WO2011122128A1 - ハイブリッド駆動装置 - Google Patents
ハイブリッド駆動装置 Download PDFInfo
- Publication number
- WO2011122128A1 WO2011122128A1 PCT/JP2011/052863 JP2011052863W WO2011122128A1 WO 2011122128 A1 WO2011122128 A1 WO 2011122128A1 JP 2011052863 W JP2011052863 W JP 2011052863W WO 2011122128 A1 WO2011122128 A1 WO 2011122128A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- axial
- axial direction
- clutch
- clutch housing
- shaft
- Prior art date
Links
Images
Classifications
-
- 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
- B60K6/38—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the driveline clutches
- B60K6/387—Actuated clutches, i.e. clutches engaged or disengaged by electric, hydraulic or mechanical actuating means
-
- 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
- B60K6/405—Housings
-
- 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
-
- 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
-
- 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
- B60L50/40—Electric propulsion with power supplied within the vehicle using propulsion power supplied by capacitors
-
- 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
-
- 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
- F16D25/12—Details not specific to one of the before-mentioned types
- F16D25/123—Details not specific to one of the before-mentioned types in view of cooling and lubrication
-
- 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
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
- B60L2240/00—Control parameters of input or output; Target parameters
- B60L2240/10—Vehicle control parameters
- B60L2240/36—Temperature of vehicle components or parts
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/62—Hybrid vehicles
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/70—Energy storage systems for electromobility, e.g. batteries
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/7072—Electromobility specific charging systems or methods for batteries, ultracapacitors, supercapacitors or double-layer capacitors
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19014—Plural prime movers selectively coupled to common output
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19023—Plural power paths to and/or from gearing
- Y10T74/19051—Single driven plural drives
Definitions
- the present invention includes a first shaft that is drivingly connected to an internal combustion engine, a rotating electrical machine, a second shaft that is disposed coaxially with the first shaft and is drivingly connected to the rotating electrical machine and a transmission mechanism, a first shaft, and a second shaft
- the present invention relates to a hybrid drive device including a clutch provided so as to be able to switch between transmission and disconnection of a driving force with a shaft, and a case that houses a first shaft, a second shaft, a rotating electrical machine, and a clutch.
- a hybrid drive device including a clutch that can be switched between transmission and disconnection of the driving force, a first shaft, a second shaft, a rotating electrical machine, and a case that houses the clutch for example, Patent Document 1 below
- the hybrid drive device includes a first shaft and a speed change mechanism that are drivingly connected to an internal combustion engine (the internal combustion engine 2 in the Patent Document 1; the same applies hereinafter).
- the second shaft (transmission input shaft 7) that is drive-coupled to the second shaft is selectively drive-coupled via a clutch (separation clutch 4), and the rotating electrical machine (electric motor 5) is connected to the second shaft.
- Drive connected so as to rotate integrally is well known as a configuration capable of realizing a so-called one-motor parallel type hybrid drive device.
- the vehicle can be started with the torque of the rotating electrical machine in the released state of the clutch, and after the vehicle speed has increased to some extent, the vehicle can be driven with the torque of the internal combustion engine and the rotating electrical machine with the clutch engaged. .
- the plurality of friction plates when the clutch performs switching of driving force transmission and disconnection, the plurality of friction plates generally generate heat due to slipping between the plurality of friction plates of the clutch.
- a configuration is adopted in which the vicinity of the clutch is filled with oil sealed for the purpose of lubrication or cooling in the hybrid drive device, and a plurality of clutch friction plates are cooled with a large amount of oil. It is possible.
- it is preferable from the viewpoint of simplification of the apparatus configuration to effectively use the oil for cooling the plurality of friction plates and also to lubricate the bearings and the like normally provided in the hybrid drive apparatus.
- a clutch housing member in order to effectively cool the clutch, it is preferable to provide a clutch housing member in order to realize a configuration in which the vicinity of the clutch is filled with oil. At this time, in order to appropriately and smoothly support the clutch housing member with respect to other members such as a case, it is preferable to perform lubrication of a support mechanism such as a bearing that rotatably supports the member.
- the rotating electrical machine when the rotating electrical machine outputs torque, the rotating electrical machine generates heat due to the occurrence of so-called copper loss or iron loss.
- foreign matter such as fine metal pieces may be mixed in the oil sealed in the device. If such foreign matter adheres to the rotating electrical machine, the rotating electrical machine for which precise control is required. May have an impact. Therefore, regarding the cooling of the rotating electrical machine, it is possible to adopt a cooling structure (air cooling structure) that uses traveling wind or the like during traveling of the vehicle, instead of a cooling structure (oil cooling structure) that uses oil enclosed in the apparatus. preferable.
- a cooling structure air cooling structure
- oil cooling structure oil enclosed in the apparatus.
- Patent Document 1 did not show any solution for these problems.
- the clutch and the rotating electric machine can be appropriately cooled, and the clutch housing member provided for effective cooling of the clutch can be supported appropriately and smoothly. Realization of a hybrid drive device capable of reducing the axial dimension is desired.
- a first shaft that is drivingly connected to an internal combustion engine, a rotating electrical machine, a second shaft that is arranged coaxially with the first shaft and is drivingly connected to the rotating electrical machine and a transmission mechanism, and the first A clutch provided so as to be able to switch between transmission and interruption of driving force between the shaft and the second shaft; and a case housing the first shaft, the second shaft, the rotating electrical machine, and the clutch.
- the hybrid drive device has a characteristic configuration that encloses both sides of the clutch in the axial direction and the outside in the radial direction, accommodates the clutch, and is connected to the second shaft to form an oil chamber filled with oil.
- a first support mechanism that supports the clutch housing in a radial direction and an axial direction while being rotatable with respect to the case, and an oil-tight state between the case and the clutch housing.
- a seal mechanism on one side in the axial direction of the clutch housing, the rotor of the rotating electrical machine is fixed to the outer peripheral portion of the clutch housing, and the case extends in the radial direction on one side in the axial direction of the clutch housing
- a cylindrical first axial projecting portion projecting from the one side support wall portion to the other axial side, and the clutch housing is disposed on one axial side of the clutch.
- the first shaft extending in the radial direction and a cylindrical second axial projecting portion projecting from the first radial extending portion toward the one axial side, and the second shaft
- the directional protrusion is formed in a stepped shape having an outer diameter that is a large diameter portion on the other side in the axial direction and a small diameter portion on the one side in the axial direction, and the first support mechanism is formed of a small diameter portion of the second axial protrusion portion.
- the first seal mechanism is in contact with the outer peripheral surface of the large-diameter portion of the second axially projecting portion and the inner peripheral surface of the first axially projecting portion; and It is in the point arrange
- the clutch accommodated in a clutch housing can be cooled effectively with a large amount of oil.
- the first support mechanism disposed in contact with the outer peripheral surface of the small-diameter portion of the second axial protruding portion and the inner peripheral surface of the first axial protruding portion causes the clutch housing to be attached to the case on one side in the axial direction. It can be supported in the radial and axial directions in a rotatable state.
- the oil for cooling the clutch is effectively used, and the first support mechanism Lubrication can be performed.
- the first seal mechanism disposed in contact with the outer peripheral surface of the large-diameter portion of the second axial protruding portion and the inner peripheral surface of the first axial protruding portion on the other side in the axial direction than the first support mechanism. An oil-tight state can be established between the case and the clutch housing. As a result, it is possible to suppress the oil lubricated to the first support mechanism from reaching the rotating electrical machine fixed to the outer peripheral portion of the clutch housing.
- the cooling structure of the rotating electrical machine uses traveling wind during traveling of the vehicle.
- the air cooling structure can be made. Therefore, the rotating electrical machine can be appropriately cooled in a state in which the influence of the foreign matter or the like is suppressed.
- the rotor of the rotating electrical machine is fixed to the outer peripheral portion of the clutch housing, for example, the axial dimension of the entire apparatus is shortened compared to the case where the rotating electrical machine and the clutch housing are arranged side by side in the axial direction. be able to. Therefore, according to the above-described characteristic configuration, the clutch and the rotating electric machine can be appropriately cooled, and the clutch housing provided for effective cooling of the clutch can be appropriately and smoothly supported. Further, it is possible to provide a hybrid drive device that can reduce the axial dimension of the entire device.
- the one side radially extending portion is formed in a shape in which the radially inner end is positioned on the other axial side of the radially outer end, and the first support mechanism and the first seal mechanism It is preferable that one or both of them be arranged so as to overlap the one side radial direction extending portion in the axial direction.
- overlap in a certain direction means that at least part of the two members has the same position with respect to the arrangement in the direction.
- the one side radial extending portion is formed in a flat plate shape extending in the radial direction, and the second axial projecting portion is pivoted from the one side radial extending portion formed in the plate shape.
- the axial dimension of the entire apparatus can be shortened by at least the amount of the first seal mechanism disposed in the axial direction overlapping the one side radial extending portion.
- the axial dimension of the entire apparatus can be further shortened.
- a second support mechanism that supports the clutch housing in a radial direction and an axial direction while being rotatable with respect to the case; and a second seal mechanism that is in an oil-tight state between the case and the clutch housing; Is provided on the other side in the axial direction of the clutch housing, and the case extends from the other side supporting wall to the one side in the axial direction.
- a cylindrical third axial projecting portion that projects, and the clutch housing is disposed on the other axial side of the clutch and extends in the radial direction, and the other radial diameter
- a cylindrical fourth axial projecting portion projecting from the direction extending portion to the other axial side, and the fourth axial projecting portion has an outer diameter on the one side in the axial direction and a large diameter portion in the axial direction.
- a step where the other side is a small diameter portion The second support mechanism is disposed in contact with the outer peripheral surface of the small-diameter portion of the fourth axial protruding portion and the inner peripheral surface of the third axial protruding portion, and the second seal mechanism is And a configuration in which the outer peripheral surface of the large-diameter portion of the fourth axially protruding portion and the inner peripheral surface of the third axially protruding portion are in contact with the second support mechanism and arranged in the axial direction. Is preferred.
- the second support mechanism disposed in contact with the outer peripheral surface of the small-diameter portion of the fourth axial projecting portion and the inner peripheral surface of the third axial projecting portion, with respect to the case on the other axial side.
- the clutch housing can be supported in the radial direction and the axial direction in a rotatable state.
- the second seal mechanism disposed in contact with the outer peripheral surface of the large-diameter portion of the fourth axial protruding portion and the inner peripheral surface of the third axial protruding portion is arranged on one axial side of the second support mechanism. An oil-tight state can be established between the case and the clutch housing. Therefore, oil supplied to the second support mechanism for lubricating the second support mechanism can be prevented from reaching the rotating electrical machine fixed to the outer peripheral portion of the clutch housing.
- the other side radially extending portion is formed in a shape in which a radially inner end is positioned on one axial side with respect to a radially outer end, and one of the second support mechanism and the second seal mechanism. Alternatively, it is preferable that both are arranged so as to overlap with the other-side radial extending portion in the axial direction.
- the other-side radial extending portion is formed in a flat plate shape extending in the radial direction, and the fourth axial projecting portion is pivoted from the other-side radial extending portion formed in the plate shape.
- the axial dimension of the entire apparatus can be shortened by at least the amount of the second seal mechanism overlapped with the other side radial extending portion in the axial direction.
- the second seal mechanism and the second support mechanism are disposed so as to overlap the other radial extension portion in the axial direction, the axial dimension of the entire apparatus can be further shortened.
- a second support mechanism that supports the clutch housing in a radial direction and an axial direction while being rotatable with respect to the case; and a second seal mechanism that is in an oil-tight state between the case and the clutch housing; Is provided on the other side in the axial direction of the clutch housing, and the case extends from the other side supporting wall to the one side in the axial direction.
- a cylindrical third axial projecting portion that projects, and the clutch housing is disposed on the other axial side of the clutch and extends in the radial direction, and the other radial diameter
- a cylindrical fourth axial projecting portion projecting from the direction extending portion to the other axial side, and the other radial extending portion is a first provided with the fourth axial projecting portion.
- Disk-shaped part and the first circle A second disk-shaped part that is offset to the other side in the axial direction with respect to the shaped part and arranged radially outward, and the first disk-shaped part and the second disk-shaped part are connected to each other A stepped cylindrical portion, and the second support mechanism is disposed in contact with an outer peripheral surface of the fourth axial projection and an inner peripheral surface of the third axial projection, It is preferable that the two-seal mechanism is arranged in contact with the outer peripheral surface of the third axial projecting portion and the inner peripheral surface of the stepped cylindrical portion so as to overlap the second support mechanism in the axial direction. It is.
- the second housing mechanism disposed in contact with the outer peripheral surface of the fourth axial projecting portion and the inner peripheral surface of the third axial projecting portion allows the clutch housing with respect to the case on the other side in the axial direction. Can be supported in a radial direction and an axial direction in a rotatable state.
- the second seal mechanism disposed in contact with the outer peripheral surface of the third axially projecting portion and the inner peripheral surface of the stepped cylindrical portion provides a space between the case and the clutch housing on the radially outer side than the second support mechanism. Can be in an oil-tight state.
- both the second seal mechanism and the second support mechanism are disposed so as to overlap in the axial direction with the stepped cylindrical portion constituting a part of the other-side radial extending portion.
- the axial dimension of the entire apparatus can be shortened.
- a plurality of friction plates included in the clutch be arranged radially outside the first seal mechanism and the second seal mechanism.
- a plurality of friction plates that the clutch has are generally arranged side by side in the axial direction. And is slidable in the axial direction. According to this configuration, a plurality of friction plates can be appropriately arranged in the space using a space that is wide in the axial direction on the radially outer side of the first seal mechanism and the second seal mechanism.
- the clutch has a piston for pressing the plurality of friction plates, and the second seal mechanism is arranged to overlap with the piston in the axial direction.
- the second seal mechanism can be disposed so as to overlap with the clutch housing in the axial direction by overlapping the piston accommodated in the clutch housing in the axial direction. . Therefore, the axial dimension of the entire apparatus can be further shortened.
- a connecting member extending in a radial direction so as to connect the first shaft and the clutch hub of the clutch; and an axially one side surface and an axially other side surface of the connecting member.
- a third support mechanism and a fourth support mechanism that support the connection member and the clutch housing so as to be relatively rotatable, and the connection member extends axially outward from the first shaft.
- a hub side connecting portion that is a part of the clutch hub and extends radially inward, and the hub side connecting portion is formed in a notch groove formed in a radially outer end portion of the shaft side connecting portion.
- the shaft side connecting portion On the other hand, it is connected to the shaft side connecting portion in a state of being in contact with one side in the axial direction, and the one side radial extending portion is continuously retracted from the surface on the other side in the axial direction to the one side in the axial direction.
- a cylindrical axial retraction surface formed on the The three support mechanisms are positioned in the radial direction by the axially retracting surface, the fourth support mechanism is disposed radially outside the third support mechanism, and the radial outer end of the shaft side coupling portion It is preferable to adopt a configuration that is positioned in the radial direction.
- the shaft side connecting portion and the hub side connecting portion are connected in a state where the hub side connecting portion is supported in the axial direction from the other side in the axial direction by the shaft side connecting portion.
- a notch groove is formed relatively easily and accurately by providing a notch groove in the shaft side connecting portion extending radially outward from the first shaft, which is a shaft-shaped member that is generally easy to process. be able to.
- the third support mechanism can be positioned in the radial direction by the axially retracting surface formed in the one side radial extending portion, and the diameter of the fourth support mechanism can be determined by the radial outer end of the shaft side coupling portion.
- Directional positioning can be performed. Further, for example, the axial dimension of the entire apparatus can be shortened as compared with a case where the third support mechanism and the fourth support mechanism are arranged in the axial direction on both sides in the axial direction of the shaft side coupling portion.
- a damper device disposed on one axial side of the one side support wall portion and interposed between the first shaft and the internal combustion engine, wherein the damper device is pivoted from a stator of the rotating electrical machine. It is preferable that the coil end portion protruding in the direction overlaps the axial direction in the axial direction.
- the output rotation of the internal combustion engine can be transmitted to the first shaft while the torsional vibration of the output rotation of the internal combustion engine is attenuated by the damper device. Further, by arranging such a damper device in the axial direction so as to overlap with the coil end portion of the rotating electrical machine, the axial dimension of the entire device is further shortened by the amount that they are arranged in the axial direction. be able to.
- the hybrid drive device 1 is a drive device for a hybrid vehicle that uses one or both of the internal combustion engine E and the rotating electrical machine MG as a drive force source of the vehicle.
- the hybrid drive device 1 is configured as a so-called 1-motor parallel type hybrid drive device.
- the hybrid drive device 1 includes an input shaft I that is drivingly connected to the internal combustion engine E, a rotating electrical machine MG, and an intermediate that is drivingly connected to the rotating electrical machine MG and the speed change mechanism TM.
- a clutch CL provided so as to be able to switch between transmission and disconnection of the driving force between the shaft M and the input shaft I and the intermediate shaft M; a case 2 housing the input shaft I, the intermediate shaft M, the clutch CL, It has.
- the hybrid drive device 1 according to the present embodiment includes a clutch housing CH (see FIG. 2) that houses the clutch CL in a state where the interior is filled with oil, and the case with respect to the case 2. It has a feature in the rotation support structure and the seal structure of the clutch housing CH.
- the hybrid drive device 1 surrounds both sides in the axial direction and the radially outer side of the clutch CL to house the clutch CL, and is drivingly connected to the intermediate shaft M, and inside thereof.
- a clutch housing CH that forms a circulating oil chamber 38 filled with oil is provided.
- a first bearing 51 that supports the clutch housing CH in a radial direction and an axial direction while being rotatable with respect to the case 2, and a first seal member 61 that makes the space between the case 2 and the clutch housing CH oil-tight.
- the rotor Ro of the rotating electrical machine MG is fixed to the outer peripheral portion of the clutch housing CH.
- the case 2 includes a first support wall 4 that extends in the radial direction on one axial side of the clutch housing CH, and a cylindrical axial protrusion 5 that protrudes from the first support wall 4 to the other axial side.
- the clutch housing CH is disposed on one side in the axial direction of the clutch CL and extends in the radial direction on one side radially extending portion 41, and a cylinder projecting from the one side radial extending portion 41 toward the one axial side.
- the axial protrusion 42 is formed in a stepped shape having a large diameter portion on the other side in the axial direction and a small diameter portion on the one side in the axial direction.
- the first bearing 51 is disposed in contact with the outer peripheral surface of the small diameter portion of the axial protruding portion 42 and the inner peripheral surface of the axial protruding portion 5, and the first seal member 61 is The first protrusion 51 and the inner peripheral surface of the axial protrusion 5 are arranged in parallel with the first bearing 51 in contact with the outer peripheral surface of the large-diameter portion of the direction protrusion 42.
- the hybrid drive device 1 includes an input shaft I that is drivingly connected to an internal combustion engine E as a first driving force source of a vehicle, and a rotating electrical machine MG as a second driving force source of the vehicle.
- the hybrid drive device 1 includes a clutch CL provided so as to be able to switch between transmission and disconnection of driving force between the input shaft I and the intermediate shaft M, a counter gear mechanism C, an output differential gear device DF, It has.
- a case 2 as a drive device case.
- the input shaft I corresponds to the “first axis” in the present invention
- the intermediate shaft M corresponds to the “second axis” in the present invention.
- Drive coupling refers to a state where two rotating elements are coupled so as to be able to transmit a driving force, and the two rotating elements are coupled so as to rotate integrally, or the two rotating elements. Is used as a concept including a state in which a driving force can be transmitted through one or more transmission members. Examples of such a transmission member include various members that transmit rotation at the same speed or a variable speed, and include, for example, a shaft, a gear mechanism, a belt, a chain, and the like. Further, “driving force” is used synonymously with torque.
- 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 internal combustion engine E is a device that is driven by combustion of fuel inside the engine to extract power, and for example, various known engines such as a gasoline engine and a diesel engine can be used.
- an internal combustion engine output shaft Eo such as a crankshaft of the internal combustion engine E is drivingly connected to the input shaft I via a damper D.
- the input shaft I is drivingly connected to the rotating electrical machine MG and the intermediate shaft M via the clutch CL, and the input shaft I is selectively connected to the rotating electrical machine MG and the intermediate shaft M by the clutch CL.
- the internal combustion engine E and the rotary electric machine MG are drivingly connected via the input shaft I, and in the released state of the clutch CL, the internal combustion engine E and the rotary electric machine MG are separated.
- the rotating electrical machine MG includes a stator St and a rotor Ro, and functions as a motor (electric motor) that generates power by receiving power supply, and a generator (power generation) that generates power by receiving power supply. 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 battery with electric power generated by the torque output from the internal combustion engine E or the inertial force of the vehicle.
- the rotor Ro of the rotating electrical machine MG is drivingly connected so as to rotate integrally with the intermediate shaft M.
- the intermediate shaft M is an input shaft (transmission input shaft) of the speed change mechanism TM.
- the speed change mechanism TM is a device that changes the rotational speed of the intermediate shaft M at a predetermined speed ratio and transmits it to the speed change output gear G.
- the transmission mechanism TM includes a single pinion type and Ravigneaux type planetary gear mechanism and a plurality of engagement devices such as a clutch, a brake, and a one-way clutch.
- An automatic transmission mechanism provided with a switchable gear is used.
- As the speed change mechanism TM an automatic speed change mechanism having other specific configurations, an automatic continuously variable speed change mechanism capable of changing the speed ratio steplessly, and a plurality of speed stages having different speed ratios can be switched.
- a manual stepped transmission mechanism or the like may be used.
- the speed change mechanism TM changes the rotational speed of the intermediate shaft M at a predetermined speed change ratio at each time point, converts torque, and transmits the torque to the speed change output gear G.
- the counter gear mechanism C transmits the rotation and torque of the transmission output gear G to the wheel W side.
- the counter gear mechanism C has a counter shaft Cs, a first gear C1, and a second gear C2.
- the first gear C1 meshes with the transmission output gear G.
- the second gear C2 meshes with the differential input gear Di included in the output differential gear device DF.
- the differential gear device for output DF distributes the rotation and torque of the differential input gear Di to the plurality of wheels W and transmits them.
- the output differential gear device DF is a differential gear mechanism using a plurality of bevel gears meshing with each other, and is transmitted to the differential input gear Di via the second gear C2 of the counter gear mechanism C. Is distributed to the two left and right wheels W via the output shaft O, respectively.
- the hybrid drive device 1 transmits the torque of one or both of the internal combustion engine E and the rotating electrical machine MG to the wheels W to cause the vehicle to travel.
- the input shaft I and the intermediate shaft M are coaxially arranged, and the counter shaft Cs and the output shaft O are the input shaft I and the intermediate shaft M, respectively. They are arranged parallel to each other on different axes.
- Such a configuration is suitable as a configuration of the hybrid drive device 1 mounted on, for example, an FF (Front Engine Front Drive) vehicle.
- the case 2 includes a case peripheral wall 3 that covers the outer periphery of each housing component such as a rotating electrical machine MG and a transmission mechanism TM housed therein, and one axial direction side of the case peripheral wall 3 (internal combustion engine).
- a first support wall 4 that closes the opening on the E side and on the right side in FIG. 2 (the same applies hereinafter), and the other axial side of the first support wall 4 (the side opposite to the internal combustion engine E and in FIG. 2).
- the second support wall 7 is disposed between the rotary electric machine MG and the speed change mechanism TM in the axial direction.
- the case 2 includes an end support wall that closes the end of the case peripheral wall 3 on the other side in the axial direction.
- the first support wall 4 has a shape extending at least in the radial direction, and extends in the radial direction and the circumferential direction in the present embodiment.
- An axial through hole is formed in the first support wall 4, and an input shaft I inserted through the through hole is inserted into the case 2 through the first support wall 4.
- the first support wall 4 is connected to a cylindrical (boss-shaped) axial projecting portion 5 projecting to the other side in the axial direction.
- the axial protrusion 5 is integrally connected to the first support wall 4.
- the first support wall 4 is located on the other axial side so that the radially inner portion is positioned on the other axial side with respect to the radially outer portion in the portion where the input shaft I is penetrated.
- the first support wall 4 is disposed on one side in the axial direction with respect to the clutch CL, and more specifically, is disposed adjacent to the clutch housing CH on one side in the axial direction with a predetermined interval. . Further, an oil passage forming member 71 having a discharge oil passage 72 formed therein is attached to the first support wall 4 along the radial direction.
- the first support wall 4 corresponds to the “one side support wall portion” in the present invention
- the axial protrusion 5 corresponds to the “first axial protrusion” in the present invention.
- the second support wall 7 has a shape extending at least in the radial direction, and in the present embodiment, extends in the radial direction and the circumferential direction.
- a through hole in the axial direction is formed in the second support wall 7, and an intermediate shaft M inserted through the through hole passes through the second support wall 7.
- the second support wall 7 is connected to a cylindrical (boss-shaped) axial projecting portion 8 projecting to one axial side.
- the axial protrusion 8 is integrally connected to the second support wall 7.
- the second support wall 7 is disposed on the other side in the axial direction with respect to the clutch CL, and more specifically, is disposed adjacent to the clutch housing CH on the other side in the axial direction with a predetermined interval. .
- An oil pump 18 is accommodated in a pump chamber formed inside the second support wall 7.
- the oil pump 18 is an inscribed gear pump having an inner rotor and an outer rotor.
- the inner rotor of the oil pump 18 is drivingly connected (here, splined) so as to rotate integrally with the clutch housing CH at its radial center.
- the oil pump 18 discharges oil and generates hydraulic pressure for supplying oil to the clutch CL, the speed change mechanism TM, and the like.
- oil passages are respectively formed inside the second support wall 7 and the intermediate shaft M, and the oil discharged by the oil pump 18 flows through a hydraulic control device (not shown) and these oil passages.
- the second support wall 7 corresponds to the “other side support wall” in the present invention
- the axial protrusion 8 corresponds to the “third axial protrusion” in the present invention.
- the input shaft I is a shaft for inputting the torque of the internal combustion engine E to the hybrid drive device 1, and is drivingly connected to the internal combustion engine E at one end portion in the axial direction.
- the input shaft I is disposed in a state of penetrating the first support wall 4, and as shown in FIG. 2, the internal combustion engine E is interposed via a damper D on one side in the axial direction of the first support wall 4.
- the internal combustion engine output shaft Eo is driven and connected to rotate integrally.
- the damper D is a device that transmits the rotation of the internal combustion engine output shaft Eo to the input shaft I while attenuating torsional vibration of the internal combustion engine output shaft Eo, and various known devices can be used.
- the damper D has a plurality of coil springs arranged along the circumferential direction, and is fixed and integrated with a drive plate DP fixed to the internal combustion engine output shaft Eo.
- the input shaft I is splined.
- the damper D as a whole has a smaller diameter than the drive plate DP, and is disposed on the other axial side of the drive plate DP.
- a third seal is formed across the input shaft I and the first support wall 4 to prevent leakage of oil to one side in the axial direction (the damper D and the internal combustion engine E side) with a liquid-tight state therebetween.
- a member 63 is provided.
- a shaft end hole portion 12 extending in the axial direction is formed in the inner diameter portion of the other end portion in the axial direction of the input shaft I.
- An end of one side of the intermediate shaft M in the axial direction enters the shaft end hole 12 in the axial direction.
- the input shaft I has a flange portion 11 extending radially from the input shaft I at the other end portion in the axial direction.
- the flange portion 11 is formed integrally with the input shaft I.
- the flange portion 11 is connected to the clutch hub 21 of the clutch CL accommodated in the clutch housing CH in the clutch housing CH.
- a second bearing 52 is disposed on one side in the axial direction of the flange portion 11, and a third bearing is provided on the other side in the radial direction of the flange portion 11 and on the other side in the axial direction of the clutch hub 21 of the clutch CL.
- a bearing 53 is provided. In such a positional relationship, the third bearing 53 is arranged on the outer side in the radial direction than the second bearing 52.
- the second bearing 52 corresponds to the “third support mechanism” in the present invention
- the third bearing 53 corresponds to the “fourth support mechanism” in the present invention.
- the intermediate shaft M is a shaft for inputting one or both of the torque of the rotating electrical machine MG and the torque of the internal combustion engine E via the clutch CL to the speed change mechanism TM, and is splined to the clutch housing CH. As shown in FIG. 2, the intermediate shaft M is disposed so as to penetrate the second support wall 7. As described above, an axial through hole is formed at the radial center of the second support wall 7, and the intermediate shaft M passes through the second support wall 7 through the through hole.
- the intermediate shaft M is supported in the radial direction so as to be rotatable with respect to the second support wall 7. Further, the end portion on one side in the axial direction of the intermediate shaft M is inserted into the shaft end hole portion 12 of the input shaft I in the axial direction.
- the intermediate shaft M has a plurality of oil passages including a supply oil passage 15 and a discharge oil passage 16 on the inner diameter portion thereof.
- the supply oil passage 15 extends in the axial direction on one side in the axial direction of the intermediate shaft M and extends in the radial direction at a predetermined position in the axial direction so as to communicate with the hydraulic oil chamber 37 of the clutch CL. Is open.
- the drain oil passage 16 extends in the axial direction at a position different from the supply oil passage 15 in the axial direction on one side of the intermediate shaft M, and opens to the end surface on the one axial side.
- the clutch CL is provided so as to be able to switch between transmission and disconnection of the driving force between the input shaft I and the intermediate shaft M, and selectively engages and connects the internal combustion engine E and the rotating electrical machine MG. It is.
- the clutch CL is configured as a wet multi-plate clutch mechanism. As shown in FIG. 3, the clutch CL includes a clutch hub 21, a clutch drum 26, a plurality of friction plates 31, and a piston 36.
- the clutch hub 21 is coupled to the flange portion 11 of the input shaft I so as to rotate integrally with the input shaft I.
- the clutch drum 26 is connected so as to rotate integrally with the intermediate shaft M via the clutch housing CH.
- the clutch drum 26 has a cylindrical shape and is formed integrally with the clutch housing CH.
- the friction plate 31 includes a hub-side friction plate and a drum-side friction plate that form a pair.
- the hub-side friction plate is supported from the inside in the radial direction by the clutch hub 21, and relative rotation with respect to the clutch hub 21 is restricted and slidable in the axial direction.
- the drum-side friction plate is supported by the clutch drum 26 from the outside in the radial direction, and relative rotation with respect to the clutch drum 26 is restricted and slidable in the axial direction.
- the hub side friction plate and the drum side friction plate are alternately arranged in the axial direction.
- a backing plate 32 that functions as a pressing member when the friction plates 31 are engaged with each other is held on one axial side of all the friction plates 31.
- the backing plate 32 is held in a state in which movement in the axial direction is restricted by a snap ring.
- the piston 36 is disposed on the other axial side with respect to the plurality of friction plates 31 in a state of being biased to the other axial side by a return spring.
- a fluid-tight hydraulic oil chamber 37 is formed between the clutch housing CH integrated with the clutch drum 26 and the piston 36.
- pressure oil discharged by the oil pump 18 and adjusted to a predetermined hydraulic pressure by a hydraulic control device is formed in the supply oil passage 15 formed in the intermediate shaft M and the clutch housing CH. Supplied through the connecting oil passage 48.
- the piston 36 moves in the direction of expanding the volume of the hydraulic oil chamber 37 (in this example, one side in the axial direction), and the backing plate 32.
- the plurality of friction plates 31 are engaged with each other in cooperation with the.
- a circulating oil chamber 38 is formed on the opposite side of the piston 36 from the hydraulic oil chamber 37.
- a circulating oil passage 47 formed in the clutch housing CH is supplied to the circulating oil chamber 38 by pressure oil discharged by the oil pump 18 and adjusted to a predetermined oil pressure by a hydraulic controller (not shown) (see FIG. 2). Is supplied through.
- the clutch hub 21 is coupled to the flange portion 11 of the input shaft I so as to rotate integrally with the input shaft I.
- the clutch hub 21 is formed in a cylindrical shape and holds a plurality of hub side plates, and extends radially inward from one axial end of the cylindrical portion. And a plurality of hub-side plates and an annular plate-like portion 22 that supports the cylindrical portion in the radial direction.
- the annular plate-shaped part 22 which comprises a part of clutch hub 21 is connected with the flange part 11 of the input shaft I, and the input shaft I and the clutch hub 21 are connected integrally.
- the flange portion 11 of the input shaft I corresponds to the “shaft side connecting portion” in the present invention
- the annular plate-like portion 22 of the clutch hub 21 corresponds to the “hub side connecting portion” in the present invention. Equivalent to. Further, the flange portion 11 and the annular plate-like portion 22 constitute a “connecting member” in the present invention.
- the flange portion 11 has a notch groove 11a at the radially outer end thereof.
- the notch groove 11a is formed at one end portion in the axial direction of the flange portion 11 so that the surface defining the bottom portion in the radial direction is continuous with the surface on one axial direction side of the flange portion 11.
- the axial width of the notch groove 11 a is substantially equal to the axial width of the radially inner end of the annular plate-like portion 22 of the clutch hub 21.
- the annular plate-shaped part 22 is connected with the flange part 11 by welding etc. in the state contact
- the input shaft I and the flange portion 11 extending radially outward from the input shaft I are formed by a cutting process such as a lathe process capable of performing a highly accurate process. Therefore, it is possible to form the notch groove 11a relatively easily and with high accuracy in accordance with the formation of the input shaft I and the flange portion 11.
- the clutch hub 21 having a lower required accuracy than the input shaft I and the flange portion 11 is formed by press working that can be manufactured at low cost.
- a second bearing 52 and a third bearing 53 are disposed in the vicinity of a connection portion between the flange portion 11 and the annular plate-like portion 22. More specifically, a second bearing 52 is disposed in contact with the surface on one axial side of the flange portion 11, and the second bearing 52 further includes a clutch housing CH (one side to be described later) on the one axial side. It is in contact with the radially extending part 41). Further, a third bearing 53 is disposed in contact with the surface on the other axial side of the annular plate-like portion 22, and this third bearing 53 is further connected to a clutch housing CH (the other side diameter described later) on the other axial side. It is in contact with the direction extending part 45).
- the second bearing 52 and the third bearing 53 thrust washers capable of receiving an axial load are used. Accordingly, the flange portion 11 and the annular plate-like portion 22 and the clutch housing CH that are integrally connected are supported via the second bearing 52 and the third bearing 53 so as to be relatively rotatable.
- a plurality of radial grooves extending in the radial direction and a plurality of axial grooves extending in the axial direction are formed on the outer surfaces of the second bearing 52 and the third bearing 53.
- These radial grooves and axial grooves pass through the second bearing 52 and the third bearing 53 when the two members are abutted in the axial direction via the second bearing 52 and the third bearing 53. It becomes a communication path for oil to circulate.
- the second bearing 52 is positioned in the radial direction by an axially retracting surface 41a formed continuously from the surface on the other axial side of the one side radial extending portion 41 described later. Yes. That is, the second bearing 52 is fixed in a state in which the outer peripheral surface thereof is fitted to the axially retracting surface 41a, thereby positioning in the radial direction.
- the third bearing 53 is positioned in the radial direction by the radially outer end of the flange portion 11. That is, the third bearing 53 is fixed in a state where the inner peripheral surface thereof is fitted to the outer peripheral surface of the portion on the other side in the axial direction from the notch groove 11a of the flange portion 11, thereby positioning in the radial direction. Has been made.
- the hybrid drive device 1 further includes a clutch housing CH that houses the clutch CL.
- the clutch housing CH is disposed across the input shaft I and the intermediate shaft M in a state of rotating relative to the input shaft I and rotating integrally with the intermediate shaft M.
- the clutch housing CH encloses both sides of the clutch CL in the axial direction and radially outside of the input shaft I and the intermediate shaft M arranged coaxially and accommodates the clutch CL. Therefore, the clutch housing CH is disposed on one side in the axial direction of the clutch CL and extends in the radial direction on one side, and the other side diameter extends in the radial direction on the other side in the axial direction of the clutch CL.
- a cylindrical portion 49 that connects the one side radial extension portion 41 and the other side radial extension portion 45 in the axial direction at their radially outer ends. Has been.
- the one-side radial extending portion 41 has a shape extending at least in the radial direction, and extends in the radial direction and the circumferential direction in the present embodiment.
- An axial through hole is formed at the radial center of the one side radial extending portion 41, and the input shaft I inserted through the through hole penetrates the one side radial extending portion 41 to engage the clutch. It is inserted in the housing CH.
- the one side radial extending portion 41 is connected to a cylindrical (boss-like) axial projecting portion 42 projecting to one axial side.
- the axial protrusion 42 is formed so as to surround the input shaft I.
- a fifth bearing 55 is disposed between the axial protrusion 42 and the input shaft I.
- the axial projecting portion 42 is integrally connected to the one-side radial extending portion 41 at the radially inner end of the one-side radial extending portion 41.
- the one-side radially extending portion 41 is a dish that is convex toward the other side in the axial direction so that the radially inner portion is located on the other side in the axial direction relative to the radially outer portion as a whole.
- the member has a curved shape.
- the one side radially extending portion 41 is adjacent to the first support wall 4 at a predetermined interval on the other side in the axial direction, and the axial protrusion 42 is connected to the axial protrusion 5 of the first support wall 4.
- the first bearing 51 and the space between them are in a liquid-tight state across the axial protrusion 42 and the axial protrusion 5 of the first support wall 4 to the other axial side (rotating electrical machine MG side).
- a first seal member 61 for suppressing oil leakage is disposed.
- the axial protrusion 42 corresponds to the “second axial protrusion” in the present invention.
- the first bearing 51 corresponds to the “first support mechanism” in the present invention
- the first seal member 61 corresponds to the “first seal mechanism” in the present invention.
- the one-side radial extending portion 41 has a cylindrical axial retraction surface 41a formed so as to continuously retreat from the surface on the other side in the axial direction to the one side in the axial direction.
- Such an axially retracting surface 41 a is formed at the radially inner end of the one side radially extending portion 41.
- the second bearing 52 is positioned in the radial direction by the axially retracting surface 41a.
- the cylindrical portion 49 has a cylindrical shape extending in the axial direction and the circumferential direction and surrounding the radially outer side of the clutch CL.
- the cylindrical portion 49 connects the one-side radial extending portion 41 and the other-side radial extending portion 45 in the axial direction at these radially outer end portions.
- the cylindrical portion 49 extends from the radially outer end of the one-side radially extending portion 41 toward the other side in the axial direction.
- the cylindrical portion 49 is formed integrally with the one side radial direction extending portion 41.
- the other-side radial extending portion 45 has a shape extending at least in the radial direction, and extends in the radial direction and the circumferential direction in the present embodiment.
- the other side radially extending portion 45 has a radially inner portion with respect to the radially outer portion such that the radially inner portion is located on one axial side of the radially outer portion as a whole.
- the plate member has a shape offset to one side in the axial direction.
- the other side radially extending portion 45 is connected to a portion on the other axial side of the cylindrical portion 49 by welding or the like in the vicinity of the radially outer end.
- An axial through hole is formed in the radial center of the other side radially extending portion 45, and the intermediate shaft M inserted through this through hole penetrates the other side radially extending portion 45 to engage the clutch. It is inserted in the housing CH.
- the other side radially extending portion 45 has an inner peripheral surface in contact with the outer peripheral surface of the intermediate shaft M over the entire circumferential direction at the radially inner end.
- the other-side radially extending portion 45 is connected to a cylindrical (boss-shaped) axial projecting portion 46 projecting to the other axial side.
- the axial protruding portion 46 is formed so as to surround the periphery of the intermediate shaft M.
- the axial protrusion 46 is integrally connected to the other-side radial extending portion 45 at the radially inner end of the other-side radial extending portion 45.
- the axial protrusion 46 corresponds to the “fourth axial protrusion” in the present invention.
- the axial projection 46 is splined so as to rotate integrally with the intermediate shaft M.
- the other-side radial extending portion 45 is adjacent to the second support wall 7 at a predetermined interval on one side in the axial direction, and the axial projection 46 is formed on the axial projection 8 of the second support wall 7. On the other hand, they are arranged in a state adjacent to each other at a predetermined interval on the radially inner side. Further, the other-side radial extending portion 45 is disposed adjacent to the clutch hub 21 and the flange portion 11 of the input shaft I at a radially inner portion at a predetermined interval on the other side in the axial direction. .
- the fourth bearing 54 spans between the axial protrusion 46 and the axial protrusion 8 of the second support wall 7, and the space between them is in a liquid-tight state toward one side in the axial direction (rotating electrical machine MG side).
- a second seal member 62 for suppressing oil leakage is disposed.
- the fourth bearing 54 corresponds to the “second support mechanism” in the present invention
- the second seal member 62 corresponds to the “second seal mechanism” in the present invention.
- the clutch drum 26 is integrally formed with the other-side radial extending portion 45. More specifically, in the vicinity of the radially outer end portion of the other-side radial extending portion 45, the cylindrical clutch extends from the other-side radial extending portion 45 toward one side in the axial direction.
- the drum 26 is integrally formed. At this time, the clutch drum 26 is disposed radially inward of the cylindrical portion 49 and adjacent to the cylindrical portion 49 at a predetermined interval in the radial direction. A gap formed between the clutch drum 26 and the cylindrical portion 49 is opened in the axial direction at one end portion in the axial direction inside the clutch housing CH.
- a hydraulic oil chamber 37 is formed between the other-side radial extending portion 45 and the piston 36. Further, the other side radially extending portion 45 is generally inclined in the radial direction while being slightly inclined toward one side in the axial direction with respect to the radial direction so that the supply oil passage 15 and the hydraulic oil chamber 37 communicate with each other.
- a communication oil passage 48 extending in the direction is formed at the connecting portion with the axial protrusion 46.
- the one-side radial extending portion 41 on the one axial side has the radially inner portion as a whole on the other side in the axial direction than the radially outer portion. It has the axial protrusion part 42 which protrudes from the radial direction inner side edge part to the axial direction one side while being located. Further, the other radial extending portion 45 on the other side in the axial direction as a whole has a radially inner portion positioned on one axial side than a radially outer portion, and from the radially inner end portion thereof. It has the axial direction protrusion part 46 which protrudes in the other axial side.
- the clutch housing CH has a cross-sectional shape in a plane including the axial direction and the radial direction as a whole in a substantially ⁇ shape.
- ⁇ -shaped refers to a cross-sectional shape in a plane including the axial direction and the radial direction.
- the space occupying most of the space excluding the hydraulic oil chamber 37 is the circulating oil chamber 38 described above.
- the oil discharged from the oil pump 18 and adjusted to a predetermined oil pressure is circulated through the circulation oil passage 47 formed so as to extend in the axial direction in the axial protrusion 46. It is supplied to the chamber 38.
- the fifth bearing 55 disposed between the axial protruding portion 42 and the input shaft I is a bearing with a sealing function (here, a seal function) configured to ensure a certain degree of liquid tightness. Needle bearing with ring).
- the inner peripheral surface of the other-side radially extending portion 45 is in contact with the outer peripheral surface of the intermediate shaft M over the entire circumferential direction at the radially inner end. Therefore, when oil is supplied to the circulating oil chamber 38 via the circulating oil passage 47, the circulating oil chamber 38 in the clutch housing CH is basically always filled with oil. Thereby, in the hybrid drive device 1 according to the present embodiment, the plurality of friction plates 31 provided in the clutch CL can be effectively cooled with a large amount of oil that is always filled in the circulating oil chamber 38. .
- the circulating oil chamber 38 corresponds to the “oil chamber” in the present invention.
- the oil basically circulates in the circulating oil chamber 38 while maintaining a state always filled with oil.
- This oil flow is indicated by broken-line arrows in FIGS. That is, the oil supplied to the circulating oil chamber 38 from the circulating oil passage 47 first passes between the other side radial extending portion 45 and the flange portion 11 and between the piston 36 and the clutch hub 21 in the radial direction.
- the plurality of friction plates 31 are cooled by flowing toward the outside. Further, the oil flows between the clutch hub 21 and the flange portion 11 and the one side radially extending portion 41 toward the radially inner side and reaches the proximal end portion of the flange portion 11. Thereafter, the oil is discharged from the circulating oil chamber 38.
- the oil may flow in the circumferential direction at the same time, but the main flows in the radial direction and the axial direction are as described above.
- the oil discharge path from the circulating oil chamber 38 is divided into two systems.
- the first discharge path is through a radial communication hole opened on the outer peripheral surface of the input shaft I and a discharge oil path 16 formed in the inner diameter portion of the intermediate shaft M.
- the outer diameter of the end portion on one side in the axial direction of the intermediate shaft M is formed to be slightly smaller than the inner diameter of the shaft end hole portion 12 of the input shaft I.
- a predetermined gap is formed between the end surface on one side in the direction and the surface defining the bottom in the axial direction of the shaft end hole 12 of the input shaft I.
- the second discharge path is intended for oil leaking in the axial direction from the fifth bearing 55, and passes through the discharge oil path 72 inside the oil path forming member 71 attached to the first support wall 4.
- Such a second discharge path includes the third seal member 63 disposed between the input shaft I and the first support wall 4, and the axial protrusion 42 of the clutch housing CH and the first support wall 4. It is demarcated by the 1st seal member 61 arrange
- the rotating electrical machine MG is disposed on the radially outer side of the clutch housing CH.
- the rotating electrical machine MG includes a stator St fixed to the case 2 and a rotor Ro that is rotatably supported on the radially inner side of the stator St.
- the stator St includes a stator core that is configured as a laminated structure in which a plurality of annular plate-shaped electromagnetic steel plates are stacked and is fixed to the first support wall 4, and a coil that is wound around the stator core.
- the part which protrudes in the axial direction both sides of a stator core among coils is the coil end part Ce.
- the rotor Ro of the rotating electrical machine MG includes a rotor core configured as a laminated structure in which a plurality of annular plate-shaped electromagnetic steel plates are stacked, and a permanent magnet embedded in the rotor core.
- the rotating electrical machine MG is disposed so as to overlap the clutch housing CH in the axial direction. That is, the rotating electrical machine MG is disposed so as to overlap the clutch housing CH when viewed from the radial direction (the same applies to the arrangement of the two members).
- the rotor Ro of the rotating electrical machine MG is fixed to the outer peripheral portion of the cylindrical portion 49 constituting the clutch housing CH. That is, the inner peripheral surfaces of the plurality of electromagnetic steel plates constituting the rotor Ro are fixed in contact with the outer peripheral surface of the cylindrical portion 49.
- the clutch housing CH also functions as a rotor support member that supports the rotor Ro, and in this embodiment, the clutch housing CH and the rotor support member are formed in common.
- the rotation sensor 19 is provided adjacent to both the second support wall 7 and the other-side radial extending portion 45 of the case 2 on the other axial side of the clutch housing CH.
- the rotation sensor 19 is a sensor for detecting the rotation phase of the rotor Ro relative to the stator St of the rotating electrical machine MG.
- the rotation sensor 19 is disposed on the radially outer side of the oil pump 18 accommodated in the second support wall 7 so as to overlap the oil pump 18 in the axial direction.
- the sensor stator of the rotation sensor 19 is fixed to the second support wall 7, and the sensor rotor of the rotation sensor 19 is fixed to the inner peripheral surface of the other end portion in the axial direction of the cylindrical portion 49.
- a resolver etc. can be used, for example.
- the damper D is disposed with a predetermined gap on one side of the first support wall 4 in the axial direction.
- the damper D is in a space in which the first support wall 4 formed in a dish-like shape that is convex toward the other side in the axial direction is retreated to the other side in the axial direction when viewed from one side in the axial direction.
- the damper D is further disposed in the radial direction inside the coil end portion Ce on the one axial side (internal combustion engine E side) of the stator St of the rotating electrical machine MG so as to overlap the coil end portion Ce in the axial direction.
- the axial dimension of the entire hybrid drive device 1 is shortened by arranging the coil end portion Ce and the damper D overlapping in the axial direction.
- the damper D corresponds to the “damper device” in the present invention.
- the rotation support structure and the seal structure according to the present embodiment are roughly realized by the first bearing 51, the fourth bearing 54, the first seal member 61, and the second seal member 62. That is, the rotation support structure according to the present embodiment is generally configured to support the clutch housing CH in the axial direction and the radial direction in a state in which the clutch housing CH is rotatable with respect to the case 2 on one side in the axial direction of the clutch housing CH.
- the seal structure according to the present embodiment generally has an oil passage between the case 2 and the clutch housing CH on the rotor Ro side of the rotating electrical machine MG with respect to the first bearing 51 in the direction along the clutch housing CH.
- the first seal member 61 that is in a tight state and the second seal member 62 that is in an oil-tight state between the case 2 and the clutch housing CH on the rotor Ro side of the rotating electrical machine MG with respect to the fourth bearing 54 are realized. ing. Details will be described below.
- the clutch housing CH includes a one-side radial extending portion 41 and an axial projecting portion 42 integrally connected to the one-side radial extending portion 41, and this axial direction.
- the protruding portion 42 is disposed adjacent to the axially protruding portion 5 of the first support wall 4 at a predetermined interval radially inward.
- An axial step 42 a is formed on the outer peripheral surface of the axial protrusion 42.
- the “stepped portion in the axial direction” on the outer peripheral surface is a portion formed at a predetermined position in the axial direction of the axial protruding portion 42 where the outer diameter of the axial protruding portion 42 changes.
- the axial protrusion 42 is formed such that a portion on one axial side has a smaller diameter than the portion on the other axial side than the stepped portion 42a. That is, the axial protruding portion 42 is formed in a stepped shape in which the portion on the other side in the axial direction is a large diameter portion and the portion on the one side in the axial direction is a small diameter portion.
- the outer peripheral surface of the small-diameter portion of the axial projection 42 and the inner peripheral surface of the axial projection 5 of the first support wall 4 are in contact with each other.
- a first bearing 51 is disposed between them.
- a ball bearing capable of receiving both a radial load and an axial load is used as the first bearing 51.
- a relatively large ball bearing is used to support the rotor Ro of the rotating electrical machine MG fixed to the outer peripheral portion of the clutch housing CH with high accuracy.
- the first bearing 51 is also in contact with the other surface of the first support wall 4 in the axial direction.
- the one side radial direction extension part 41 which comprises clutch housing CH is supported by the 1st support wall 4 in the radial direction and the axial direction in the state which can rotate via the 1st bearing 51.
- the one side radially extending portion 41 is supported by the first support wall 4 in the axial direction from one side in the axial direction.
- the oil leaked in the axial direction from the circulating oil chamber 38 in the clutch housing CH through the fifth bearing 55 is between the one-side radial extending portion 41 and the first support wall 4. Supplied through the gap.
- the third seal member 63 blocks the leakage to one side in the axial direction (internal combustion engine E side) passing between the input shaft I and the first support wall 4 and supplies oil to the first bearing 51. Is done. As a result, the first bearing 51 can be lubricated by effectively using the oil after cooling the plurality of friction plates 31.
- a first seal member 61 is arranged side by side with the first bearing 51 in the axial direction.
- the first seal member 61 is in contact with the outer peripheral surface of the large-diameter portion of the axial projecting portion 42 and the inner peripheral surface of the axial projecting portion 5 of the first support wall 4 and is disposed therebetween.
- the first seal member 61 suppresses oil leakage to the rotor Ro side (here, the other side in the axial direction) of the rotating electrical machine MG with a liquid-tight state between the axial direction protruding portion 42 and the axial direction protruding portion 5. To do. Thereby, it can suppress that the oil which lubricated the 1st bearing 51 flows in the direction along the clutch housing CH, and reaches the rotary electric machine MG. Further, the oil that has lubricated the first bearing 51 can be appropriately guided to the discharge oil passage 72 formed in the oil passage formation member 71 and discharged.
- the clutch housing CH includes the other-side radial extending portion 45 and an axial projecting portion 46 integrally connected to the other-side radial extending portion 45, and this axial direction.
- the protruding portion 46 is disposed adjacent to the axial protruding portion 8 of the second support wall 7 at a predetermined interval radially inward.
- a stepped portion 46 a in the axial direction is formed on the outer peripheral surface of the axial protruding portion 46.
- the axial protrusion 46 is formed such that a portion on the other side in the axial direction has a smaller diameter than a portion on the one side in the axial direction with respect to the stepped portion 46a. That is, the axial protrusion 46 is formed in a stepped shape in which a part on one side in the axial direction is a large diameter part and a part on the other side in the axial direction is a small diameter part.
- a fourth bearing 54 is disposed between them.
- a ball bearing capable of receiving both a radial load and an axial load is used as the fourth bearing 54.
- a relatively large ball bearing is used to support the rotor Ro of the rotating electrical machine MG fixed to the outer peripheral portion of the clutch housing CH with high accuracy.
- the fourth bearing 54 is also in contact with the surface on one side in the axial direction of the second support wall 7.
- the other side radial direction extension part 45 which comprises clutch housing CH is supported by the 2nd support wall 7 through the 4th bearing 54 in the radial direction and the axial direction in the rotatable state.
- the other side radially extending portion 45 is supported by the second support wall 7 in the axial direction from the other side in the axial direction.
- the fourth bearing 54 is supplied with oil that leaks in the axial direction from the pump chamber that houses the oil pump 18 through the space between the second support wall 7 and the axial protrusion 46. As a result, the fourth bearing 54 can be lubricated.
- a second seal member 62 is arranged side by side with the fourth bearing 54 in the axial direction.
- the second seal member 62 is disposed in contact with the outer peripheral surface of the large-diameter portion of the axial protrusion 46 and the inner peripheral surface of the axial protrusion 8 of the second support wall 7. .
- the second seal member 62 suppresses oil leakage to the rotor Ro side (here, one side in the axial direction) of the rotating electrical machine MG by making a liquid-tight state between the axial direction protruding portion 46 and the axial direction protruding portion 8. To do. Thereby, it can suppress that the oil which lubricated the 4th bearing 54 flows in the direction along the clutch housing CH, and reaches the rotary electric machine MG. Further, the oil that has lubricated the fourth bearing 54 can be appropriately guided to the discharge oil passage 9 formed in the second support wall 7 and discharged.
- the one-side radial extending portion 41 that constitutes a part of the clutch housing CH is axially moved from one axial direction by the first support wall 4 via the first bearing 51.
- the other side radially extending portion 45 constituting the other part of the clutch housing CH is supported by the second support wall 7 through the fourth bearing 54 in the axial direction from the other side in the axial direction. Yes. Therefore, the clutch housing CH can be supported from both axial sides by the first support wall 4 and the second support wall 7.
- the circulating oil chamber 38 formed in the clutch housing CH is basically always filled with oil so as to effectively cool the friction plate 31 of the clutch CL. It has become.
- first seal member 61 and the second seal member are disposed closer to the rotor Ro side of the rotating electrical machine MG than the first bearing 51 and the fourth bearing 54 in the direction along the clutch housing CH formed in an ⁇ -shape as a whole. 62 are arranged. Therefore, it is possible to suppress the oil that has lubricated the first bearing 51 and the fourth bearing 54 from reaching the rotating electrical machine MG. Therefore, the cooling structure of the rotating electrical machine MG can be an air-cooling structure that uses traveling wind during traveling of the vehicle. Therefore, the rotating electrical machine MG requiring precise control can be appropriately cooled in a state in which the influence of foreign matter or the like is suppressed.
- the first bearing 51 is disposed so as to overlap the one-side radial extending portion 41 in the axial direction. More specifically, the first bearing 51 is disposed so as to overlap with the radially outer portion of the one side radially extending portion 41 in the axial direction. Moreover, the 1st seal member 61 arrange
- the one-side radial extending portion 41 formed in a dish-like shape that is convex toward the other side in the axial direction is viewed from one side in the axial direction.
- Both the first bearing 51 and the first seal member 61 are disposed in a space retracted to the other side in the axial direction.
- the fourth bearing 54 is disposed so as to overlap with the other-side radial extending portion 45 in the axial direction. More specifically, the fourth bearing 54 is disposed so as to overlap with the radially outer portion of the other-side radially extending portion 45 in the axial direction.
- the second seal member 62 disposed adjacent to one side in the axial direction with respect to the fourth bearing 54 is naturally disposed so as to overlap with the other-side radial extending portion 45 in the axial direction.
- the second seal member 62 is disposed so as to overlap with the radial center portion of the other-side radial extending portion 45 in the axial direction.
- the other-side radial extending portion 45 includes a first disc-like portion 45a provided with an axial protrusion 46 and an axially other side of the first disc-like portion 45a.
- a second disc-like portion 45c that is offset and arranged radially outward, and an offset portion between the first disc-like portion 45a and the second disc-like portion 45c are formed and connected to each other.
- the stepped cylindrical portion 45b is formed, and the second seal member 62 is disposed so as to overlap the stepped cylindrical portion 45b in the axial direction.
- Both the fourth bearing 54 and the second seal member 62 are disposed in the formed space. Thereby, on the other side in the axial direction of the clutch housing CH, the axial dimension is shortened while realizing the rotation support structure and the seal structure of the clutch housing CH with a simple configuration.
- the first bearing 51, the fourth bearing 54, the first seal member 61, and the second seal are not projected in the axial direction from the space occupied by the clutch housing CH in the axial direction. All of the members 62 are disposed, and the rotation support structure and the seal structure of the clutch housing CH with respect to the case 2 are realized.
- the rotor Ro of the rotating electrical machine MG is fixed to the outer peripheral portion of the cylindrical portion 49 constituting the clutch housing CH, overlapping the clutch housing CH in the axial direction.
- the clutch housing CH and the clutch CL, the rotary electric machine MG, and the plurality of bearings 51 and 54 and the seal members 61 and 62 accommodated therein are arranged in a compact manner.
- the axial dimension of the entire hybrid drive device 1 can be shortened.
- the oil discharged from the circulating oil chamber 38 is supplied to the first bearing 51 and the first bearing 51 is lubricated. In such a configuration, it is not necessary to provide a dedicated oil passage for lubricating the first bearing 51. Therefore, also from this point, the axial dimension of the entire hybrid drive device 1 can be shortened, and the mountability to the vehicle is improved.
- the first bearing 51, the first seal member 61, the fourth bearing 54, and the second seal member 62 are disposed so as to overlap each other in the radial direction. That is, they are arranged so as to overlap each other when viewed from the axial direction (the same applies to the arrangement of the two members). Further, between the first bearing 51 and the first seal member 61 and the fourth bearing 54 and the second seal member 62 in the axial direction, one or more of these are overlapped in the radial direction, and the second bearing 52 and A third bearing 53 is arranged. Then, the fifth bearing 55 is added to the first bearing 51, the second bearing 52, the third bearing 53, the fourth bearing 54, the fifth bearing 55, the first seal member 61, and the second seal member 62.
- a plurality of friction plates 31 of the clutch CL are arranged on the outer side in the radial direction than each component.
- the plurality of friction plates 31 are disposed so as to overlap with at least the second bearing 52, the third bearing 53, and the second seal member 62 in the axial direction.
- the second seal member 62 is further overlapped with the piston 36 in the axial direction.
- Second Embodiment A second embodiment of the present invention will be described with reference to the drawings.
- 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 arrangement configuration of the rotation support structure and the seal structure with respect to the case 2 of the clutch housing CH on the other axial side of the clutch housing CH is partially different from the first embodiment. Therefore, the following description will be made 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.
- an axial step portion (the step portion 46 a in the first embodiment, see FIG. 3) is not formed on the outer peripheral surface of the axial protrusion 46. Instead, the axial protrusion 46 is formed with substantially the same diameter over the entire axial direction.
- the outer peripheral surface of the axial protrusion 46 and the axial protrusion of the second support wall 7 are in contact with the first disc-like portion 45a of the other radial extension 45 from the other axial side.
- a fourth bearing 54 is disposed between and in contact with the inner peripheral surface of the portion 8. In this example, a ball bearing capable of receiving both a radial load and an axial load is used as the fourth bearing 54.
- the fourth bearing 54 is also in contact with the surface on one side in the axial direction of the second support wall 7.
- the other side radial direction extension part 45 which comprises clutch housing CH is supported by the 2nd support wall 7 through the 4th bearing 54 in the radial direction and the axial direction in the rotatable state.
- the other side radially extending portion 45 is supported by the second support wall 7 in the axial direction from the other side in the axial direction.
- the fourth bearing 54 is supplied with oil that leaks in the axial direction from the pump chamber that houses the oil pump 18 through the space between the second support wall 7 and the axial protrusion 46. As a result, the fourth bearing 54 can be lubricated.
- a second seal member 62 is disposed overlapping the fourth bearing 54 in the axial direction.
- the second seal member 62 is in contact with the outer peripheral surface of the axially protruding portion 8 of the second support wall 7 and the inner peripheral surface of the stepped cylindrical portion 45b of the other-side radial extending portion 45, and between them. It is arranged.
- the fourth bearing 54 and the second seal member 62 that are overlapped in the axial direction are also overlapped in the axial direction with the other-side radial extending portion 45. . More specifically, the fourth bearing 54 and the second seal member 62 are both arranged overlapping the stepped cylindrical portion 45b of the other-side radial extending portion 45 in the axial direction.
- the second seal member 62 suppresses leakage of oil to the rotor Ro side of the rotating electrical machine MG by setting a liquid-tight state between the stepped cylindrical portion 45b and the axial projecting portion 8.
- all of the first bearing 51, the fourth bearing 54, the first seal member 61, and the second seal member 62 do not protrude significantly in the axial direction from the space occupied by the clutch housing CH in the axial direction. Is provided, and a rotation support structure and a seal structure of the clutch housing CH with respect to the case 2 are realized. Also in the present embodiment, the rotor Ro of the rotating electrical machine MG is fixed to the outer peripheral portion of the cylindrical portion 49 constituting the clutch housing CH overlapping with the clutch housing CH in the axial direction.
- the clutch housing CH and the clutch CL, the rotary electric machine MG, and the plurality of bearings 51 and 54 and the seal members 61 and 62 accommodated therein are arranged in a compact manner.
- the axial dimension of the entire hybrid drive device 1 can be shortened.
- the oil discharged from the circulating oil chamber 38 is supplied to the first bearing 51 and the first bearing 51 is lubricated. Therefore, it is not necessary to provide a dedicated oil passage for lubricating the first bearing 51, and the axial dimension of the entire hybrid drive device 1 can be shortened from this point as well.
- the first bearing 51, the first seal member 61, and the second seal member 62 are arranged to overlap each other in the radial direction.
- the second bearing 52, the third bearing 53, the fourth bearing 54, and the fifth bearing 55 are arranged so as to overlap each other in the radial direction.
- the second bearing 52 and the third bearing 53 are arranged on both sides of the flange portion 11 in the axial direction so as to sandwich the flange portion 11.
- thrust bearings that can receive an axial load are used as the second bearing 52 and the third bearing 53.
- the second bearing 52 is positioned in the radial direction by the axially retracting surface 41 a and the input shaft I that are continuously formed from the surface on the other axial side of the one side radial extending portion 41. That is, the second bearing 52 is fixed in a state where its outer peripheral surface is fitted to the axially retracting surface 41a and its inner peripheral surface is in contact with the outer peripheral surface of the input shaft I.
- the third bearing 53 is positioned in the radial direction by the axially retracting surface 45 d and the input shaft I that are formed continuously from the surface on the one side in the axial direction of the other side radially extending portion 45. That is, the third bearing 53 is fixed in a state where its outer peripheral surface is fitted to the axially retracting surface 45d and its inner peripheral surface is in contact with the outer peripheral surface of the input shaft I, thereby enabling radial positioning. Has been made.
- both the 1st bearing 51 and the 1st seal member 61 do not overlap with the one side radial direction extension part 41 in the axial direction, and are further on the one axial side rather than the said one side radial direction extension part 41.
- Arranging the arrangement is also one of the preferred embodiments of the present invention. Even in these cases, it is possible to appropriately realize the rotation support structure and the seal structure for the case 2 of the clutch housing CH at least on one side in the axial direction.
- both the fourth bearing 54 and the second seal member 62 do not overlap the other-side radial extending portion 45 in the axial direction, and are further further on the other axial side than the other-side radial extending portion 45.
- Arranging the arrangement is also one of the preferred embodiments of the present invention. Even in these cases, at least the rotation support structure and the seal structure for the case 2 of the clutch housing CH on the other side in the axial direction can be appropriately realized.
- the embodiment of the present invention is not limited to this.
- the fourth seal 54 is arranged at least on the rotor Ro side of the rotating electrical machine MG in the direction along the clutch housing CH on the outer side in the radial direction of the fourth bearing 54, the second seal member 62 is disposed on the fourth bearing 54.
- One of the preferred embodiments of the present invention is a configuration in which the second bearing 54 is arranged so as to be shifted to one axial side or the other axial side without overlapping with the fourth bearing 54 in the axial direction. .
- the second seal member 62 is disposed so as to overlap the piston 36 of the clutch CL in the axial direction.
- the embodiment of the present invention is not limited to this. That is, the second seal member 62 may be configured so as to be shifted to the one axial side or the other axial side with respect to the piston 36 without overlapping the piston 36 in the axial direction. This is one of the preferred embodiments.
- the flange portion 11 constituting a part of the connecting member has the notch groove 11a at the radially outer end and the one axial end, and the notch groove 11a
- the annular plate-like portion 22 is connected to the flange portion 11 while being in contact with one side in the axial direction.
- the embodiment of the present invention is not limited to this. That is, for example, the flange portion 11 has a notch groove at the radially outer end and the other axial end, and the annular plate-like portion 22 is in contact with the notch groove from the other axial side.
- a configuration connected to the flange portion 11 is also one of the preferred embodiments of the present invention.
- the annular plate-like portion 22 constituting another part of the connecting member may have a notch groove at the radially inner end thereof, and the flange portion 11 may be connected to the notch groove. This is one of the preferred embodiments of the present invention.
- the one-side radial extending portion 41 is formed in a cylindrical axial retraction formed so as to continuously retreat from the other axial surface to the one axial side.
- the case where the second bearing 52 is positioned in the radial direction by the axially retracting surface 41a has been described as an example.
- the embodiment of the present invention is not limited to this. That is, for example, the one-side radial extending portion 41 has a cylindrical axial projecting portion formed so as to project from the other axial surface to the other axial direction, and the axial projecting portion A configuration in which the two bearings 52 are positioned in the radial direction is also a preferred embodiment of the present invention.
- both the first support mechanism and the second support mechanism are configured using ball bearings as the first bearing 51 and the second bearing 52 has been described as an example.
- the embodiment of the present invention is not limited to this. That is, if the mechanism is capable of receiving both a radial load and an axial load, for example, a radial bearing such as a needle bearing capable of receiving a radial load and a thrust capable of receiving an axial load. It is also one of the preferred embodiments of the present invention that one or both of the first support mechanism and the second support mechanism are configured by a combination with a thrust bearing such as a bearing.
- the clutch hub 21 is drivingly connected so as to rotate integrally with the input shaft I, and the clutch drum 26 is driven and connected so as to rotate integrally with the intermediate shaft M.
- the embodiment of the present invention is not limited to this. That is, the drive connection relationship between the clutch hub 21 and the clutch drum 26 with the input shaft I and the intermediate shaft M is switched, and the clutch hub 21 is driven and connected to rotate integrally with the intermediate shaft M, and the clutch drum 26 is input. It is also one of preferred embodiments of the present invention that the drive connection is made so as to rotate integrally with the shaft I.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transportation (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Power Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Hybrid Electric Vehicles (AREA)
- Arrangement Of Transmissions (AREA)
- Electric Propulsion And Braking For Vehicles (AREA)
Abstract
Description
更に、一般に装置全体の軸方向寸法は極力短縮されていることが好ましい。
従って、上記の特徴構成によれば、クラッチ及び回転電機をそれぞれ適切に冷却することが可能であると共に、クラッチの効果的な冷却のために設けられるクラッチハウジングを適切かつ円滑に支持することが可能であり、更に装置全体の軸方向寸法を短縮することが可能なハイブリッド駆動装置を提供することができる。
また、この構成では、第二シール機構及び第二支持機構の双方が、他方側径方向延在部の一部を構成する段付円筒部と軸方向に重複して配置されることになるので、装置全体の軸方向寸法を短縮することができる。
この構成によれば、第一シール機構及び第二シール機構の径方向外側において軸方向に広くなる空間を利用して、当該空間に複数の摩擦プレートを適切に配置することができる。
して軸方向一方側から当接した状態で前記軸側連結部に連結され、前記一方側径方向延在部は、その軸方向他方側の面から連続して軸方向一方側に引退するように形成された円筒状の軸方向引退面を有し、前記第三支持機構は、前記軸方向引退面により径方向に位置決めされ、前記第四支持機構は、前記第三支持機構よりも径方向外側に配置されると共に、前記軸側連結部の径方向外側端により径方向に位置決めされている構成とすると好適である。
また、一方側径方向延在部に形成される軸方向引退面により第三支持機構の径方向の位置決めをすることができると共に、軸側連結部の径方向外側端により第四支持機構の径方向の位置決めをすることができる。更に、例えば第三支持機構と第四支持機構とを軸側連結部の軸方向両側で軸方向に並べて配置する場合等と比較して、装置全体の軸方向寸法を短縮することができる。
本発明の第一の実施形態について、図面を参照して説明する。ハイブリッド駆動装置1は、車両の駆動力源として内燃機関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、いわゆる1モータパラレルタイプのハイブリッド駆動装置として構成されている。
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1に示すように、このハイブリッド駆動装置1は、車両の第一の駆動力源としての内燃機関Eに駆動連結される入力軸Iと、車両の第二の駆動力源としての回転電機MGと、変速機構TMと、回転電機MGに駆動連結されると共に変速機構TMに駆動連結される中間軸Mと、車輪Wに駆動連結される出力軸Oと、を備えている。また、ハイブリッド駆動装置1は、入力軸Iと中間軸Mとの間の駆動力の伝達及び遮断を切替可能に設けられるクラッチCLと、カウンタギヤ機構Cと、出力用差動歯車装置DFと、を備えている。これらの各構成は、駆動装置ケースとしてのケース2内に収容されている。本実施形態においては、入力軸Iが本発明における「第一軸」に相当し、中間軸Mが本発明における「第二軸」に相当する。
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説明する。図2に示すように、ケース2は、その内部に収容される回転電機MGや変速機構TM等の各収容部品の外周を覆うケース周壁3と、当該ケース周壁3の軸方向一方側(内燃機関E側であって図2における右側、以下同じ。)の開口を塞ぐ第一支持壁4と、当該第一支持壁4よりも軸方向他方側(内燃機関Eとは反対側であって図2における左側、以下同じ。)において軸方向で回転電機MGと変速機構TMとの間に配置される第二支持壁7と、を備えている。更に、図示はしていないが、このケース2は、ケース周壁3の軸方向他方側の端部を塞ぐ端部支持壁を備えている。
で固定されており、これにより径方向の位置決めがなされている。また、第三軸受53は、フランジ部11の径方向外側端により径方向に位置決めされている。すなわち、第三軸受53は、その内周面をフランジ部11の切欠溝11aよりも軸方向他方側の部位の外周面に嵌合させた状態で固定されており、これにより径方向の位置決めがなされている。
次に、本実施形態に係るクラッチハウジングCHの、ケース2に対する回転支持構造及びシール構造について説明する。本実施形態に係る回転支持構造及びシール構造は、概略的には、第一軸受51、第四軸受54、第一シール部材61、及び第二シール部材62により実現されている。すなわち、本実施形態に係る回転支持構造は、概略的には、クラッチハウジングCHの軸方向一方側で当該クラッチハウジングCHをケース2に対して回転可能な状態で軸方向及び径方向に支持する第一軸受51と、軸方向他方側で当該クラッチハウジングCHをケース2に対して回転可能な状態で軸方向及び径方向に支持する第四軸受54と、により実現されている。また、本実施形態に係るシール構造は、概略的には、クラッチハウジングCHに沿った方向で、第一軸受51よりも回転電機MGのロータRo側においてケース2とクラッチハウジングCHとの間を油密状態とする第一シール部材61と、第四軸受54よりも回転電機MGのロータRo側においてケース2とクラッチハウジングCHとの間を油密状態とする第二シール部材62と、により実現されている。以下、詳細に説明する。
より具体的には、第四軸受54は、他方側径方向延在部45の径方向外側部分と軸方向に重複して配置されている。また、第四軸受54に対して軸方向一方側に隣接して配置される第二シール部材62も、当然ながら他方側径方向延在部45と軸方向に重複して配置されている。第二シール部材62は、他方側径方向延在部45の径方向中央部と軸方向に重複して配置されている。より具体的には、他方側径方向延在部45は、軸方向突出部46が設けられた第一円板状部45aと、当該第一円板状部45aに対して軸方向他方側にオフセットされて径方向外側に配置された第二円板状部45cと、第一円板状部45aと第二円板状部45cとの間のオフセット部を形成すると共にこれらを連結するように形成された段付円筒部45bと、を有しており、第二シール部材62は段付円筒部45bと軸方向に重複して配置されている。このようにして、本実施形態では、他方側径方向延在部45の第二円板状部45cに対して軸方向一方側にオフセットされた第一円板状部45aの軸方向他方側に形成される空間に、第四軸受54及び第二シール部材62の双方が配置されている。これにより、クラッチハウジングCHの軸方向他方側において、簡易な構成で当該クラッチハウジングCHの回転支持構造及びシール構造を実現しながら、軸方向寸法の短縮が図られている。
本発明の第二の実施形態について、図面を参照して説明する。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、本実施形態では、クラッチハウジングCHの軸方向他方側における当該クラッチハウジングCHのケース2に対する回転支持構造及びシール構造の配置構成が、上記第一の実施形態とは一部異なっている。そこで、以下では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。
最後に、本発明に係るハイブリッド駆動装置の、その他の実施形態について説明する。なお、以下のそれぞれの実施形態で開示される特徴構成は、その実施形態でのみ適用されるものではなく、矛盾が生じない限り、他の実施形態で開示される特徴構成と組み合わせて適用することも可能である。
(1)上記の各実施形態においては、第一軸受51及び第一シール部材61の双方が、一方側径方向延在部41と軸方向に重複して配置されてい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、例えば第一軸受51及び第一シール部材61のうち、軸方向他方側に配置される第一シール部材61のみが一方側径方向延在部41と軸方向に重複して配置された構成とすることも、本発明の好適な実施形態の一つである。或いは、第一軸受51及び第一シール部材61の双方が、一方側径方向延在部41と軸方向に重複することなく、当該一方側径方向延在部41よりも更に軸方向一方側に配置された構成とすることも、本発明の好適な実施形態の一つである。これらの場合であっても、少なくとも軸方向一方側におけるクラッチハウジングCHのケース2に対する回転支持構造及びシール構造を適切に実現できる。
2 ケース
4 第一支持壁(一方側支持壁部)
5 軸方向突出部(第一軸方向突出部)
7 第二支持壁(他方側支持壁部)
8 軸方向突出部(第三軸方向突出部)
21 クラッチハブ
22 円環板状部(ハブ側連結部)
31 摩擦プレート
36 ピストン
41 一方側径方向延在部
41a 軸方向引退面
42 軸方向突出部(第二軸方向突出部)
45 他方側径方向延在部
45a 第一円板状部
45b 段付円筒部
45c 第二円板状部
46 軸方向突出部(第四軸方向突出部)
51 第一軸受(第一支持機構)
52 第二軸受(第三支持機構)
53 第三軸受(第四支持機構)
54 第四軸受(第二支持機構)
61 第一シール部材(第一シール機構)
62 第二シール部材(第二シール機構)
E 内燃機関
D ダンパ
MG 回転電機
St ステータ
Ce コイルエンド部
Ro ロータ
I 入力軸(第一軸)
M 中間軸(第二軸)
TM 変速機構
CL クラッチ
CH クラッチハウジング
Claims (9)
- 内燃機関に駆動連結される第一軸と、回転電機と、前記第一軸と同軸上に配置され前記回転電機及び変速機構に駆動連結される第二軸と、前記第一軸と前記第二軸との間の駆動力の伝達及び遮断を切替可能に設けられるクラッチと、前記第一軸、前記第二軸、前記回転電機、及び前記クラッチを収容するケースと、を備えたハイブリッド駆動装置であって、
前記クラッチの軸方向両側及び径方向外側を包囲して前記クラッチを収容すると共に、前記第二軸に駆動連結され、その内部に油で満たされる油室を形成するクラッチハウジングを備え、
前記クラッチハウジングを前記ケースに対して回転可能な状態で径方向及び軸方向に支持する第一支持機構と、前記ケースと前記クラッチハウジングとの間を油密状態とする第一シール機構と、を前記クラッチハウジングの軸方向一方側に備え、
前記回転電機のロータが、前記クラッチハウジングの外周部に固定され、
前記ケースは、前記クラッチハウジングの軸方向一方側において径方向に延びる一方側支持壁部と、当該一方側支持壁部から軸方向他方側へ突出する筒状の第一軸方向突出部と、を有し、
前記クラッチハウジングは、前記クラッチの軸方向一方側に配置されて径方向に延びる一方側径方向延在部と、当該一方側径方向延在部から軸方向一方側へ突出する筒状の第二軸方向突出部と、を有し、
前記第二軸方向突出部は、軸方向他方側が大径部、軸方向一方側が小径部となる段付形状に形成され、
前記第一支持機構が、前記第二軸方向突出部の小径部の外周面と前記第一軸方向突出部の内周面とに接して配置され、
前記第一シール機構が、前記第二軸方向突出部の大径部の外周面と前記第一軸方向突出部の内周面とに接して、前記第一支持機構と軸方向に並んで配置されているハイブリッド駆動装置。 - 前記一方側径方向延在部は、径方向内側端部が径方向外側端部よりも軸方向他方側に位置する形状に形成され、
前記第一支持機構及び前記第一シール機構の一方又は双方が、前記一方側径方向延在部と軸方向に重複して配置されている請求項1に記載のハイブリッド駆動装置。 - 前記クラッチハウジングを前記ケースに対して回転可能な状態で径方向及び軸方向に支持する第二支持機構と、前記ケースと前記クラッチハウジングとの間を油密状態とする第二シール機構と、を前記クラッチハウジングの軸方向他方側に更に備え、
前記ケースは、前記クラッチハウジングの軸方向他方側において径方向に延びる他方側支持壁部と、当該他方側支持壁部から軸方向一方側へ突出する筒状の第三軸方向突出部と、を有し、
前記クラッチハウジングは、前記クラッチの軸方向他方側に配置されて径方向に延びる他方側径方向延在部と、当該他方側径方向延在部から軸方向他方側へ突出する筒状の第四軸方向突出部と、を有し、
前記第四軸方向突出部は、軸方向一方側が大径部、軸方向他方側が小径部となる段付形状に形成され、
前記第二支持機構が、前記第四軸方向突出部の小径部の外周面と前記第三軸方向突出部の内周面とに接して配置され、
前記第二シール機構が、前記第四軸方向突出部の大径部の外周面と前記第三軸方向突出部の内周面とに接して、前記第二支持機構と軸方向に並んで配置されている請求項1又は2に記載のハイブリッド駆動装置。 - 前記他方側径方向延在部は、径方向内側端部が径方向外側端部よりも軸方向一方側に位置する形状に形成され、
前記第二支持機構及び前記第二シール機構の一方又は双方が、前記他方側径方向延在部と軸方向に重複して配置されている請求項3に記載のハイブリッド駆動装置。 - 前記クラッチハウジングを前記ケースに対して回転可能な状態で径方向及び軸方向に支持する第二支持機構と、前記ケースと前記クラッチハウジングとの間を油密状態とする第二シール機構と、を前記クラッチハウジングの軸方向他方側に更に備え、
前記ケースは、前記クラッチハウジングの軸方向他方側において径方向に延びる他方側支持壁部と、当該他方側支持壁部から軸方向一方側へ突出する筒状の第三軸方向突出部と、を有し、
前記クラッチハウジングは、前記クラッチの軸方向他方側に配置されて径方向に延びる他方側径方向延在部と、当該他方側径方向延在部から軸方向他方側へ突出する筒状の第四軸方向突出部と、を有し、
前記他方側径方向延在部は、前記第四軸方向突出部が設けられた第一円板状部と、前記第一円板状部に対して軸方向他方側にオフセットされて径方向外側に配置された第二円板状部と、前記第一円板状部と前記第二円板状部とを連結するように形成された段付円筒部と、を有し、
前記第二支持機構が、前記第四軸方向突出部の外周面と前記第三軸方向突出部の内周面とに接して配置され、
前記第二シール機構が、前記第三軸方向突出部の外周面と前記段付円筒部の内周面とに接して、前記第二支持機構と軸方向に重複して配置されている請求項1又は2に記載のハイブリッド駆動装置。 - 前記クラッチが有する複数の摩擦プレートが、前記第一シール機構及び前記第二シール機構よりも径方向外側に配置されている請求項3から5のいずれか一項に記載のハイブリッド駆動装置。
- 前記クラッチは、前記複数の摩擦プレートを押圧するためのピストンを有し、
前記第二シール機構が、前記ピストンと軸方向に重複して配置されている請求項6に記載のハイブリッド駆動装置。 - 前記第一軸と前記クラッチのクラッチハブとを連結するように径方向に延びる連結部材と、前記連結部材の軸方向一方側の面及び軸方向他方側の面にそれぞれ接して配置され、前記連結部材と前記クラッチハウジングとの間を相対回転可能に支持する第三支持機構及び第四支持機構と、を備え、
前記連結部材は、前記第一軸から径方向外側に延びる軸側連結部と、前記クラッチハブの一部であって径方向内側に延びるハブ側連結部と、からなり、
前記ハブ側連結部は、前記軸側連結部の径方向外側端部に形成された切欠溝に対して軸方向一方側から当接した状態で前記軸側連結部に連結され、
前記一方側径方向延在部は、その軸方向他方側の面から連続して軸方向一方側に引退するように形成された円筒状の軸方向引退面を有し、
前記第三支持機構は、前記軸方向引退面により径方向に位置決めされ、
前記第四支持機構は、前記第三支持機構よりも径方向外側に配置されると共に、前記軸側連結部の径方向外側端により径方向に位置決めされている請求項1から7のいずれか一項に記載のハイブリッド駆動装置。 - 前記一方側支持壁部よりも軸方向一方側に配置されて前記第一軸と前記内燃機関との間に介挿されるダンパ装置を備え、
前記ダンパ装置が、前記回転電機のステータから軸方向に突出するコイルエンド部と軸方向に重複して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ハイブリッド駆動装置。
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112011100243T DE112011100243T5 (de) | 2010-03-31 | 2011-02-10 | Hybridantriebsvorrichtung |
CN2011800126038A CN102791504A (zh) | 2010-03-31 | 2011-02-10 | 混合动力驱动装置 |
US13/137,284 US8448541B2 (en) | 2010-03-31 | 2011-08-03 | Hybrid drive speed change device |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2010081513A JP5168598B2 (ja) | 2010-03-31 | 2010-03-31 | ハイブリッド駆動装置 |
JP2010-081513 | 2010-03-31 |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/137,284 Continuation US8448541B2 (en) | 2010-03-31 | 2011-08-03 | Hybrid drive speed change device |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2011122128A1 true WO2011122128A1 (ja) | 2011-10-06 |
Family
ID=44708087
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2011/052863 WO2011122128A1 (ja) | 2010-03-31 | 2011-02-10 | ハイブリッド駆動装置 |
Country Status (5)
Country | Link |
---|---|
US (2) | US20110239818A1 (ja) |
JP (1) | JP5168598B2 (ja) |
CN (1) | CN102791504A (ja) |
DE (1) | DE112011100243T5 (ja) |
WO (1) | WO2011122128A1 (ja) |
Families Citing this family (52)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5581922B2 (ja) * | 2010-09-10 | 2014-09-03 | アイシン精機株式会社 | ハイブリッド車両用駆動装置およびケース |
JP5589247B2 (ja) * | 2011-11-04 | 2014-09-17 | アイシン・エィ・ダブリュ株式会社 | 車両用駆動装置 |
US8960393B2 (en) | 2012-01-31 | 2015-02-24 | Ford Global Technologies, Llc | Modular powertrain component for hybrid electric vehicles |
US9421857B2 (en) | 2012-01-31 | 2016-08-23 | Ford Global Technologies, Llc | Modular powertrain component for hybrid electric vehicles |
US8851861B2 (en) * | 2012-01-31 | 2014-10-07 | Ford Global Technologies, Llc | Powertrain hydraulic system for hybrid electric vehicles |
US9593761B2 (en) | 2012-01-31 | 2017-03-14 | Ford Global Technologies, Llc | Pneumatic venting of modular hybrid electric vehicle |
US9579965B2 (en) * | 2012-01-31 | 2017-02-28 | Ford Global Technologies, Llc | Modular powertrain component for hybrid electric vehicles |
US9581210B2 (en) | 2012-01-31 | 2017-02-28 | Ford Global Technologies, Llc | Modular hybrid electric vehicle rotor hub |
US9416826B2 (en) | 2012-01-31 | 2016-08-16 | Ford Global Technologies, Llc | Disconnect clutch for modular hybrid electric vehicle |
US8770364B2 (en) * | 2012-01-31 | 2014-07-08 | Ford Global Technologies, Llc | Modular powertrain component for hybrid electric vehicles |
DE102012214327A1 (de) * | 2012-08-10 | 2014-02-13 | Engineering Center Steyr Gmbh & Co. Kg | Antriebseinheit für ein Hybridfahrzeug |
WO2014051110A1 (ja) * | 2012-09-28 | 2014-04-03 | アイシン・エィ・ダブリュ株式会社 | ハイブリッド駆動装置 |
GB2509084B (en) * | 2012-12-19 | 2015-06-10 | Jaguar Land Rover Ltd | Hybrid vehicle powertrain |
JP6115131B2 (ja) * | 2012-12-28 | 2017-04-19 | 日産自動車株式会社 | 乾式多板クラッチ装置 |
DE102013204784B4 (de) * | 2013-03-19 | 2018-01-11 | Robert Bosch Gmbh | Elektrische Fahrzeugachsenvorrichtung |
WO2014192376A1 (ja) * | 2013-05-31 | 2014-12-04 | アイシン・エィ・ダブリュ株式会社 | 車両用駆動装置 |
JP6070444B2 (ja) * | 2013-06-28 | 2017-02-01 | アイシン・エィ・ダブリュ株式会社 | 車両用駆動装置 |
USRE48173E1 (en) * | 2013-05-31 | 2020-08-25 | Aisin Aw Co., Ltd. | Vehicle driving device |
US9849791B2 (en) * | 2013-05-31 | 2017-12-26 | Aisin Aw Co., Ltd. | Vehicle drive device |
JP6048347B2 (ja) * | 2013-08-29 | 2016-12-21 | アイシン・エィ・ダブリュ株式会社 | 車両用駆動装置 |
DE102014014236A1 (de) | 2014-02-22 | 2015-08-27 | Borgwarner Inc. | Antriebsstrang für ein Kraftfahrzeug und Verfahren zum Betrieb eines solchen Antriebsstrangs |
JP6027044B2 (ja) * | 2014-03-14 | 2016-11-16 | トヨタ自動車株式会社 | 車両用駆動装置とその組付方法 |
JP2016033003A (ja) * | 2014-07-29 | 2016-03-10 | アイシン・エィ・ダブリュ株式会社 | ハイブリッド駆動装置 |
DE102016013417A1 (de) * | 2016-01-19 | 2017-07-20 | Borgwarner Inc. | Drehmomentübertragungseinrichtung für ein Kraftfahrzeug |
CN107139711B (zh) * | 2016-03-01 | 2022-01-11 | 舍弗勒技术股份两合公司 | 用于混合动力汽车的动力耦合装置 |
DE102016210857A1 (de) * | 2016-06-17 | 2017-12-21 | Robert Bosch Gmbh | Elektrischer Achsantrieb für ein Fahrzeug |
DE102016211940A1 (de) * | 2016-06-30 | 2018-01-04 | Zf Friedrichshafen Ag | Hybridantriebsmodul für einen Kraftfahrzeugantriebsstrang, sowie Kraftfahrzeugantriebsstrang |
DE102017129269A1 (de) * | 2017-03-06 | 2018-09-06 | Schaeffler Technologies AG & Co. KG | Hybridmodul mit integrierter Sensoreinrichtung sowie Hybridantriebsstrang mit Hybridmodul |
JP6531133B2 (ja) * | 2017-04-27 | 2019-06-12 | 本田技研工業株式会社 | ハイブリッド車両の駆動装置 |
CN107482827A (zh) * | 2017-04-28 | 2017-12-15 | 宝沃汽车(中国)有限公司 | Isg电机的密封结构及具有其的动力总成和车辆 |
DE102017218868A1 (de) * | 2017-10-23 | 2019-04-25 | Audi Ag | Antriebseinrichtung |
DE102018203073A1 (de) * | 2018-03-01 | 2019-09-05 | Zf Friedrichshafen Ag | Antriebsanordnung für ein Schienenfahrzeug |
DE102018205460A1 (de) * | 2018-04-11 | 2019-10-17 | Zf Friedrichshafen Ag | Hybridantriebsmodul für ein Kraftfahrzeug |
DE102018211374A1 (de) * | 2018-07-10 | 2020-01-16 | Zf Friedrichshafen Ag | Rotorträger für eine elektrische Maschine |
DE102018219676A1 (de) | 2018-11-16 | 2020-05-20 | Zf Friedrichshafen Ag | Konuselement als Kupplung im K0-Bauraum |
JP7209742B2 (ja) * | 2019-01-09 | 2023-01-20 | 株式会社アイシン | 車両用駆動装置 |
EP3885174A4 (en) * | 2019-01-09 | 2022-01-12 | Aisin Corporation | HYBRID DRIVE DEVICE |
DE102019001957C5 (de) * | 2019-03-20 | 2024-03-28 | Mercedes-Benz Group AG | Hybridantriebsystem |
US10933730B2 (en) * | 2019-06-26 | 2021-03-02 | Ford Global Technologies, Llc | Power split hybrid-electric powertrain with multi-step gearset |
DE102019123791A1 (de) * | 2019-09-05 | 2021-03-11 | Schaeffler Technologies AG & Co. KG | Drehmomentübertragungsvorrichtung mit einem geschmierten Abstützlager |
US20210143717A1 (en) * | 2019-11-08 | 2021-05-13 | Schaeffler Technologies AG & Co. KG | Resolver stator clamping plate |
JP7411392B2 (ja) * | 2019-11-18 | 2024-01-11 | 株式会社アイシン | 駆動装置 |
JP2021132435A (ja) * | 2020-02-18 | 2021-09-09 | 本田技研工業株式会社 | 車両用駆動装置 |
US11114917B1 (en) | 2020-02-26 | 2021-09-07 | Schaeffler Technologies AG & Co. KG | Electric motor rotor for hybrid module |
JP7439673B2 (ja) * | 2020-07-16 | 2024-02-28 | トヨタ自動車株式会社 | 駆動装置のシール構造 |
US11245318B1 (en) * | 2020-07-29 | 2022-02-08 | Schaeffler Technologies AG & Co. KG | Resolver clamping plate for electric motor |
FR3115580B1 (fr) * | 2020-10-23 | 2022-09-23 | Valeo Embrayages | Dispositif de transmission de couple, en particulier pour véhicule automobile |
EP3988808A1 (fr) * | 2020-10-23 | 2022-04-27 | Valeo Embrayages | Dispositif de transmission de couple, en particulier pour vehicule automobile |
US11876433B2 (en) * | 2020-11-19 | 2024-01-16 | Nidec Corporation | Drive device |
DE102020007296A1 (de) | 2020-11-30 | 2022-06-02 | Daimler Ag | Hybridgetriebe für ein Fahrzeug |
US11912132B2 (en) * | 2020-11-30 | 2024-02-27 | Mercedes-Benz Group AG | Hybrid transmission for a vehicle |
US11926220B2 (en) | 2020-11-30 | 2024-03-12 | Mercedes-Benz Group AG | Hybrid transmission for a vehicle |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2003063261A (ja) * | 2001-08-24 | 2003-03-05 | Honda Motor Co Ltd | ハイブリッド車両の動力伝達装置 |
JP2004215393A (ja) * | 2002-12-27 | 2004-07-29 | Nissan Motor Co Ltd | 複軸多層モータのロータシール構造 |
WO2006054661A1 (ja) * | 2004-11-19 | 2006-05-26 | Aisin Aw Co., Ltd. | ハイブリッド車用駆動装置 |
JP2009101730A (ja) * | 2007-10-19 | 2009-05-14 | Aisin Aw Co Ltd | ハイブリッド駆動装置 |
Family Cites Families (23)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5427196A (en) * | 1992-07-08 | 1995-06-27 | Kabushikikaisha Equos Research | Electric motor drive system |
US6258001B1 (en) * | 1999-03-26 | 2001-07-10 | Aisin Aw Co., Ltd. | Vehicle drive train |
JP3651575B2 (ja) * | 1999-09-06 | 2005-05-25 | スズキ株式会社 | 車両の推進装置 |
DE60234104D1 (de) * | 2001-08-10 | 2009-12-03 | Aisin Aw Co | Antriebsvorrichtung für hybridfahrzeug |
FR2829538B1 (fr) * | 2001-09-12 | 2003-12-19 | Valeo Equip Electr Moteur | Montage d'un volant d'un embrayage, portant le rotor d'une machine electrique tournante, sur le vilebrequin du moteur d'un vehicule |
JP4069777B2 (ja) | 2002-04-03 | 2008-04-02 | アイシン・エィ・ダブリュ株式会社 | ハイブリッド車用駆動装置 |
JP4225150B2 (ja) * | 2003-08-12 | 2009-02-18 | アイシン・エィ・ダブリュ株式会社 | 電動駆動制御装置及び電動駆動制御方法 |
DE10346640A1 (de) | 2003-10-08 | 2005-05-12 | Zahnradfabrik Friedrichshafen | Antriebsstrang für ein Hybridfahrzeug |
JP3998041B2 (ja) * | 2004-04-28 | 2007-10-24 | アイシン・エィ・ダブリュ株式会社 | ハイブリッド車用駆動装置 |
CN100491776C (zh) * | 2004-09-23 | 2009-05-27 | 通用汽车环球科技运作公司 | 车辆变速箱 |
CN101595320B (zh) * | 2007-01-29 | 2011-11-30 | 舍弗勒技术两合公司 | 具有湿式起动离合器的混合应用的动力总成系统 |
DE102008004097A1 (de) * | 2007-06-29 | 2009-01-02 | TRüTZSCHLER GMBH & CO. KG | Vorrichtung zur Fasersortierung bzw. -selektion eines Faserverbandes aus Textilfasern, insbesondere zum Kämmen, der über Zuführmittel einer Fasersortiereinrichtung, insbesondere Kämmeinrichtung zugeführt wird |
JP5246466B2 (ja) * | 2007-10-19 | 2013-07-24 | アイシン・エィ・ダブリュ株式会社 | ハイブリッド駆動装置 |
DE102008040497A1 (de) * | 2008-07-17 | 2010-01-21 | Zf Friedrichshafen Ag | Hybridantriebsstrang für ein Kraftfahrzeug |
ATE479029T1 (de) * | 2008-07-25 | 2010-09-15 | Zahnradfabrik Friedrichshafen | Antriebseinheit für ein hybridfahrzeug und verfahren zu deren montage |
JP4941778B2 (ja) * | 2008-10-31 | 2012-05-30 | アイシン・エィ・ダブリュ株式会社 | 車両用駆動装置 |
JP5297352B2 (ja) * | 2009-11-19 | 2013-09-25 | アイシン・エィ・ダブリュ株式会社 | 車両用駆動装置 |
US8997956B2 (en) * | 2009-11-19 | 2015-04-07 | Aisin Aw Co., Ltd. | Vehicle drive device |
JP5255555B2 (ja) * | 2009-12-18 | 2013-08-07 | アイシン・エィ・ダブリュ株式会社 | 車両用駆動装置 |
JP5278774B2 (ja) * | 2010-08-06 | 2013-09-04 | アイシン・エィ・ダブリュ株式会社 | 車両用駆動装置 |
JP2012086826A (ja) * | 2010-09-24 | 2012-05-10 | Aisin Aw Co Ltd | 車両用駆動装置 |
JP2012182861A (ja) * | 2011-02-28 | 2012-09-20 | Aisin Aw Co Ltd | 車両用駆動装置 |
JP5610226B2 (ja) * | 2011-03-22 | 2014-10-22 | アイシン・エィ・ダブリュ株式会社 | 車両用駆動装置 |
-
2010
- 2010-03-31 JP JP2010081513A patent/JP5168598B2/ja not_active Expired - Fee Related
-
2011
- 2011-02-10 CN CN2011800126038A patent/CN102791504A/zh active Pending
- 2011-02-10 DE DE112011100243T patent/DE112011100243T5/de not_active Withdrawn
- 2011-02-10 WO PCT/JP2011/052863 patent/WO2011122128A1/ja active Application Filing
- 2011-03-22 US US13/053,795 patent/US20110239818A1/en not_active Abandoned
- 2011-08-03 US US13/137,284 patent/US8448541B2/en not_active Expired - Fee Related
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2003063261A (ja) * | 2001-08-24 | 2003-03-05 | Honda Motor Co Ltd | ハイブリッド車両の動力伝達装置 |
JP2004215393A (ja) * | 2002-12-27 | 2004-07-29 | Nissan Motor Co Ltd | 複軸多層モータのロータシール構造 |
WO2006054661A1 (ja) * | 2004-11-19 | 2006-05-26 | Aisin Aw Co., Ltd. | ハイブリッド車用駆動装置 |
JP2009101730A (ja) * | 2007-10-19 | 2009-05-14 | Aisin Aw Co Ltd | ハイブリッド駆動装置 |
Also Published As
Publication number | Publication date |
---|---|
DE112011100243T5 (de) | 2012-10-31 |
CN102791504A (zh) | 2012-11-21 |
JP2011213189A (ja) | 2011-10-27 |
US8448541B2 (en) | 2013-05-28 |
US20110239818A1 (en) | 2011-10-06 |
US20120090425A1 (en) | 2012-04-19 |
JP5168598B2 (ja) | 2013-03-21 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP5168598B2 (ja) | ハイブリッド駆動装置 | |
JP5471955B2 (ja) | 回転電機及び車両用駆動装置 | |
WO2011062266A1 (ja) | 車両用駆動装置 | |
WO2012039378A1 (ja) | 車両用駆動装置 | |
US8678115B2 (en) | Vehicle drive device | |
WO2011062264A1 (ja) | 車両用駆動装置 | |
WO2011062265A1 (ja) | 車両用駆動装置 | |
WO2012039370A1 (ja) | 車両用駆動装置 | |
JP2011213230A (ja) | ハイブリッド駆動変速装置 | |
WO2012117798A1 (ja) | 車両用駆動装置 | |
JP2012001102A (ja) | ハイブリッド駆動装置 | |
JP2011213190A (ja) | ハイブリッド駆動装置 | |
WO2013018201A1 (ja) | ハイブリッド駆動装置 | |
JP5250013B2 (ja) | 車両用駆動装置 | |
JP4858783B2 (ja) | 流体ポンプ及び車両用駆動装置 | |
WO2012018027A1 (ja) | ハイブリッド駆動装置 | |
JP2021129361A (ja) | 装置 | |
JP2014015962A (ja) | 車両用駆動装置 | |
JP2011214655A (ja) | 摩擦係合装置 | |
JP5261461B2 (ja) | 車両用駆動装置 | |
JP2011207387A (ja) | 車両用駆動装置 | |
JP5406815B2 (ja) | 車両用駆動装置 | |
JP2011213231A (ja) | ハイブリッド駆動装置 | |
JP2011214671A (ja) | 変速装置 | |
JP2012067804A (ja) | 発進装置 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
WWE | Wipo information: entry into national phase |
Ref document number: 201180012603.8 Country of ref document: CN |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 11762369 Country of ref document: EP Kind code of ref document: A1 |
|
WWE | Wipo information: entry into national phase |
Ref document number: 112011100243 Country of ref document: DE Ref document number: 1120111002432 Country of ref document: DE |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 11762369 Country of ref document: EP Kind code of ref document: A1 |