission of driving force between the engine E and the hybrid drive device 1.
- the first protrusion 5 of the support wall 4 rotatably supports a second protrusion 6 formed on a front cover member 32 of a torque converter TC described later via a support bearing 71.
- the support part comprised by the 1st protrusion part 5, the 2nd protrusion part 6, and the support bearing 71 is the rotation support part 11 in this invention.
- the first projecting portion 5, the second projecting portion 6, and the support bearing 71 that constitute the rotation support portion 11 are disposed so as to overlap with the rotor 22 in the axial direction.
- the 1st protrusion part 5 and the 2nd protrusion part 6 are arrange
- a support bearing 71 is arranged between the radially inner side surface of the first protrusion 5 and the radially outer surface of the second protrusion 6.
- the radially inner side surface of the first protrusion 5 supports the radially outer surface of the second protrusion 6 via the support bearing 71.
- the radially inner side surface of the first protrusion 5 formed in a cylindrical shape is fitted with the radially outer surface of the support bearing 71 to position the support bearing 71 in the radial direction.
- the radially inner side surface of the support bearing 71 is fitted with the radially outer surface of the second protruding portion 6 formed in a cylindrical shape to position the second protruding portion 6 in the radial direction.
- the first protrusion 5 rotatably supports the second protrusion 6 via the support bearing 71 and positions the second protrusion 6 in the radial direction.
- a ball bearing which is a kind of radial bearing is used as the support bearing 71. Ball bearings can support relatively large radial loads.
- the fact that one member completely overlaps the other member in the axial direction means that the entire one member is at the same position as at least a part of the other member with respect to the arrangement in the axial direction. Point to.
- a needle bearing 72a is disposed between the radially inner side surface of the second protrusion 6 and the radially outer surface of the input shaft I. That is, the radially inner side surface of the second protrusion 6 supports the radially outer surface of the input shaft I via the needle bearing 72a. Thereby, the 2nd protrusion part 6 positions the input shaft I to radial direction while rotatably supporting the input shaft I via the needle bearing 72a. Further, as will be described later, the input shaft I is formed in a hollow cylindrical shape on the other side in the axial direction from the support wall 4, and the radially inner side surface of the input shaft I in the cylindrical portion is interposed through an oil film or the like.
- the outer side surface of the intermediate shaft M in the radial direction is supported.
- the input shaft I rotatably supports the intermediate shaft M via an oil film or the like, and positions the intermediate shaft M in the radial direction. Therefore, according to the present embodiment, the first protrusion 5 of the support wall 4 that is a non-rotating member can rotatably support the second protrusion 6 of the front cover member, the input shaft I, and the intermediate shaft M, It can be positioned in the radial direction.
- the rotating members of the second projecting portion 6, the input shaft I, and the intermediate shaft M are disposed so as to overlap with the first projecting portion 5 in the axial direction and overlap with the first projecting portion 5 in the axial direction.
- each rotating member can be rotatably supported by effectively using the radial space of the first projecting portion 5.
- the end on the other axial side of the input shaft I is formed in a hollow cylindrical shape
- the end on the one axial side of the intermediate shaft M is inserted radially inside the cylindrical portion
- the intermediate shaft M is Since it is configured to overlap with the one projecting portion 5 in the axial direction, the radial positioning accuracy including the intermediate shaft M can be improved, and the radial positioning accuracy in which the rotating members of the hybrid drive device 1 are integrated is improved. it can.
- the bearing to be added is configured to be disposed at a position overlapping with the support bearing 71 or the needle bearing 72a in the axial direction.
- the first protrusion 5 is engaged with the support bearing 71 on the radially inner side surface to position the support bearing 71 in the radial direction.
- one axial side of the support bearing 71 abuts against the other axial surface (of the axial step) of the support wall 4 that extends radially inward from the first protrusion 5.
- the other axial side of the support bearing 71 is fixed by a snap ring 71 c that is a fixing member attached to the radially inner side surface of the first protrusion 5.
- the snap ring 71c is fitted and fixed in a groove formed on the radially inner side surface of the first protrusion 5. Therefore, the 1st protrusion part 5 has positioned the support bearing 71 in the axial direction in cooperation with the snap ring 71c.
- the rotation sensor 27 of the rotating electrical machine MG is attached to the radially outer surface of the first protrusion 5.
- the rotation sensor 27 is a sensor that detects the rotation speed of the rotor 22.
- the rotation sensor 27 includes a sensor rotor 27a and a sensor stator 27b.
- the sensor stator 27b is attached to the case 2 that is a non-rotating member, and the sensor rotor 27a is attached to the rotor support member 23.
- the radially outer surface of the first protrusion 5 is fitted with the sensor stator 27b, and positions the sensor stator 27b in the radial direction.
- a resolver is used as the rotation sensor 27.
- Various sensors other than the resolver can be used as the rotation sensor 27.
- the support bearing 71 is attached to the radially inner surface of the first protrusion 5 and the rotation sensor 27 is attached to the radially outer surface of the first protrusion 5, the radially inner surface of the first protrusion 5 and The support bearing 71 and the rotation sensor 27 can be attached by making effective use of both the outer side surfaces. Therefore, it is not necessary to newly form a protrusion for mounting the rotation sensor 27 on the support wall 4 or for radial positioning, and the protrusion can be shared. Moreover, since the protrusion is formed, the processing accuracy of the fitting surface for the radial positioning can be improved.
- the radial positioning portion 27d and the connecting portion 27c of the sensor stator 27b are separated. As shown in FIG. 1, in the radial positioning portion 27d, the radial outer surface of the first protrusion 5 and the radial inner side surface of the stator core of the sensor stator 27b are fitted to position the sensor stator 27b in the radial direction. In the connecting portion 27c, the stator core of the sensor stator 27b is fixed to the support wall 4 using fastening members such as bolts and nuts.
- the intermediate support wall 90 (see FIG. 2) has a shape extending at least in the radial direction, and in the present embodiment, has an annular plate shape extending in the radial direction and the circumferential direction.
- the intermediate support wall 90 is fixed to the second case 2b by a fastening member such as a bolt.
- the pump cover 91 (see FIG. 3) is fixed to the intermediate support wall 90 by a fastening member such as a bolt in a state where the pump cover 91 is in contact with the intermediate support wall 90 from one axial side.
- a pump chamber (not shown) is formed between the intermediate support wall 90 and the pump cover 91, and an oil pump (not shown) is arranged in the pump chamber.
- the pump cover 91 includes a cylindrical axial projecting portion 92 that projects around one side in the axial direction (torque converter TC side) around the intermediate shaft M.
- the axial protrusion 92 is formed integrally with the pump cover 91.
- the circular center of the cylindrical axial protrusion 92 becomes the axis X, and the axial protrusion 92 rotates the intermediate shaft M of the hybrid drive device 1, the pump impeller 31, etc. on the other axial side of the hybrid drive device 1.
- the member is rotatably supported around the axis X and positioned in the radial direction.
- the oil pump is connected to rotate integrally with the pump impeller 31.
- the oil pump discharges oil (operating oil), and the torque converter TC, the first Hydraulic pressure for supplying oil to the clutch C1, the transmission TM, etc., and the bearings and support portions such as the support bearing 71, each needle bearing 72, and each thrust bearing 73 is generated.
- a plurality of shaft center oil passages which will be described later, are formed inside the intermediate shaft M, and oil discharged by the oil pump flows through a hydraulic control device (not shown) and the plurality of shaft center oil passages.
- axial oil passages Lc1 and Lc2 are illustrated.
- the input shaft I is a shaft for inputting the driving force of the engine E into the hybrid drive device 1.
- the tip end portion (left end portion in FIG. 3) of the input shaft I is inserted through the inner peripheral portion of the damper DP, and the input shaft I is connected to the output side of the damper DP.
- the boss 82 formed on the member is spline-fitted so that torque can be transmitted. Therefore, the input shaft I is coupled to rotate integrally with the engine output shaft of the engine E via the damper DP. Further, one end of the input shaft I in the axial direction is inserted into a hollow cylindrical portion formed at the other end of the output shaft of the engine E in the axial direction.
- a bearing 74 is disposed between the radially inner side surface and the radially outer surface of the distal end portion of the input shaft I.
- the input shaft I is supported so as to be relatively rotatable with respect to the output shaft of the engine E via the bearing 74, and therefore, misalignment between the shaft center X of the input shaft and the output shaft of the engine E is suppressed. It is possible to suppress rotational vibration due to axial misalignment between the engine E and the hybrid drive device 1.
- the input shaft I is disposed so as to penetrate the support wall 4 of the case 2. As described above, an axial through hole is formed in the radial center portion of the support wall 4 of the case 2.
- the input shaft I passes through the through hole of the support wall 4 of the case 2 in the axial direction, and the input shaft I enables transmission of driving force between the engine E and the hybrid drive device 1.
- the input shaft I is arranged in a form that completely penetrates the cylindrical first protrusion 5 formed on the support wall 4 in the axial direction.
- the input shaft I is connected to the first protrusion 5 of the support wall 4 via the support bearing 71, the second protrusion 6 of the front cover member, and the needle bearing 72a (see FIG. 1).
- the shaft X is rotatably supported around the axis X and is positioned in the radial direction. Since the needle bearing 72a disposed between the input shaft I and the second protrusion 6 is disposed at a position overlapping the first protrusion 5 in the axial direction, the diameter of the input shaft I with respect to the first protrusion 5 Directional positioning accuracy can be improved.
- the input shaft I is formed in a solid columnar shape on the substantially axial one side from the one axial end of the radially inner side surface of the support wall 4.
- the support wall 4 is formed in a hollow cylindrical shape centered on the axis X on the other side in the axial direction from the one axial end on the radially inner side surface.
- the input shaft I includes an annular plate-shaped hub portion extending substantially radially outward from the other axial end of the hollow cylindrical portion.
- a first clutch hub 52 formed integrally with a substantially annular plate-like member extending outward in the radial direction and a cylindrical member is integrally rotated with the input shaft I at the radially outer end of the annular plate-like hub portion. It is connected.
- the inner diameter of the hollow cylindrical portion of the input shaft I is slightly smaller than the outer diameter of the intermediate shaft M so that the intermediate shaft M inserted therein can be rotatably supported and positioned in the radial direction. Is formed.
- the intermediate shaft M is a shaft for inputting torque output from the torque converter TC to the transmission apparatus TM, and is connected to rotate integrally with the turbine runner 41 of the torque converter TC.
- the intermediate shaft M is disposed so as to penetrate the intermediate support wall 90 and the pump cover 91.
- an axial through hole is formed in the radial center portion of the intermediate support wall 90 and the pump cover 91, and the intermediate shaft M connects the intermediate support wall 90 and the pump cover 91 through the through hole. It penetrates.
- the intermediate shaft M is arranged in such a manner that it completely penetrates the through hole provided in the intermediate support wall 90 and the cylindrical axial protrusion 92 provided in the pump cover 91 in the axial direction.
- the intermediate shaft M is rotatably supported with respect to the intermediate support wall 90 via a fixing sleeve 49 connected and fixed to the intermediate support wall 90 at a connecting portion (see FIG. 2), and is positioned in the radial direction. ing.
- a plurality of axial oil passages Lc1 and Lc2 extending in the axial direction are formed inside the intermediate shaft M.
- the axial center oil passages Lc1 and Lc2 serve as flow passages for supplying the oil discharged by the oil pump to the respective parts to be supplied with oil.
- the intermediate shaft M is formed with oil holes Lh2, Lh4, Lh7 (see FIG. 1) penetrating each axial center oil passage and the outer peripheral surface of the intermediate shaft M in the radial direction, and the oil holes Lh2, Oil circulates between the axial oil passages Lc1, Lc2 and the respective oil supply targets via Lh4, Lh7.
- the oil holes Lh2, Lh4, Lh7 of the respective axial center oil passages Lc1, Lc2 are arranged at different axial positions, and correspond to the axial positions in the flow passages to be supplied with oil.
- the first shaft oil passage Lc1 is a flow passage that mainly supplies hydraulic pressure to the first clutch C1
- the second shaft oil passage Lc2 is the support bearing 71 and the torque. This is a flow passage for supplying oil into the converter TC and the like.
- an oil hole Lh2 is formed in the first shaft oil passage Lc1 so as to penetrate the first shaft oil passage Lc1 and the outer peripheral surface of the intermediate shaft M in the radial direction.
- the oil hole Lh2 is positioned so as to overlap with the radially inner end of the oil hole Lh3 formed in the front cover member 32 in order to supply hydraulic pressure to the first supply oil chamber H1 of the first clutch C1.
- the hydraulic pressure supplied to the first supply oil chamber H1 of the first clutch C1 is supplied through the oil hole Lh3.
- the input shaft I disposed between the intermediate shaft M and the front cover member 32 also has an outer peripheral surface and an inner peripheral surface of the cylindrical portion of the input shaft I at positions overlapping the oil hole Lh3 in the axial direction.
- An oil hole Lh1 is formed so as to penetrate through in the radial direction. Since the intermediate shaft M, the input shaft I, and the front cover member 32 rotate relative to each other, the circumferential positions of the oil holes Lh1, Lh2, and Lh3 do not always coincide. Therefore, the intermediate shaft M and the input shaft I are radially inward over the entire circumference on the radially outer surface of each of the intermediate shaft M and the input shaft I at positions overlapping the oil holes Lh1 and Lh2.
- All-round oil passages Lr1 and Lr2 formed by retraction are provided. Since oil flows between the oil hole Lh2 and the oil hole Lh1 and between the oil hole Lh1 and the oil hole Lh3, respectively, through the entire circumference oil passages Lr1 and Lr2, the oil holes Even if the positions in the circumferential direction of Lh1, Lh2, and Lh3 do not coincide with each other due to relative rotation, oil can always be circulated. Further, seal rings 77 are disposed between the relative rotation members on both sides in the axial direction of the entire circumferential oil passages Lr1, Lr2, respectively, so that the entire circumferential oil passages Lr1, Lr2 are in a liquid-tight state.
- the hydraulic pressure supplied by the first shaft oil passage Lc1 can be supplied to the first supply oil chamber H1 of the first clutch C1.
- the hydraulic pressure supplied to the second supply oil chamber H ⁇ b> 2 of the second clutch C ⁇ b> 2 passes through Lh ⁇ b> 5 formed in the turbine hub 44 and is not shown in the center shaft oil formed on the intermediate shaft M. Supplied from the road and oil hole.
- the second axial oil passage Lc2 is formed with an oil hole Lh4 and an oil hole Lh7 that respectively penetrate the second axial oil passage Lc2 and the outer peripheral surface of the intermediate shaft M in the radial direction.
- the oil hole Lh4 is an oil hole for supplying oil to the friction plate 56 of the first clutch C1, the friction plate 66 of the second clutch C2, the thrust bearings 73a, 73d, etc. in the torque converter TC. It arrange
- the friction plate 56 and the second clutch C1 of the first clutch C1 are connected via the one oil hole Lh4. Oil can be supplied to the friction plate 66 of the clutch C2.
- the oil hole Lh7 is an oil hole for supplying oil from the second shaft center oil passage Lc2 to the support bearing 71, the needle bearing 72a, and the space between the intermediate shaft M and the input shaft I.
- the oil hole Lh7 is arranged at a position overlapping with the oil hole Lh8 formed in the input shaft I in order to supply hydraulic pressure to the support bearing 71 and the needle bearing 72a in the axial direction.
- the oil hole Lh8 is formed through the outer peripheral surface and the inner peripheral surface of the hollow cylindrical portion of the input shaft I in the radial direction. Since the intermediate shaft M and the input shaft I rotate relative to each other, the circumferential positions of the oil holes Lh7 and Lh8 do not always coincide with each other.
- the intermediate shaft M is provided with an all-round oil passage Lr3 formed at the position overlapping with the oil hole Lh7 in the axial direction by retreating radially inward over the entire circumference on the radially outer surface of the intermediate shaft M. ing. Since the oil flow between the oil hole Lh7 and the oil hole Lh8 is through the entire circumferential oil passage Lr3 formed over the entire circumference, the circumferential positions of the oil hole Lh7 and the oil hole Lh8 are equalized by relative rotation. Even if you do not do it, you can always distribute oil.
- the above-described seal ring 77 is disposed and is in a liquid-tight state.
- no seal ring or the like is disposed between the intermediate shaft M on the one side in the axial direction of the entire circumferential oil passage Lr3 and the input shaft I, and the oil supplied to the entire circumferential oil passage Lr3 is not oil holes Lh7.
- the oil supplied to the oil hole Lh8 is supplied to the needle bearing 72a and the support bearing 71 as described later.
- the torque converter TC is disposed on the other side in the axial direction of the support wall 4 and the rotor support member 23 of the rotating electrical machine MG.
- the first clutch C1 is disposed inside the outer shell support member 30 of the torque converter TC.
- the outer shell support member 30 is a cover member that forms the outer shell of the torque converter TC, and is drivingly connected so as to rotate integrally with the pump impeller 31. Inside the outer shell support member 30, a pump impeller 31, a turbine runner 41, a first clutch C1, a second clutch C2, and the like are arranged. In the present embodiment, the outer shell support member 30 is formed by welding a plurality of members.
- the outer shell support member 30 has a peripheral wall portion that covers the outer periphery, and includes at least a portion of the front cover member 32 that extends at least in the radial direction from one axial end portion of the peripheral wall portion, and at least from the other axial end portion of the peripheral wall portion.
- the front cover member 32 has an annular plate shape extending in the radial direction and the circumferential direction, and the outer shell support member 30 that covers one side in the axial direction of the torque converter TC. Part.
- the front cover member 32 refers to an annular plate-shaped portion that forms a part of the outer shell support member 30 and covers one side in the axial direction regardless of whether or not the members are welded. To do.
- the front cover member 32 includes a cylindrical second protrusion 6 that is formed integrally with the front cover member 32 and protrudes from the front cover member 32 in the axial direction toward the support wall 4 (one axial side).
- the second projecting portion 6 has a cylindrical shape that projects from the radially inner end of the front cover member 32 toward the one axial side.
- the second protrusion 6 is rotatably supported with respect to the first protrusion 5 of the support wall 4 via the support bearing 71 and is positioned in the radial direction.
- the second protrusion 6 is disposed so as to overlap the first protrusion 5 in the axial direction.
- the second projecting portion 6 is disposed so as to completely overlap the first projecting portion 5 in the axial direction.
- the support bearing 71 is attached between the radially inner side surface of the first protrusion 5 and the radially outer surface of the second protrusion 6.
- the second projecting portion 6 is fitted with the support bearing 71 on the radially outer surface, and the second projecting portion 6 is radial with respect to the first projecting portion 5 via the support bearing 71. Is positioned.
- the other axial side of the support bearing 71 has a diameter larger than that of the fitting surface on the other side in the axial direction of the fitting surface of the second protruding portion 6 on the radially outer surface of the second protruding portion 6. It is fixed in contact with the protruding portion (step portion in the axial direction) of the second protruding portion 6 protruding outward in the direction.
- the second protrusion 6 positions the support bearing 71 in the axial direction with respect to the second protrusion 6, and the second protrusion 6 is located with respect to the first protrusion 5 via the support bearing 71. Positioned in the axial direction.
- the radially inner side of the second projecting portion 6 forms a through-hole that penetrates the inner side and the outer side of the outer shell support member 30 in the axial direction on one axial side of the outer shell support member 30.
- the input shaft I passes through the through hole of the outer shell support member 30, and the input shaft I enables transmission of driving force between the engine E and the torque converter TC.
- the radially inner surface of the second protrusion 6 rotatably supports the radially outer surface of the input shaft I via the needle bearing 72a and the like, and the input shaft I is positioned in the radial direction. is doing.
- the needle bearing 72a is fixed in the axial direction by a snap ring or the like.
- the space in which the support bearing 71 between the first projecting portion 5 and the second projecting portion 6 is attached is liquid-tight by an oil seal 71a and an oil seal 71b on one axial side and the other axial side, respectively. .
- Oil is supplied to the space defined by the oil seal 71a and the oil seal 71b through the oil hole Lh8 as described above. Therefore, the support bearing 71 can be supplied with oil.
- the cylindrical space between the radially inner side surface of the first projecting portion 5 and the radially outer surface of the second projecting portion 6 is the other in the axial direction.
- an annular plate-like lid is formed by the oil seal 71b to make it liquid-tight.
- the space between the radially inner side surface of the first protrusion 5 and the input shaft I is made to be in a liquid-tight state by being covered with an annular plate by an oil seal 71a on one side in the axial direction.
- One axial end of the second protrusion 6 is disposed on the other axial end of the oil seal 71a. Therefore, the space on the radially outer side surface and the radially inner side surface of the second protrusion 6 is made liquid-tight by the oil seals 71a and 71b, and the support bearing 71 and the needle bearing 72a attached to the second protrusion 6 are provided. Can be supplied with oil.
- the oil supplied to the space between the first protrusion 5 and the second protrusion 6 from the oil hole Lh8 is, as shown in FIG. 3, the oil hole Lh6 and the drain pipe Lp1 formed in the first protrusion 5. Through the space. The drained oil is returned to an oil pan (not shown) and then resupplied to each oil supply object by the oil pump as described above.
- the front cover member 32 has a cylindrical protruding portion that protrudes from the radially inner end of the front cover member 32 to the other axial side opposite to the second protruding portion 6, and the radial direction of the protruding portion.
- the outer surface supports components such as the first piston 54 and the first return spring 55 of the first clutch C1.
- the front cover member 32 is provided on the front cover member 32 with a rotor support member 23, which will be described later, on the radially outer side of the second projecting portion 6 and on the radially inner side of the torque transmission connecting portion 13 which will be described later.
- a fitting portion on the front cover member side of the positioning fitting portion 12 that is fitted and positioned in the radial direction is provided.
- the front cover member 32 includes a third protrusion 7 that protrudes in the axial direction toward the support wall 4 (one side in the axial direction), and the third protrusion 7 is a front cover of the positioning fitting portion 12.
- the fitting part on the member side is configured.
- the radially outer surface of the third protrusion 7 constitutes a fitting surface 7 a on the front cover member 32 side of the positioning fitting portion 12, and the rotor support member 23 is a radially outer fitting surface of the third protrusion 7. 7a is fitted.
- the third projecting portion 7 is disposed so as to overlap in the axial direction with respect to the rotation support portion 11 including the first projecting portion 5, the second projecting portion 6, and the support bearing 71.
- the third projecting portion 7 has a cylindrical shape projecting from the front cover member 32 toward the one side in the axial direction. It overlaps in the direction and is arranged close to the radially outer side of the first protrusion 5.
- the 3rd protrusion part 7 is completely overlapped and arrange
- the third protrusion 7 of the front cover member 32 positions the rotor support member 23 in the radial direction.
- the front cover member 32 is positioned in the radial direction by the second protrusion 6 with respect to the first protrusion 5 of the support wall 4 via the support bearing 71. Therefore, the rotor support member 23 is positioned in the radial direction with respect to the first protrusion 5 of the support wall 4 via the third protrusion 7 of the front cover member 32.
- the front cover member 32 is spaced from the positioning fitting portion 12 on the radially outer side of the positioning fitting portion 12, and is connected to the rotor support member 23 and the front cover member 32 so that torque transmission is possible.
- a connecting portion 13a on the front cover member 32 side is provided.
- the connecting portion 13 a of the front cover member 32 is disposed so as to overlap with the rotation support portion 11 in the axial direction.
- the contact surface on one side in the axial direction that contacts the rotor support member 23 defines the radial position of the contact surface for flattening processing or to which torque is transmitted. Therefore, it is formed to protrude in the axial direction toward the rotor support member 23 (one side in the axial direction).
- the connecting portion 13a of the front cover member 32 is connected to the connecting portion 13b of the rotor support member 23 so that torque can be transmitted, and the rotor 22 is drivingly connected so as to rotate integrally with the pump impeller 31 of the torque converter TC. ing.
- the connecting portion 13a of the front cover member 32 is formed near the radially outer end of the front cover member 32 as shown in FIGS.
- the connecting portion 13b of the rotor support member 23 is fixed so as to rotate integrally with the connecting portion 13a of the front cover member 32 from one side in the axial direction by a connecting mechanism 13c such as a bolt or a washer.
- the connecting portion 13a of the front cover member 32 is formed with a bolt insertion hole and a screw thread that open on one side in the axial direction, and the bolt is inserted and screwed in from one side in the axial direction.
- the connecting portion 13a of the front cover member 32 is formed with a bolt insertion hole in the axial direction and the stress is increased, so that the thickness of the axial member is increased and protrudes to the other side in the axial direction. .
- the connecting portion 13a of the front cover member 32 is formed such that the contact surface on one side in the axial direction that contacts the rotor support member 23 protrudes to one side in the axial direction for flattening processing or the like.
- the surface on the one side in the axial direction of the front cover member 32 is relatively on the other side in the axial direction (rotor support member) on the radially inner side of the connection portion 13a than the contact surface with the rotor support member 23 of the connection portion 13a. Retired to the opposite side of 23).
- the rotor support member 23 is formed to be offset in the axial direction toward the front cover member 32 side (the other side in the axial direction) on the radially inner side of the torque transmission connecting portion 13 as described later.
- An offset portion 14 is provided.
- the connection part 13a of the front cover member 32 is provided with the attachment part of the connection mechanism 13c in the multiple places along the circumferential direction.
- the front cover member 32 is connected to a cylindrical member extending from the other axial side surface of the front cover member 32 to the other axial side.
- This cylindrical member constitutes a support member on the pump impeller 31 side of the first clutch C1 and the second clutch C2, and becomes a shared support member 50 shared by the first clutch C1 and the second clutch C2.
- the common support member 50 is referred to as a first clutch support member 51 when used as a component on the first clutch C1 side, and a second clutch support member 62 when used as a component on the second clutch C2 side. Called.
- a friction plate 56 of the first clutch C1 is attached to the radially inner side surface of the common support member 50, and a friction plate 66 of the second clutch C2 is attached to the radially outer side surface.
- the first clutch C1 and the second clutch C2 are arranged by effectively using both the radially inner and outer surfaces.
- 1st clutch hub 52 connected with the above-mentioned input shaft I is attached to the diameter direction inner side of friction plate 56 of first clutch C1. That is, the friction plate 56 is disposed between the first clutch support member 51 and the first clutch hub 52, and the first clutch support member 51 and the first clutch hub 52 of the first clutch C1 have the friction plate 56 as described later. To be engaged or released.
- a second clutch hub 61 connected to the turbine runner 41 is attached on the radially outer side of the friction plate 66 of the second clutch C2. That is, the friction plate 66 is disposed between the second clutch support member 62 and the second clutch hub 61, and the second clutch support member 62 and the second clutch hub 61 of the second clutch C2 have the friction plate 66 as described later.
- the second clutch hub 61 is a member integrally formed by an annular plate member and a cylindrical member extending radially outward from the radially outer surface of the turbine hub 44 connected to the intermediate shaft M.
- the second clutch hub 61 is connected to the intermediate shaft M and the turbine runner 41 via the turbine hub 44 so as to rotate integrally. Therefore, by providing the common support member 50 for the first clutch C1 and the second clutch C2 on the other side in the axial direction of the front cover member 32, the first clutch C1 and the second clutch C2 are arranged overlapping in the axial direction. Therefore, the first clutch C1 and the second clutch C2 can be arranged by effectively using the space on the other axial side of the front cover member 32 in the radial direction, and the overall axial length of the hybrid drive device 1 is kept short. be able to.
- the rear cover member 33 is formed so as to cover the other side in the axial direction of the pump impeller 31 and the torque converter TC, and has a circular hole in the central portion in the radial direction and the cross-sectional shape is convex toward the other side in the axial direction.
- the pump impeller 31 is configured by fixing a large number of blade-like blades inside the arcuately curved portion.
- the rear cover member 33 is formed with a cylindrical hub extending from the radially inner end of the rear cover member 33 to the other axial side. As described above, the hub of the rear cover member 33 is rotatably supported with respect to the pump cover 91 fixed to the intermediate support wall 90 constituting a part of the case 2 via the needle bearing 72b. It is positioned in the radial direction. Further, the end portion (not shown) on the other axial side of the hub of the rear cover member 33 is connected to rotate integrally with the inner rotor of the oil pump.
- the turbine runner 41 of the torque converter TC includes a turbine cover 42, blades, and a turbine hub 44.
- the turbine cover 42 is disposed between the second clutch C2 and the rear cover member 33 in the axial direction, has a circular hole at the center in the radial direction, and is curved in an arc shape in which a cross-sectional shape is convex toward one side in the axial direction. This is an annular member having the shape.
- a number of blade-shaped blades are formed on the turbine cover 42.
- the multiple blades of the turbine runner 41 are arranged to face the multiple blades of the pump impeller 31 at predetermined intervals in the axial direction.
- the radially inner end of the turbine cover 42 is connected so as to rotate integrally with the turbine hub 44 via a connecting member such as a rivet.
- the radially inner end of the turbine hub 44 is connected to the intermediate shaft M by spline fitting, and the turbine hub 44 rotates integrally with the intermediate shaft M.
- the stator 46 of the torque converter TC includes a blade, a one-way clutch 48, and a fixed sleeve 49.
- a large number of blades of the stator 46 are provided, and these blades are arranged between the blades of the pump impeller 31 and the blades of the turbine runner 41 in the axial direction. Further, the blade is connected to the fixed sleeve 49 via the one-way clutch 48 in a state in which only rotation in one circumferential direction is allowed and rotation in the other circumferential direction is restricted.
- the fixing sleeve 49 is fixed to the intermediate support wall 90 with the outer peripheral surface of the end portion on the other side in the axial direction coming into contact with the inner peripheral surface of the through hole formed in the radial center portion of the intermediate support wall 90 ( (See FIG. 2).
- the radially inner side surface of the fixed sleeve 49 supports the intermediate shaft M rotatably via a bearing (not shown) and is positioned in the radial direction. Therefore, the intermediate shaft M is rotatably supported with respect to the intermediate support wall 90 of the case 2 via the fixed sleeve 49 on the other side in the axial direction, and is positioned in the radial direction.
- the pump impeller 31, the turbine runner 41, and the stator 46 form an annular torque converter unit.
- the second clutch C2 is a friction engagement device that selectively connects the pump impeller 31 and the turbine runner 41 of the torque converter TC.
- the second clutch C2 includes a second clutch support member 62 connected to rotate integrally with a front cover member 32 connected to the pump impeller 31, as shown in FIG.
- a second clutch hub 61 connected to rotate integrally with the turbine hub 44 of the turbine runner 41, a friction plate 66, a turbine hub 44 functioning as a second clutch drum, and a second piston 64 are provided.
- the second piston 64 is urged to the other side in the axial direction by the second return spring 65.
- a liquid-tight second supply oil chamber H2 is formed between the turbine hub 44 and the second piston 64, and this second supply oil chamber H2 is formed in the intermediate shaft M (not shown).
- Oil of a predetermined hydraulic pressure controlled by a hydraulic control device is supplied through an oil hole Lh5 formed in the shaft center oil passage and the turbine hub 44.
- the second piston 64 expands the volume of the second supply oil chamber H2 (in this example, one side in the axial direction). )
- the driving force of one or both of the engine E and the rotating electrical machine MG is directly transmitted to the intermediate shaft M via the second clutch C2.
- the first clutch C1 is a friction engagement device that selectively drives and connects the engine E, the torque converter TC, and the rotating electrical machine MG as described above.
- the first clutch C1 includes a first clutch hub 52 connected to rotate integrally with the input shaft I and a front connected to the pump impeller 31, as shown in FIG.
- a first clutch support member 51, a friction plate 56, and a first piston 54 that are coupled to rotate integrally with the cover member 32 are provided.
- the front cover member 32 and the first clutch support member 51 function as a first clutch drum.
- the first piston 54 is urged toward the one side in the axial direction by the first return spring 55.
- a liquid-tight first supply oil chamber H1 is formed between the first clutch drum and the first piston 54.
- the first supply oil chamber H1 has a first shaft oil passage as described above. Oil of a predetermined hydraulic pressure controlled by the hydraulic control device is supplied through Lc1 and an oil hole Lh3 formed in the front cover member 32 (see FIG. 1).
- the first piston 54 expands the volume of the first supply oil chamber H1 (in this example, the other side in the axial direction). )
- the driving force of the engine E transmitted from the engine E is transmitted to the pump impeller 31 and the rotating electrical machine MG via the first clutch C1.
- the rotating electrical machine MG is disposed adjacent to the support wall 4 on the other axial side of the support wall 4 of the case 2.
- the stator 21 and the rotor 22 of the rotating electrical machine MG are disposed on the radially outer side of the front cover member 32.
- the stator 21 of the rotating electrical machine MG is fixed to the case 2 by a fastening member such as a bolt.
- the rotor 22 is rotatably supported with respect to the case 2 via the rotor support member 23, the front cover member 32, and the like, and is positioned in the radial direction.
- the rotating electrical machine MG is arranged coaxially with the input shaft I and the intermediate shaft M, and the axis X of the rotor 22 coincides with the rotational axes of the input shaft I and the intermediate shaft M. Further, the rotor 22 is connected to the pump impeller 31 of the torque converter TC via the rotor support member 23 and the front cover member 32 so as to rotate integrally.
- the rotor support member 23 is a member provided so as to extend at least in the radial direction and support the rotor 22.
- the rotor support member 23 is disposed in a space on the other axial side of the support wall 4 and on the one axial side of the front cover member 32, that is, a space between the support wall 4 and the front cover member 32.
- a positioning fitting portion 12 for fitting the rotor support member 23 to the front cover member 32 and positioning it in the radial direction is provided across the rotor support member 23 and the front cover member 32.
- the rotor support member 23 includes a fitting portion on the rotor support member 23 side of the positioning fitting portion 12.
- the rotor support member 23 has a fitting surface 23 a on the rotor support member 23 side that is fitted to the radially outer surface 7 a of the third protrusion 7 formed on the front cover member 32.
- the rotor support member 23 is provided so as to extend radially inward from the rotor 22, and is an annular plate member having a circular hole in the radial center.
- the rotor support member 23 is integrally formed with a cylindrical cylindrical portion that protrudes from the radially outer end of the annular plate member toward the one side and the other side in the axial direction. It is the shape prepared for.
- the inner peripheral surface of the rotor 22 is in contact with and fixed to the outer peripheral surface portion of the cylindrical portion.
- the radially inner side surface of the rotor support member 23 is a fitting portion (fitting surface 23a) on the rotor support member 23 side of the positioning fitting portion 12 with the front cover member 32.
- the positioning fitting portion 12 is disposed so as to overlap the rotation support portion 11 in the axial direction.
- the positioning fitting portion 12 is disposed so as to be completely overlapped in the axial direction with respect to each of the first protruding portion 5 and the second protruding portion 6.
- the positioning fitting portion 12 is disposed so as to overlap the rotor 22 in the axial direction.
- the positioning fitting part 12 shall point out the whole fitting part by the side of the front cover member 32, and the fitting part by the side of the rotor support member 23.
- the positioning fitting portion 12 is configured by the entire third protrusion 7 and the fitting surface 23 a on the radially inner side of the rotor support member 23.
- the rotor support member 23 is spaced apart from the positioning fitting portion 12 on the outer side in the radial direction of the positioning fitting portion 12, and is connected to the rotor support member 23 and the front cover member 32 so that torque transmission is possible.
- a connecting portion 13b on the rotor support member 23 side is provided.
- the connecting portion 13 b of the rotor support member 23 is disposed so as to overlap with the rotation support portion 11 in the axial direction.
- the connecting portion 13b of the rotor support member 23 is a portion that is in contact with an abutting surface that protrudes to one axial side of the connecting portion 13a of the front cover member 32.
- the connecting portion 13b of the rotor support member 23 is connected to the connecting portion 13a of the front cover member 32 so that torque can be transmitted, and the rotor 22 is drivingly connected so as to rotate integrally with the pump impeller 31 of the torque converter TC.
- the connecting portion 13b of the rotor support member 23 is fixed to the connecting portion 13a of the front cover member 32 from one side in the axial direction by a connecting mechanism 13c such as a bolt or a washer.
- the torque transmission connecting portion 13 is disposed so as to overlap the rotation support portion 11 in the axial direction. Further, the torque transmission connecting portion 13 and the rotor support member 23 are disposed so as to overlap with the rotor 22 in the axial direction.
- the torque transmission connecting portion 13 refers to the whole including the connecting mechanism 13c when the connecting portion 13a on the front cover member 32 side and the connecting portion 13b on the rotor support member 23 side or the connecting mechanism 13c are provided. That is, in this example, the torque transmission connecting portion 13 is configured by the connecting portion 13a of the front cover member 32, the connecting portion 13b on the rotor support member 23 side, and the connecting mechanism 13c as a whole.
- the positioning fitting portion 12 and the torque transmission connecting portion 13 are formed apart from each other, and the positioning fitting portion 12 is arranged radially inside and the torque transmission connecting portion 13 is arranged radially outside.
- the radial positioning accuracy and torque transmission capability of the rotor 22 can be improved at the same time. That is, since the positioning fitting portion 12 does not need to transmit torque, the member thickness near the positioning fitting portion 12 of the rotor support member 23 or the front cover member 32 can be formed thin. For this reason, processing of the positioning fitting portion 12 is facilitated, the processing accuracy of the fitting surfaces of the front cover member 32 and the rotor support member 23 for radial positioning can be improved, and the positioning fitting portion The axial length of the member in the vicinity of 12 can be kept short.
- the positioning fitting portion 12 is disposed radially inward of the torque transmission connecting portion 13, the circumference to be processed can be reduced, and the processing accuracy of the positioning fitting portion 12 can be further improved. Can do.
- the torque transmission connecting portion 13 is arranged on the radially outer side with respect to the positioning fitting portion 12, the shaft torque that can be transmitted by the torque transmitting connecting portion 13 can be increased by the lever principle. Further, each of the positioning fitting portion 12 and the torque transmission connecting portion 13 overlaps in the axial direction with respect to the rotation support portion 11 including the first protrusion portion 5, the second protrusion portion 6, and the support bearing 71.
- the positioning fitting portion 12 and the torque transmission connecting portion 13 can be arranged by effectively using the space on the radially outer side of the rotation support portion 11. Accordingly, the axial length of the hybrid drive device 1 as a whole can be kept short. Further, the first projecting portion 5, the second projecting portion 6, the support bearing 71, the rotor support member 23, the positioning fitting portion 12, and the torque transmission connecting portion 13 are arranged by effectively using the space in the radial direction of the rotor. The axial length of the hybrid drive device 1 as a whole can be kept short.
- the third projecting portion 7 is formed to project from the front cover member 32 in the axial direction to the support wall 4 side (one axial direction side), the space between the front cover member 32 and the support wall 4 is effective. By utilizing this, it is possible to form the fitting surface 7a on the front cover member 32 side that constitutes the positioning fitting portion 12. Further, since the protruding portion is provided, the radially outer surface of the protruding portion can be processed with high accuracy to form the fitting surface 7a for positioning the rotor support member 23 in the radial direction with high accuracy. Therefore, the processing accuracy for positioning the positioning fitting portion 12 can be improved, and the radial positioning accuracy of the rotor 22 is improved.
- the rotor support member 23 includes an offset portion 14 formed on the radially inner side of the torque transmission connecting portion 13 and offset in the axial direction toward the front cover member 32 (the other side in the axial direction).
- the rotation sensor 27 is disposed between the support wall 4 and the rotor support member 23 at a position overlapping the offset portion 14 of the rotor support member 23 in the radial direction.
- the torque transmission connecting portion 13 of the front cover member 32 is the rotor in the axial direction for flattening processing or to define the radial position of the contact surface to which torque is transmitted.
- the portion projecting to the support member 23 side (one side in the axial direction) and radially inward from the torque transmission connecting portion 13 of the front cover member 32 is the opposite side to the rotor support member 23 in the axial direction (the other side in the axial direction). Retired to.
- the rotor support member 23 is formed to be offset in the axial direction toward the front cover member 32 side (the other side in the axial direction) on the radially inner side of the torque transmission connecting portion 13. Further, since the rotor support member 23 does not need to transmit torque on the radially inner side of the torque transmission connecting portion 13, the member thickness in the axial direction can be made thinner than that of the torque transmitting connecting portion 13.
- the rotor support member 23 can be formed offset in the axial direction toward the front cover member 32 side (the other side in the axial direction) on the radially inner side of the torque transmission connecting portion 13.
- the space between the rotor support member 23 and the support wall 4 can be expanded in the axial direction.
- a rotation sensor 27 is disposed in a space between the rotor support member 23 and the support wall 4 that expands in the axial direction. Thereby, it is suppressed that the axial direction length as the whole hybrid drive device 1 becomes long.
- offsetting the rotor support member 23 in the axial direction at a certain radial position means that the axial member center line, which is the center line of the axial member width of the rotor support member 23 at a certain radial position, This means that the rotor support member 23 is translated in one axial direction or the other axial direction with respect to the axial center line of the rotor support member 23 at the radial position.
- the rotation sensor 27 is disposed so as to overlap the rotation support portion 11 in the axial direction.
- the rotation sensor 27 is disposed so as to be completely overlapped in the axial direction with respect to each of the first protrusion 5 and the second protrusion 6.
- the rotation sensor 27 is disposed so as to overlap the rotor 22 in the axial direction.
- the rotation sensor 27 can also be arranged by effectively utilizing the space outside the rotation support portion 11 in the radial direction.
- the rotation sensor 27 can also be arranged by effectively using the space inside the rotor 22 in the radial direction. Accordingly, the axial length of the hybrid drive device 1 as a whole can be kept short.
- the rotor support member 23 is a cylindrical first member that protrudes radially inward of the torque transmission connecting portion 13 and radially outward of the first protruding portion 5 toward the support wall 4 side (one axial direction side).
- 4 protrusions 8 are provided.
- the fourth protrusion 8 is disposed so as to overlap the first protrusion 5 in the axial direction.
- a rotation sensor 27 is disposed between the radially inner side surface of the fourth protrusion 8 and the radially outer surface of the first protrusion 5.
- the fourth protrusion 8 is formed between the torque transmission connecting portion 13 and the offset portion 14 of the rotor support member 23 in the radial direction, and has a cylindrical shape extending to one side in the axial direction. is doing.
- the sensor rotor 27a of the rotation sensor 27 is fixed to the radially inner side surface of the fourth protrusion 8 so as to rotate integrally with the rotor support member 23, and is positioned in the radial direction.
- the sensor stator 27 b of the rotation sensor 27 is fixed to the support wall 4 and is positioned in the radial direction by the radial outer surface of the first protrusion 5.
- the 4th protrusion part 8 overlaps with the rotation support part 11, and is arrange
- the 4th protrusion part 8 is completely overlapped and arrange
- the fourth protrusion 8 is disposed so as to overlap the rotor 22 in the axial direction.
- the 4th protrusion part 8 is projected and formed in the axial direction from the rotor support member 23 to the support wall 4 side, it rotates using the space between the rotor support member 23 and the support wall 4 effectively.
- a protrusion for attaching the sensor 27 to the rotor 22 side can be formed.
- the 4th protrusion part 8 is arrange
- the 4th protrusion part 8 can be arrange
- the rotation sensor 27 can be arranged in a radial space formed between the fourth protrusion 8 and the first protrusion 5. Accordingly, the rotation sensor 27 can be disposed by effectively using the space between the rotor support member 23 and the support wall 4 in the radial direction, and the axial length of the hybrid drive device 1 as a whole is increased. This can be suppressed. Further, since the support bearing 71 is attached to the radially inner side surface of the first projecting portion 5 and the rotation sensor 27 is attached to the radially outer side surface of the first projecting portion 5, the radially inner side surface of the first projecting portion 5 and The support bearing 71 and the rotation sensor 27 can be attached by making effective use of both the outer side surfaces.
- a new protrusion for separately attaching the rotation sensor 27 is formed. There is no need to do so, and the protrusion can be shared. Therefore, the space between the front cover member 32 and the support wall 4 can be effectively used in the radial direction to arrange each component member, and the overall axial length of the hybrid drive device 1 can be kept short. Can do. Moreover, the 3rd protrusion part 7 and the 4th protrusion part 8 can further be arrange
- the 3rd protrusion part 7 and the 4th protrusion part 8 can further be arrange
- the first protrusion 5 and the second protrusion 6 are completely overlapped with each other in the axial direction, and each of the first protrusion 5 and the second protrusion 6 is The 3rd protrusion part 7, the 4th protrusion part 8, and the rotation sensor 27 are arrange
- Second Embodiment A second embodiment of the present invention will be described with reference to the drawings. Also in this embodiment, the case where the vehicle drive device according to the present invention is applied to the hybrid drive device 1 will be described as an example.
- the overall configuration and the configuration of each part of the hybrid drive device 1 according to this embodiment are basically the same as those of the first embodiment.
- the diameter of the first protrusion 5 formed on the support wall 4 and the support bearing 71 in the second protrusion 6 formed on the front cover member 32 is sandwiched.
- the directional arrangement is formed opposite to that of the first embodiment.
- a fifth protrusion 9 for fixing the rotation sensor 27 to the support wall 4 is newly provided.
- the hybrid drive device 1 according to the present embodiment will be described in detail with a focus on differences from the first embodiment. Note that points not particularly specified are the same as those in the first embodiment.
- the radial arrangement of the first protrusion 5 formed on the support wall 4 of the case 2 with respect to the second protrusion 6 and the support bearing 71 is as described above.
- the first protrusion 5 is disposed on the radially inner side with respect to the second protrusion 6 and the support bearing 71.
- the 1st protrusion part 5 and the 2nd protrusion part 6 each overlap a part of axial direction. That is, the substantially half on the other axial side of the first protrusion 5 and the substantially half on the one axial side of the second protrusion 6 overlap in the axial direction.
- the support bearing 71 is attached between the radial direction outer side surface of the 1st protrusion part 5 and the radial direction inner side surface of the 2nd protrusion part 6 in the said overlap part.
- the radially inner surface of the support bearing 71 is fitted to the radially outer surface of the first protrusion 5, and the radially inner surface of the second protrusion 6 is fitted to the radially outer surface of the support bearing 71.
- the 1st protrusion part 5 of the support wall 4 supports the 2nd protrusion part 6 via the support bearing 71 rotatably, and is positioning to radial direction.
- the support wall 4 is on the radially outer side of the rotation support portion 11 composed of the first projecting portion 5, the second projecting portion 6, and the support bearing 71, and on the radially inner side of the fourth projecting portion 8.
- a cylindrical fifth protrusion 9 that protrudes toward the rotor support member 23 in the axial direction (the other side in the axial direction) is provided.
- the fifth projecting portion 9 and the fourth projecting portion 8 are disposed so as to overlap each other in the axial direction.
- the fourth projecting portion 8 is disposed so as to completely overlap with the fifth projecting portion 9 in the axial direction.
- a rotation sensor 27 is disposed between the radially inner side surface of the fourth protrusion 8 and the radially outer surface of the fifth protrusion 9.
- a sensor stator 27b of the rotation sensor 27 is fitted on the radially outer surface of the fifth protrusion 9 to position the sensor stator 27b of the rotation sensor 27 in the radial direction.
- the fifth protrusion 9 is a cylindrical protrusion.
- the radially outer side surface of the fifth protrusion 9 and the radially inner side surface of the stator core of the sensor stator 27b are fitted to each other so that the sensor stator 27b is positioned in the radial direction, and the stator core of the sensor stator 27b is connected at the connecting portion 27c.
- fastening members such as a volt
- the fifth protruding portion 9 is also arranged so as to overlap with the rotation support portion 11 in the axial direction.
- the fifth protruding portion 9 is disposed so as to be completely overlapped with the rotation support portion 11 in the axial direction.
- the first protruding portion 5 and the second protruding portion 6 have a configuration in which a part of each axial direction is overlapped. “To do” refers to overlapping with at least one of the first protrusion 5 and the second protrusion 6 in the axial direction.
- the fifth protrusion 9 is disposed so as to overlap the rotor 22 in the axial direction.
- the 4th protrusion part 8 is projected and formed in the axial direction from the rotor support member 23 to the support wall 4 side (one axial direction side), and the 5th protrusion part 9 is formed in the axial direction from the support wall 4. Since it is formed so as to protrude to the rotor support member 23 side (the other side in the axial direction), the rotation sensor 27 is connected to the rotor 22 side and the support wall 4 side by effectively utilizing the space between the rotor support member 23 and the support wall 4. Protrusions for attachment to can be formed.
- the 4th protrusion part 8 is arrange
- the 4th protrusion part 8 can be arrange
- the rotation sensor 27 can be arranged in a radial space formed between the fourth protrusion 8 and the fifth protrusion 9. Accordingly, the rotation sensor 27 can be disposed by effectively using the space between the rotor support member 23 and the support wall 4 in the radial direction, and the axial length of the hybrid drive device 1 as a whole is increased.
- the 5th protrusion part 9 is formed in the radial direction outer side of the rotation support part 11, it can design separately the rotation support part 11 and attachment of the rotation sensor 27, and each design freedom improves To do. Therefore, it is possible to attach the support bearing 71 between the radially outer side surface of the first projecting portion 5 and the radially inner side surface of the second projecting portion 6.
- the first projecting portion 5 of the support wall 4 can rotate the input shaft I via a needle bearing 72 a disposed between the radially inner side surface of the first projecting portion 5 and the radially outer surface of the input shaft I. While supporting, it is positioned in the radial direction. Therefore, the input shaft I can be positioned in the radial direction at a position overlapping with the first protrusion 5 in the axial direction. Moreover, since the 1st protrusion part 5 can support the input shaft I directly, without passing through other rotating members, such as the front cover member 32, the radial direction positioning accuracy of the input shaft I improves.
- the space in which the support bearing 71 between the first projecting portion 5 and the second projecting portion 6 is attached is liquid-tight by an oil seal 71a and an oil seal 71b on one axial side and the other axial side, respectively. .
- Oil is supplied to the space defined by the oil seal 71a and the oil seal 71b through the oil hole Lh8 as described above. Therefore, the support bearing 71 can be supplied with oil.
- the cylindrical space between the radially inner side surface of the fifth projecting portion 9 and the radially outer side surface of the second projecting portion 6 is the other side in the axial direction.
- An annular plate-like lid is formed by the oil seal 71b to make it liquid-tight.
- the space between the radially inner side surface of the first projecting portion 5 and the input shaft I is an end portion on one side in the axial direction of the first projecting portion 5 and is covered with an annular plate by an oil seal 71a. It is made liquid-tight. Therefore, the space on the radially outer side surface and the radially inner side surface of the first protrusion 5 is made liquid-tight by the oil seals 71a and 71b, and the support bearing 71 and the needle bearing 72a attached to the first protrusion 5 are provided. Can be supplied with oil.
- the fitting portion on the front cover member 32 side of the positioning fitting portion 12 is configured by the cylindrical third protruding portion 7 has been described as an example.
- the embodiment of the present invention is not limited to this. That is, the fitting portion of the front cover member 32 may have any shape as long as it can be fitted to the rotor support member 23 to position the rotor support member 23 in the radial direction. Forming the fitting portion of the member 32 in a substantially cylindrical shape having a fitting surface on the radially outer side is also one preferred embodiment of the present invention.
- the radial outer surface of the third protrusion 7 is fitted to the rotor support member 23 has been described as an example.
- the embodiment of the present invention is not limited to this. That is, the radially inner side surface of the third protrusion 7 may be configured to be fitted to the rotor support member 23.
- the rotor support member 23 has a cylindrical portion that protrudes to the other side in the axial direction.
- a configuration in which the radially outer side surface of the cylindrical portion of the rotor support member 23 and the radially inner side surface of the third projecting portion 7 are fitted is also one preferred embodiment of the present invention.
- the sensor rotor 27 a is attached to the fourth protrusion 8 of the rotor support member 23, and the first protrusion 5 (first embodiment) or the fifth protrusion 9 of the support wall 4.
- the case where the sensor stator 27b is attached to (second embodiment) has been described as an example.
- the embodiment of the present invention is not limited to this. That is, without providing the fourth projecting portion 8, the sensor rotor 27 a is directly connected to the rotor support member 23 by a fastening member such as a bolt on the radial inner side of the torque transmission connecting portion 13 (main body portion). It is also one of the preferred embodiments of the present invention to have a configuration to be attached to the.
- connection part 27c is set as the structure which attaches the sensor stator 27b to the support wall 4 by the connection part 27c in the position spaced apart from the 1st protrusion part 5 (1st embodiment) or the 5th protrusion part 9 (2nd embodiment) in radial direction. This is also one of the preferred embodiments of the present invention.
- the 1st protrusion part 5 and the 2nd protrusion part 6 mutually overlap in the axial direction completely, and with respect to each of the 1st protrusion part 5 and the 2nd protrusion part 6.
- the case where the third projecting portion 7, the fourth projecting portion 8, and the rotation sensor 27 are arranged so as to overlap completely in the axial direction has been described as an example.
- the embodiment of the present invention is not limited to this. That is, in the first embodiment, the first projecting portion 5 and the second projecting portion 6 may be configured such that a part of each axial direction overlaps in the axial direction.
- the first projecting portion It is also possible to configure the present invention so that at least a part of the fifth or second projecting portion 6, the third projecting portion 7, the fourth projecting portion 8, and the rotation sensor 27 are arranged to overlap each other in the axial direction.
- the first projecting portion 5 and the second projecting portion 6 are partially overlapped in the axial direction of the first projecting portion 5 or the second projecting portion 6.
- positioned overlapping in an axial direction was demonstrated as an example.
- the embodiment of the present invention is not limited to this.
- the first protrusion 5 and the second protrusion 6 may be configured to completely overlap each other in the axial direction.
- the first protrusion 5 and the second protrusion The third protrusion 7, the fourth protrusion 8, the fifth protrusion 9, and the rotation sensor 27 may be configured so as to be completely overlapped with each other in the axial direction. It is one of the preferred embodiments of the invention.
- the power transmission device may be any device as long as it transmits a driving force.
- the power transmission device includes only a pump impeller 31 as a driving side rotating member and a turbine runner 41 as a driven side rotating member. It is also one preferred embodiment of the present invention to use a fluid coupling or the like as a power transmission device.
- the rotor support member 23 extends radially inward from the vicinity of the axial center of the radially inner side surface of the rotor 22 to support the rotor 22.
- the case where the rotation sensors 27 are arranged overlapping in the axial direction has been described as an example.
- the embodiment of the present invention is not limited to this.
- the rotor support member 23 may be configured to support the rotor 22 by extending radially inward from, for example, the vicinity of the end portion on one axial side other than the vicinity of the axial center of the radially inner side surface of the rotor 22. It is one of the preferred embodiments of the present invention.
- the configuration of a part of the portion 13 and the rotation sensor 27 is arranged so as not to have a portion that is in the same position in the axial direction with respect to the rotor 22. This is one of the embodiments.
- the rotor support member 23 has the offset portion 14 formed by being offset toward the front cover member 32 side in the axial direction on the radially inner side of the torque transmission connecting portion 13.
- the case where the rotation sensor 27 is disposed at a position overlapping the offset portion 17 in the radial direction has been described as an example.
- the embodiment of the present invention is not limited to this. That is, the rotor support member 23 does not have the offset portion 14 and is configured so that the rotor support member 23 is formed in an annular plate shape in which the axial center line of the member is aligned over the entire radial direction. Is also one preferred embodiment of the present invention.
- the rotation sensor 27 is arranged at a position overlapping with the portion of the rotor support member 23 on the radially inner side of the torque transmission connecting portion 13 in the radial direction. Configuration is also one of the preferred embodiments of the present invention.
- a driving force output from the rotating electrical machine is output via a power transmission device such as a torque converter. It can utilize suitably for the comprised drive device.
- Hybrid drive device vehicle drive device
- drive case case 4: support wall 5: first protrusion 6: second protrusion 7: third protrusion 8: fourth protrusion 9: fifth protrusion 11: rotation support 12: positioning fitting part 13: torque transmission connection Part 14: offset part 22: rotor 23: rotor support member 27: rotation sensor 32: front cover member 71: support bearing MG: rotating electrical machine E: engine TC: torque converter (power transmission device) X: Axis center
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Abstract
Description
このような車両用駆動装置においては、回転電機は、動力伝動装置もしくはエンジンと相互に駆動力を伝達可能に連結される必要がある。また、回転電機は、動力伝動装置等と同様に、軸心周りに回転可能な状態で支持される必要がある。この場合、伝達可能な駆動力すなわち軸トルクを十分大きく確保できるように連結されることが好ましく、また軸心精度が十分高く確保できることが好ましい。
また、軸心は、動力伝動装置を収容する非回転部材であるケースを基準に画定されるため、各回転部材は、ケースに形成された支持部に対して支持軸受等を介して軸心周りに回転可能に支持される必要がある。
また、入力軸の軸心は、ケースに形成された支持部により支持軸受を介して画定されており、入力軸に連結されている車両用駆動装置及びロータは、各連結部で入力軸の軸心に一致するように軸心合わせをされている。
この点、特許文献1に記載の車両用駆動装置では、回転電機は、動力伝動装置とともにケース内に収容され、ケースの径方向内側に延びる支持壁と、動力伝動装置のフロントカバーとの間の空間に、入力軸のハブとロータの支持部材の連結部が配置されている。
また、本願において、2つの部材の配置に関して、ある方向に「重複」とは、2つの部材のそれぞれが、当該方向の配置に関して同じ位置となる部分を少なくとも一部に有することを指す。
また、「回転電機」は、モータ(電動機)、ジェネレータ(発電機)、及び必要に応じてモータ及びジェネレータの双方の機能を果たすモータ・ジェネレータのいずれをも含む概念として用いている。
また、位置決め嵌合部とトルク伝達連結部のそれぞれが、第1突出部、第2突出部、及び支持軸受で構成される回転支持部に対して、軸方向に重複して配置されるので、回転支持部の径方向外側の空間を有効利用して、位置決め嵌合部とトルク伝達連結部を配置することができる。よって、車両用駆動装置の全体としての軸方向長さを短く抑えることができる。
また、このような第3突出部を軸方向の突出部としているため、当該第3突出部の径方向外側面を高精度に加工してロータ支持部材の径方向位置決めのための嵌合面とすることができる。そのため、位置決め嵌合部の位置決めのための加工精度を向上でき、ロータの径方向位置決め精度が向上する。
また、第1突出部の径方向外側面に回転センサが取り付けられ、第1突出部の径方向内側面に支持軸受が取り付けられるため、第1突出部の径方向内側面及び外側面の両面を有効利用して、支持軸受及び回転センサを取り付けることができる。よって、支持壁に回転センサの取り付けのための突出部を新たに形成する必要がなく、突出部を共用化できる。従って、フロントカバー部材と支持壁との間の空間を径方向に有効利用して、各構成部品を配置することができ、車両用駆動装置の全体としての軸方向長さを短く抑えることができる。
また、第5突出部は、回転支持部の径方向外側に形成されているので、回転支持部と、回転センサの取り付けとを分離して設計でき、それぞれの設計自由度が向上する。そのため、第1突出部の径方向外側面と第2突出部の径方向内側面との間に支持軸受を取り付けることも可能になる。
本発明の第一の実施形態について図面に基づいて説明する。本実施形態においては、本発明に係る車両用駆動装置を、ハイブリッド駆動装置1に適用した場合を例として説明する。ハイブリッド駆動装置1は、車両の駆動力源としてエンジンE及び回転電機MGの一方又は双方を用いるハイブリッド車両用の駆動装置である。このハイブリッド駆動装置1は、図3に示すように、軸心X周りに回転するロータ22を有する回転電機MGと、エンジンE及び回転電機MGからの駆動力が伝達される動力伝動装置としてのトルクコンバータTCと、回転電機MGとトルクコンバータTCとを収容する駆動装置ケース2(以下、単に「ケース2」と言う。)と、を備えている。なお、以下の説明では、特に断らない限り、軸心Xを基準として、軸方向、周方向、径方向を定義している。
まず、本実施形態に係るハイブリッド駆動装置1の全体構成について説明する。図2に示すように、このハイブリッド駆動装置1は、第一の駆動力源としてのエンジンEに駆動連結される入力軸Iと、トルクコンバータTCに駆動連結される第二の駆動力源としての回転電機MGと、エンジンEとトルクコンバータTC及び回転電機MGとの間の駆動力の断接を行う第一クラッチC1と、トルクコンバータTCに中間軸Mを介して駆動連結される変速装置TMと、車輪Wに駆動連結される出力軸Oと、を備えており、これらはケース2に収容されている。
次に、本実施形態に係るハイブリッド駆動装置1の各部の構成について、図1、3を参照して説明する。上記のとおり、ハイブリッド駆動装置1は、入力軸I、中間軸M、出力軸O、回転電機MG、トルクコンバータTC、変速装置TM、第一クラッチC1、及びケース2等を備えている。以下、このハイブリッド駆動装置1の各部の構成について詳細に説明する。
図3に示すように、エンジンEにフライホイール81が連結されている。このフライホイール81は、従来の各種エンジンに取り付けられているものと同様に、エンジンEのトルク変動を抑制するためのものであり、回転慣性モーメントの大きい円板状の部材である。このフライホイール81に制振機構であるダンパDPが連結されている。このダンパDPは、フライホイール81から入力されるトルクの振動又は変動を減衰させて、振動の振幅を平滑化して出力する機構であり、必要に応じて各種の構成のものを使用することができる。一般的には、相対回転可能な入力側の部材と出力側の部材との間に、ばね等の弾性体を介在させ、その弾性体の伸縮によって振動を減衰させる機構のものを使用することができる。ダンパDPの入力側の部材は、フライホイール81に連結されており、出力側の部材は入力軸Iに連結されているため、エンジンEの駆動力がハイブリッド駆動装置1に入力される。また、フライホイール81又はダンパDPは、選択的に採用することができる部材であって、これらの一方もしくは双方を省いてエンジンEと入力軸Iとを連結してもよい。なお、ダンパDPの入力側、出力側としたが、出力側の部材から入力側の部材にもトルク伝達でき、ダンパDPの入力側の部材と出力側の部材で相互にトルク伝達可能である。
ケース2は、上記のように、その内部にトルクコンバータTC及び回転電機MG等の各収容部品を収容する略円筒状の部材であって、非回転部材である。また、ケース2は、入力軸I、中間軸M、トルクコンバータTC、及び回転電機MGのロータ22等の各回転部材を、ケース2のエンジンE側(軸方向一方側)及び変速装置TM側(軸方向他方側)に形成される各支持部により軸心X周りに回転可能に支持するとともに、径方向に位置決めする。図3に示すように、ケース2は、各収容部品の外周を覆うケース周壁3と、ケース2の軸方向一方側(図3における左側)の開口を塞ぐとともに各回転部材を軸方向一方側で回転可能に支持する支持壁4を備えている。更に、このケース2は、軸方向他方側(図3における右側)でトルクコンバータTCと変速装置TMとの間に配置されるとともに各回転部材を軸方向他方側で回転可能に支持する中間支持壁90(図2参照)を備えている。また、本実施形態においては、ケース2は、第一ケース2aと、当該第一ケース2aの軸方向他方側に取り付けられる第二ケース2bと、に分割可能に構成されている。ここで、第一ケース2aにはケース周壁3の軸方向一方側の一部分と支持壁4とが一体的に形成される。また、第二ケース2bには、ケース周壁3の軸方向他方側の残りの部分が形成されるとともに、中間支持壁90が取り付けられる。ケース2内において、ケース周壁2と支持壁4と中間支持壁90との間に画定される空間には、トルクコンバータTC、回転電機MG、及び第一クラッチC1等が収容されている。また、図3には示されていないが、ケース2内において中間支持壁90の軸方向他方側に変速装置TMが収容されている。
入力軸Iは、エンジンEの駆動力をハイブリッド駆動装置1内に入力するための軸である。図3に示すように、入力軸Iの先端部(図3での左側端部)が、ダンパDPの内周部を貫通して挿入されており、入力軸Iは、ダンパDPの出力側の部材に形成されたボス部82とトルク伝達可能にスプライン嵌合されている。よって、入力軸Iは、ダンパDPを介してエンジンEのエンジン出力軸と一体回転するように連結されている。また、入力軸Iの軸方向一方側の端部は、エンジンEの出力軸の軸方向他方側の端部に形成された中空の円筒状部内に挿入されており、このエンジンEの円筒状部の径方向内側面と入力軸Iの先端部の径方向外側面との間には軸受74が配置されている。これにより、入力軸Iは、エンジンEの出力軸に対して、軸受74を介して相対回転可能に支持されているので、入力軸の軸心XとエンジンEの出力軸の軸心ズレを抑制でき、エンジンEとハイブリッド駆動装置1の間の軸心ズレによる回転振動を抑制できる。
図3に示すように、トルクコンバータTCは、支持壁4及び回転電機MGのロータ支持部材23の軸方向他方側に配置されている。本実施形態では、第一クラッチC1は、トルクコンバータTCの外殻支持部材30の内側に配置されている。
第一クラッチC1は、上記のとおりエンジンEと、トルクコンバータTC及び回転電機MGとを選択的に駆動連結する摩擦係合装置である。このような機能を実現するため、第一クラッチC1は、図3に示すように、入力軸Iと一体回転するように連結された第一クラッチハブ52と、ポンプインペラ31と連結されているフロントカバー部材32と一体回転するように連結された第一クラッチ支持部材51と、摩擦プレート56と、第一ピストン54と、を備えている。なお、フロントカバー部材32及び第一クラッチ支持部材51は、第一クラッチドラムとして機能する。第一ピストン54は、第一リターンスプリング55により軸方向一方側に付勢されている。更に、第一クラッチドラムと第一ピストン54との間には液密状態の第一供給油室H1が形成され、この第一供給油室H1には、上記のように第一軸心油路Lc1及びフロントカバー部材32に形成された油穴Lh3等を介して油圧制御装置により制御された所定油圧の油が供給される(図1を参照)。第一供給油室H1の油圧が上昇して第一リターンスプリング55の付勢力よりも大きくなると、第一ピストン54は第一供給油室H1の容積を広げる方向(本例では、軸方向他方側)に移動して摩擦プレート56どうしを互いに係合させる。その結果、エンジンEから伝達されたエンジンEの駆動力が第一クラッチC1を介してポンプインペラ31及び回転電機MGに伝達される。
図3に示すように、回転電機MGは、ケース2の支持壁4の軸方向他方側に、当該支持壁4に隣接して配置されている。回転電機MGのステータ21とロータ22は、フロントカバー部材32の径方向外側に配置されている。回転電機MGのステータ21は、ボルト等の締結部材によりケース2に固定されている。ロータ22は、上記のように、ロータ支持部材23及びフロントカバー部材32等を介してケース2に対して回転可能に支持されているとともに、径方向に位置決めをされている。なお、回転電機MGは入力軸I及び中間軸Mと同軸状に配置されており、ロータ22の軸心Xは、入力軸I及び中間軸Mの回転軸心に一致している。また、ロータ22は、ロータ支持部材23及びフロントカバー部材32を介してトルクコンバータTCのポンプインペラ31と一体回転するように連結されている。
また、位置決め嵌合部12とトルク伝達連結部13のそれぞれが、第1突出部5、第2突出部6、及び支持軸受71で構成される回転支持部11に対して、軸方向に重複して配置されるので、回転支持部11の径方向外側の空間を有効利用して、位置決め嵌合部12とトルク伝達連結部13を配置することができる。よって、ハイブリッド駆動装置1の全体としての軸方向長さを短く抑えることができる。また、ロータの径方向内側の空間を有効利用して、第1突出部5、第2突出部6、支持軸受71、ロータ支持部材23、位置決め嵌合部12、及びトルク伝達連結部13を配置することができ、ハイブリッド駆動装置1の全体としての軸方向長さを短く抑えることができる。
また、第1突出部5の径方向内側面に支持軸受71が取り付けられ、第1突出部5の径方向外側面に回転センサ27が取り付けられるため、第1突出部5の径方向内側面及び外側面の両面を有効利用して、支持軸受71及び回転センサ27を取り付けることができる。よって、支持壁4に支持軸受71を介してフロントカバー部材32を回転可能に支持するための第1突出部5を形成する以外には、回転センサ27を別途取り付けるための突出部を新たに形成する必要がなく、突出部を共用化できる。従って、フロントカバー部材32と支持壁4との間の空間を径方向に有効利用して、各構成部材を配置することができ、ハイブリッド駆動装置1の全体としての軸方向長さを短く抑えることができる。
また、回転支持部11の径方向外側の空間を有効利用して、第3突出部7、及び第4突出部8も更に配置することができる。また、ロータ22の径方向内側の空間を有効利用して、第3突出部7、及び第4突出部8も更に配置することができる。よって、ハイブリッド駆動装置1の全体としての軸方向長さを短く抑えることができる。
本発明の第二の実施形態について図面に基づいて説明する。本実施形態においても、本発明に係る車両用駆動装置を、ハイブリッド駆動装置1に適用した場合を例として説明する。本実施形態に係るハイブリッド駆動装置1の全体構成及び各部の構成は、基本的には上記第一の実施形態と同様である。但し、本実施形態においては、図4に示すように、支持壁4に形成された第1突出部5、及びフロントカバー部材32に形成された第2突出部6における支持軸受71を挟んだ径方向の配置が、上記第一の実施形態と逆転して形成されている。これに対応して、回転センサ27を支持壁4に固定する第5突出部9が新たに設けられている。また、オイルシール71a、71bの配置も変更されている。以下では、本実施形態に係るハイブリッド駆動装置1について、上記第一の実施形態との相違点を中心に詳細に説明する。なお、特に明記しない点については、上記第一の実施形態と同様とする。
本実施形態においては、図4に示すように、ケース2の支持壁4に形成される第1突出部5の、第2突出部6及び支持軸受71に対する径方向の配置が、上記第一の実施形態と異なっている。すなわち、第1突出部5は、第2突出部6及び支持軸受71に対して径方向内側に配置されている。また、本実施形態では、第1突出部5と第2突出部6とはそれぞれ軸方向の一部が重複している。すなわち、第1突出部5の軸方向他方側の略半分と第2突出部6の軸方向一方側の略半分とが軸方向に重複している。そして、当該重複部位における第1突出部5の径方向外側面と第2突出部6の径方向内側面との間に支持軸受71が取り付けられている。本例では、第1突出部5の径方向外側面に支持軸受71の径方向内側面が嵌合され、支持軸受71の径方向外側面に第2突出部6の径方向内側面が嵌合されている。よって、支持壁4の第1突出部5が、支持軸受71を介して、第2突出部6を回転可能に支持するとともに、径方向に位置決めしている。
また、第5突出部9は、回転支持部11の径方向外側に形成されているので、回転支持部11と、回転センサ27の取り付けとを分離して設計でき、それぞれの設計自由度が向上する。そのため、第1突出部5の径方向外側面と第2突出部6の径方向内側面との間に支持軸受71を取り付けることも可能になる。
(1)上記の各実施形態においては、トルク伝達連結部13の連結機構13cがボルト等により構成された場合を例として説明した。しかし、本発明の実施形態はこれに限定されない。すなわち、ロータ支持部材23とフロントカバー部材32とをトルク伝達可能に連結する構成であれば、連結機構13cを、例えば、溶接等の連結機構とする構成とすることも、本発明の好適な実施形態の一つである。
また、上記第二実施形態においては、第1突出部5と第2突出部6とは、それぞれの軸方向の一部が軸方向に重複し、第1突出部5又は第2突出部6の少なくとも一部と、第3突出部7、第4突出部8、第5突出部9、及び回転センサ27が、それぞれ軸方向に重複して配置される場合を例として説明した。しかし、本発明の実施形態はこれに限定されない。すなわち、第二実施形態において、第1突出部5と第2突出部6とは、互いに軸方向に完全重複するように構成してもよく、この場合、第1突出部5及び第2突出部6のそれぞれに対して、第3突出部7、第4突出部8、第5突出部9、及び回転センサ27が、それぞれ軸方向に完全重複して配置されるように構成することも、本発明の好適な実施形態の一つである。
2:駆動装置ケース(ケース)
4:支持壁
5:第1突出部
6:第2突出部
7:第3突出部
8:第4突出部
9:第5突出部
11:回転支持部
12:位置決め嵌合部
13:トルク伝達連結部
14:オフセット部
22:ロータ
23:ロータ支持部材
27:回転センサ
32:フロントカバー部材
71:支持軸受
MG:回転電機
E:エンジン
TC:トルクコンバータ(動力伝動装置)
X:軸心
Claims (14)
- 軸心周りに回転するロータを有する回転電機と、当該回転電機及びエンジンからの駆動力が伝達される動力伝動装置と、前記回転電機及び前記動力伝動装置を収容するケースと、を備える車両用駆動装置であって、
前記ケースは、少なくとも径方向内側に延びる支持壁を有すると共に、前記支持壁と一体的に形成されて前記支持壁から軸方向に前記動力伝動装置側へ突出する筒状の第1突出部を備え、
前記動力伝動装置は、少なくとも径方向に延びるフロントカバー部材を有すると共に、軸方向に前記支持壁側へ突出する筒状の第2突出部を備え、
前記第2突出部は、支持軸受を介して前記第1突出部に対して回転可能に支持され、
前記ロータは、少なくとも径方向内側に延びて前記ロータを支持するロータ支持部材を備え、
前記第2突出部の径方向外側に、前記ロータ支持部材を前記フロントカバー部材に嵌合させて径方向に位置決めする位置決め嵌合部を備え、
前記位置決め嵌合部の径方向外側に、当該位置決め嵌合部と離間して、前記ロータ支持部材と前記フロントカバー部材とをトルク伝達可能に連結するトルク伝達連結部を備え、
前記第1突出部、前記第2突出部、及び前記支持軸受で構成される回転支持部に対して、前記位置決め嵌合部及び前記トルク伝達連結部のそれぞれが軸方向に重複して配置されている車両用駆動装置。 - 前記ロータに対して、前記第1突出部、前記第2突出部、前記支持軸受、前記ロータ支持部材、前記位置決め嵌合部、及び前記トルク伝達連結部がそれぞれ軸方向に重複して配置されている請求項1に記載の車両用駆動装置。
- 前記ロータ支持部材は、前記トルク伝達連結部の径方向内側に、軸方向に前記フロントカバー部材側へオフセットして形成されたオフセット部を有し、
前記支持壁と前記ロータ支持部材との間であって、当該ロータ支持部材の前記オフセット部と径方向に重複する位置に回転センサが配置されている請求項1又は2に記載の車両用駆動装置。 - 前記回転支持部に対して、前記回転センサが軸方向に重複して配置されている請求項3に記載の車両用駆動装置。
- 前記ロータに対して、前記回転センサが軸方向に重複して配置されている請求項3又は4に記載の車両用駆動装置。
- 前記フロントカバー部材は、前記第2突出部の径方向外側に、軸方向に前記支持壁側へ突出する第3突出部を備え、
前記第3突出部の径方向外側面が、前記位置決め嵌合部の前記フロントカバー部材側の嵌合面を構成し、前記ロータ支持部材が前記第3突出部の径方向外側面に嵌合される請求項1から5のいずれか一項に記載の車両用駆動装置。 - 前記回転支持部に対して、前記第3突出部が軸方向に重複して配置されている請求項6に記載の車両用駆動装置。
- 前記ロータに対して、前記第3突出部が軸方向に重複して配置されている請求項6又は7に記載の車両用駆動装置。
- 前記第1突出部の径方向内側面と前記第2突出部の径方向外側面との間に前記支持軸受が取り付けられ、
前記ロータ支持部材は、前記トルク伝達連結部の径方向内側であって、前記第1突出部の径方向外側に、軸方向に前記支持壁側へ突出する筒状の第4突出部を備え、
前記第4突出部は、前記第1突出部と軸方向に重複して配置され、
前記第4突出部の径方向内側面と前記第1突出部の径方向外側面との間に回転センサが配置されている請求項1から8のいずれか一項に記載の車両用駆動装置。 - 前記回転支持部に対して、前記第4突出部が軸方向に重複して配置されている請求項9に記載の車両用駆動装置。
- 前記ロータに対して、前記第4突出部が軸方向に重複して配置されている請求項9又は10に記載の車両用駆動装置。
- 前記第1突出部の径方向外側面と前記第2突出部の径方向内側面との間に前記支持軸受が取り付けられ、
前記ロータ支持部材は、前記トルク伝達連結部の径方向内側に、軸方向に前記支持壁側へ突出する筒状の第4突出部を備え、
前記支持壁は、前記回転支持部の径方向外側であって、前記第4突出部の径方向内側に、軸方向に前記ロータ支持部材側へ突出する筒状の第5突出部を備え、
前記第4突出部と前記第5突出部とは、互いに軸方向に重複して配置され、
前記第4突出部の径方向内側面と前記第5突出部の径方向外側面との間に回転センサが配置されている請求項1から8のいずれか一項に記載の車両用駆動装置。 - 前記回転支持部に対して、前記第4突出部及び前記第5突出部がそれぞれ軸方向に重複して配置されている請求項12に記載の車両用駆動装置。
- 前記ロータに対して、前記第4突出部及び前記第5突出部がそれぞれ軸方向に重複して配置されている請求項12又は13に記載の車両用駆動装置。
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JP2000085387A (ja) * | 1998-09-17 | 2000-03-28 | Toyota Motor Corp | 車両用駆動装置 |
JP2000289475A (ja) * | 1999-04-12 | 2000-10-17 | Aisin Aw Co Ltd | ハイブリット車用駆動装置 |
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WO2006054661A1 (ja) * | 2004-11-19 | 2006-05-26 | Aisin Aw Co., Ltd. | ハイブリッド車用駆動装置 |
JP4584171B2 (ja) * | 2006-03-23 | 2010-11-17 | トヨタ自動車株式会社 | 動力伝達装置およびその組立方法 |
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JP5131153B2 (ja) * | 2008-10-28 | 2013-01-30 | アイシン・エィ・ダブリュ株式会社 | 車両用駆動装置 |
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JP4981149B2 (ja) * | 2010-01-14 | 2012-07-18 | トヨタ自動車株式会社 | 動力伝達装置 |
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- 2010-12-17 DE DE201011003514 patent/DE112010003514T5/de not_active Withdrawn
- 2010-12-17 WO PCT/JP2010/072754 patent/WO2011074662A1/ja active Application Filing
- 2010-12-17 US US13/505,074 patent/US8652001B2/en not_active Expired - Fee Related
- 2010-12-17 CN CN201080049226.0A patent/CN102712244B/zh not_active Expired - Fee Related
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JP2000289475A (ja) * | 1999-04-12 | 2000-10-17 | Aisin Aw Co Ltd | ハイブリット車用駆動装置 |
JP2002103998A (ja) * | 2000-09-26 | 2002-04-09 | Aisin Aw Co Ltd | ハイブリッド車用駆動装置 |
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Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
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CN103717942A (zh) * | 2011-08-06 | 2014-04-09 | 戴姆勒股份公司 | 用于机动车的扭矩转换装置 |
US20140144742A1 (en) * | 2011-08-06 | 2014-05-29 | Daimler Ag | Torque converter device for a motor vehicle |
US8991576B2 (en) * | 2011-08-06 | 2015-03-31 | Daimler Ag | Torque converter device for a motor vehicle |
CN103717942B (zh) * | 2011-08-06 | 2017-06-13 | 戴姆勒股份公司 | 用于机动车的扭矩转换装置 |
CN102390250A (zh) * | 2011-09-09 | 2012-03-28 | 耿军 | 混合动力汽车充电发动机 |
EP2684725B2 (de) † | 2012-07-10 | 2022-06-29 | Schaeffler Technologies AG & Co. KG | Lagerungssystem für ein Antriebssystem |
WO2018039240A1 (en) * | 2016-08-23 | 2018-03-01 | Schaeffler Technologies AG & Co. KG | Rotor carrier assembly |
US10465780B2 (en) | 2016-08-23 | 2019-11-05 | Schaeffler Technologies AG & Co. KG | Rotor carrier assembly |
CN113811704A (zh) * | 2019-05-10 | 2021-12-17 | 株式会社法雷奥凯佩科 | 具有带有双活塞组件的锁止离合器和可选择单向离合器的流体动力扭矩耦合装置 |
Also Published As
Publication number | Publication date |
---|---|
US8652001B2 (en) | 2014-02-18 |
JP5255555B2 (ja) | 2013-08-07 |
JP2011126460A (ja) | 2011-06-30 |
US20120242199A1 (en) | 2012-09-27 |
DE112010003514T5 (de) | 2012-10-25 |
CN102712244A (zh) | 2012-10-03 |
CN102712244B (zh) | 2015-03-11 |
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