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WO2012018027A1 - Dispositif d'entraînement hybride - Google Patents

Dispositif d'entraînement hybride Download PDF

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Publication number
WO2012018027A1
WO2012018027A1 PCT/JP2011/067707 JP2011067707W WO2012018027A1 WO 2012018027 A1 WO2012018027 A1 WO 2012018027A1 JP 2011067707 W JP2011067707 W JP 2011067707W WO 2012018027 A1 WO2012018027 A1 WO 2012018027A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
clutch
axial direction
oil
drive shaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2011/067707
Other languages
English (en)
Japanese (ja)
Inventor
糟谷悟
加藤博
鬼頭昌士
関祐一
杉坂繁
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Aisin AW Co Ltd
Original Assignee
Aisin AW Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2010177818A external-priority patent/JP5278774B2/ja
Priority claimed from JP2010177817A external-priority patent/JP5471955B2/ja
Application filed by Aisin AW Co Ltd filed Critical Aisin AW Co Ltd
Publication of WO2012018027A1 publication Critical patent/WO2012018027A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines
    • 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 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 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/26—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 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 motors or the generators
    • 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
    • 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 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 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 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
    • 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 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 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
    • B60L15/00—Methods, circuits, or devices for controlling the traction-motor speed of electrically-propelled vehicles
    • B60L15/20—Methods, circuits, or devices for controlling the traction-motor speed of electrically-propelled vehicles for control of the vehicle or its driving motor to achieve a desired performance, e.g. speed, torque, programmed variation of speed
    • 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
    • B60L3/00—Electric devices on electrically-propelled vehicles for safety purposes; Monitoring operating variables, e.g. speed, deceleration or energy consumption
    • B60L3/0023—Detecting, eliminating, remedying or compensating for drive train abnormalities, e.g. failures within the drive train
    • B60L3/0061—Detecting, eliminating, remedying or compensating for drive train abnormalities, e.g. failures within the drive train relating to electrical machines
    • 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
    • B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
    • B60W10/00—Conjoint control of vehicle sub-units of different type or different function
    • B60W10/04—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units
    • B60W10/08—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units including control of electric propulsion units, e.g. motors or generators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0434—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps; Pressure control
    • F16H57/0441—Arrangements of pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0467—Elements of gearings to be lubricated, cooled or heated
    • F16H57/0469—Bearings or seals
    • F16H57/0471—Bearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0467—Elements of gearings to be lubricated, cooled or heated
    • F16H57/0476—Electric machines and gearing, i.e. joint lubrication or cooling or heating thereof
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
    • H02K5/16—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields
    • H02K5/173—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using bearings with rolling contact, e.g. ball bearings
    • H02K5/1735—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using bearings with rolling contact, e.g. ball bearings radially supporting the rotary shaft at only one end of the rotor
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/006—Structural association of a motor or generator with the drive train of a motor vehicle
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
    • B60L2220/00—Electrical machine types; Structures or applications thereof
    • B60L2220/50—Structural details of electrical machines
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
    • B60L2240/00—Control parameters of input or output; Target parameters
    • B60L2240/40—Drive Train control parameters
    • B60L2240/42—Drive Train control parameters related to electric machines
    • B60L2240/421—Speed
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
    • B60L2240/00—Control parameters of input or output; Target parameters
    • B60L2240/40—Drive Train control parameters
    • B60L2240/42—Drive Train control parameters related to electric machines
    • B60L2240/423—Torque
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
    • B60L2240/00—Control parameters of input or output; Target parameters
    • B60L2240/40—Drive Train control parameters
    • B60L2240/44—Drive Train control parameters related to combustion engines
    • B60L2240/443—Torque
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
    • B60L2240/00—Control parameters of input or output; Target parameters
    • B60L2240/40—Drive Train control parameters
    • B60L2240/48—Drive Train control parameters related to transmissions
    • B60L2240/486—Operating parameters
    • 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
    • Y02T10/64—Electric machine technologies in electromobility
    • 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
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/72—Electric energy management in electromobility

Definitions

  • the present invention includes a first shaft that is drivingly connected to the internal combustion engine, a second shaft that is drivingly connected to the speed change mechanism, a clutch that selectively drives and connects the first shaft and the second shaft, a rotating electrical machine,
  • the present invention relates to a hybrid drive device including a case that houses a clutch and a rotating electrical machine.
  • an engine input shaft 10 (first shaft) that is drivingly connected to an engine 2 (internal combustion engine), and a belt-type continuously variable transmission ( A transmission input shaft 45 (second shaft) that is drive-coupled to the transmission mechanism) is configured to be selectively drive-coupled via a clutch 49.
  • the clutch 49 is accommodated in a casing formed by joining the front cover 24 and the rear cover 102.
  • a cylindrical portion 38 included in the rear cover 102 is disposed so as to penetrate the body 35 of the oil pump 34 and engage with a rotor 37 disposed in the pump chamber, and the oil pump 34 is rotated by the rotation of the casing.
  • the cylindrical portion 38 is a pump drive shaft that drives the oil pump 34.
  • the cylindrical portion 38 is rotatably supported with respect to the body 35 by a bush disposed between the outer peripheral surface of the cylindrical portion 38 and the inner peripheral surface of the body 35.
  • the cylindrical portion 38 extends through the body 35 to the pump chamber, and between the outer peripheral surface of the cylindrical portion 38 and the inner peripheral surface of the body 35. Since there is a gap, a part of the oil whose pressure is increased in the pump chamber leaks to the bush side in the axial direction through the gap. Since such oil leakage affects the amount of oil discharged from the pump chamber through the discharge chamber, it is desirable that the amount of oil leakage through the gap be limited.
  • Patent Document 1 an oil seal 39 is disposed on the opposite side of the bush from the pump chamber in the axial direction, so that oil is generated in a space where the motor / generator 3 (rotary electric machine) is disposed.
  • the motor / generator 3 rotary electric machine
  • Patent Document 1 does not disclose any means for limiting the amount of oil leakage through the gap.
  • a first shaft that is drivingly connected to an internal combustion engine
  • a second shaft that is drivingly connected to a transmission mechanism
  • a clutch that selectively drives and connects the first shaft and the second shaft
  • rotation A characteristic configuration of a hybrid drive device including an electric machine and a case housing the clutch and the rotating electric machine is driven and connected to one of the first shaft and the second shaft and houses the clutch.
  • a clutch case a pump case that is fixed to the case and forms a pump chamber therein, and a pump rotor that is rotatably disposed in the pump chamber, and is coaxial with the clutch case with respect to the clutch case
  • An oil pump disposed on one side in the axial direction, a first bearing that supports the clutch case radially on the one side in the axial direction, and the clutch case axially A second bearing that is radially supported with respect to the case on the other side, wherein the rotor of the rotating electrical machine is supported by the clutch case, and the first bearing includes an outer ring, an inner ring, and the outer ring A rolling element interposed between the inner ring and the clutch case, the clutch case including a pump drive shaft extending in one axial direction and drivingly connected to the pump rotor, the pump drive shaft including the first bearing and the
  • the pump case is supported by the case via a pump case, and the pump case includes a partition wall that partitions the first bearing and the pump rotor, and the partition wall is
  • a gap between the outer peripheral surface of the pump drive shaft and the inner peripheral surface of the drive shaft insertion hole is an oil flow passage flowing from the pump chamber to the first bearing, and the flow passage is Oil flow
  • a flow passage diameter difference that is a difference between the diameter of the outer peripheral surface of the pump drive shaft and the diameter of the inner peripheral surface of the drive shaft insertion hole in the flow passage is set so as to function as a restricting portion. It is in.
  • the flow passage that is the oil path when oil leaks in the axial direction along the outer peripheral surface of the pump drive shaft from the pump chamber functions as a throttle portion that restricts the oil flow path.
  • the flow path diameter difference is set. Therefore, the amount of oil leaking in the axial direction along the outer peripheral surface of the pump drive shaft from the pump chamber can be limited, and the amount of oil discharged from the pump chamber through the discharge chamber can be ensured appropriately. it can.
  • a dedicated member for restricting the oil flow rate in the flow passage it is possible to suppress an increase in size and cost in the axial direction of the hybrid drive device.
  • the clutch case provided with a pump drive shaft is radially supported with respect to the case by the 1st bearing and the 2nd bearing on both sides of an axial direction.
  • the first bearing that supports one side in the axial direction which is the side on which the pump drive shaft of the clutch case is provided, is a bearing that includes an outer ring, an inner ring, and a rolling element, and is radial compared to a bearing that does not include a rolling element. Bearings with high support accuracy are used. Therefore, the clutch case can be accurately supported in the radial direction, and the displacement in the radial direction of the outer peripheral surface of the pump drive shaft included in the clutch case can be easily suppressed within a relatively narrow range. It has become.
  • a drive shaft insertion hole which is another member that divides the flow passage in the radial direction, is provided in a pump case fixed to the case. That is, the radial width of the air gap between the outer peripheral surface of the pump drive shaft and the inner peripheral surface of the drive shaft insertion hole can be maintained within a relatively narrow range centered on a value determined according to the flow path diameter difference. It has a possible configuration. Therefore, it is easy to set the flow passage diameter difference to such a small value that the flow passage functions properly as a throttle portion while suppressing contact between the outer peripheral surface of the pump drive shaft and the inner peripheral surface of the drive shaft insertion hole. It has a configuration.
  • the flow passage diameter difference is set to be larger than the maximum value of the amount by which the pump drive shaft supported by the first bearing can be displaced in the radial direction, and the flow passage cross-sectional area of the flow passage is It is preferable that the flow path diameter difference is set so as to be smaller than a flow path cross-sectional area of a flow path in the pump that is formed by a gap between the partition wall and the pump rotor and communicates with the flow path.
  • the flow path diameter difference is set to be larger than the maximum value of the amount by which the pump drive shaft supported by the first bearing can be displaced in the radial direction. Contact with the inner peripheral surface of the hole can be suppressed. Also, since the flow passage cross-sectional area of the flow passage is smaller than the flow passage cross-sectional area of the flow passage in the pump, only a part of the oil flowing through the flow passage in the pump is discharged into the flow passage without being discharged from the discharge chamber. Is possible. Therefore, the flow path can be appropriately functioned as the throttle portion while suppressing contact between the outer peripheral surface of the pump drive shaft and the inner peripheral surface of the drive shaft insertion hole.
  • the pump drive shaft is formed in a stepped shape in which one side in the axial direction is a small diameter portion and the other side in the axial direction is a large diameter portion, and an inner peripheral surface of the drive shaft insertion hole is an outer peripheral surface of the small diameter portion.
  • the first bearing is disposed so as to be in contact with the outer peripheral surface of the large-diameter portion, the difference between the diameter of the large-diameter portion and the diameter of the small-diameter portion is defined as a pump shaft step width, and the flow It is preferable that the path diameter difference is set to a value larger than a maximum value of an amount by which the pump drive shaft supported by the first bearing can be displaced in the radial direction and smaller than the pump shaft step width.
  • the flow path diameter difference is set to be larger than the maximum value of the amount by which the pump drive shaft supported by the first bearing can be displaced in the radial direction. Contact with the inner peripheral surface of the hole can be suppressed.
  • the inner peripheral surface of the drive shaft insertion hole can be disposed at a position close to the radially outer side with respect to the outer peripheral surface of the small diameter portion. It has an easy configuration. Therefore, the gap between the inner peripheral surface of the drive shaft insertion hole and the outer peripheral surface of the small diameter portion can be made a minute space, and the contact between the outer peripheral surface of the pump drive shaft and the inner peripheral surface of the drive shaft insertion hole can be reduced.
  • the flow path can be appropriately functioned as the throttle portion while being suppressed.
  • the pump drive shaft includes a supply oil passage for supplying oil to the clutch, and the pump case is disposed on the opposite side of the partition wall in the axial direction with respect to the pump rotor. It is preferable that a partition wall that partitions one axial side of the pump chamber is provided, and a partition wall side pump internal flow path formed by a gap between the partition wall and the pump rotor communicates with the supply oil path. It is.
  • the oil that has not been discharged to the flow passage can be actively guided to the supply oil passage for supplying oil to the clutch by the flow passage functioning as a throttle portion. Therefore, by securing the discharge destination of the oil that circulates in the pump chamber without being discharged from the discharge chamber, the amount of oil discharged to the flow passage can be appropriately limited and not discharged from the discharge chamber.
  • the oil circulating in the pump chamber can be used effectively.
  • the clutch case is arranged on one side in the axial direction of the clutch and extends in the radial direction, and has a one-side radial extension portion in which the pump drive shaft is provided at a radially inner end portion;
  • the other side radial extending portion that is arranged on the other side in the axial direction and extends in the radial direction, and a cylindrical axial direction extending portion that is arranged on the outer side in the radial direction of the clutch and extends in the axial direction.
  • the electric machine is disposed coaxially with the clutch case, and the rotor of the rotating electric machine is fixed in contact with the outer peripheral surface of the axially extending portion, and the other radial extending portion and the axial direction are fixed.
  • the extending portion is integrally formed, and the one side radial extending portion and the axial extending portion are joined and integrated by welding, and the welding joined portion of the rotor When located radially outward from the inner surface It is suitable.
  • the welded joint can be positioned away from the pump drive shaft in the radial direction. Therefore, it can suppress that the one side radial direction extension part in which the pump drive shaft and the pump drive shaft were provided in the radial direction inner end part by the heat
  • FIG. 3 is a partially enlarged view of FIG. 2.
  • 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, a rotating electrical machine MG, an intermediate shaft M that is drivingly connected to the speed change mechanism TM, and an input shaft.
  • a clutch CL that selectively drives and connects the I and the intermediate shaft M, and a case 2 that houses the clutch CL and the rotating electrical machine MG.
  • the hybrid drive device 1 according to the present embodiment includes a clutch case CH that is supported in the radial direction with respect to the case 2 on both sides in the axial direction (see FIG. 2), and a pump drive shaft.
  • the flow path L (see FIG.
  • axial direction In the following description, unless otherwise specified, “axial direction”, “circumferential direction”, and “radial direction” are defined on the basis of the rotational axes of the input shaft I and the intermediate shaft M arranged on the same axis. Yes. These rotating shafts correspond to the rotating shafts of the rotating elements included in the clutch CL, the clutch case CH, the inner rotor 18b included in the oil pump 18, and the rotor Ro included in the rotating electrical machine MG.
  • the left side in FIG. 2 is referred to as “one axial side” and the right side in FIG. 2 is referred to as “the other axial direction” unless otherwise specified.
  • 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 and the intermediate shaft M correspond to the “first axis” and the “second axis” in the present invention, respectively.
  • 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 the rotating electrical machine MG and the speed change mechanism TM housed therein, and the other axial side of the case peripheral wall 3 (internal combustion engine).
  • the first support wall 4 that closes the opening on the E side), and the rotating electrical machine MG and the speed change in the axial direction on one axial side of the first support wall 4 (on the side opposite to the internal combustion engine E, that is, the speed change mechanism TM side).
  • a second support wall 7 disposed between the mechanism TM.
  • the case 2 includes an end support wall (not shown) that closes one end of the case peripheral wall 3 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 integrally provided with a cylindrical (boss-shaped) axial projecting portion 5 projecting to one axial side.
  • the first support wall 4 is located on one axial side so that the radially inner portion is positioned on one axial side with respect to the radially outer portion in the portion where the input shaft I is penetrated. It is set as the wall part which has the shape curved in the dish shape which becomes convex toward it.
  • the first support wall 4 is disposed adjacent to a clutch case CH, which will be described later, at a predetermined interval on the other side in the axial direction. 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 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.
  • An axial through hole is formed in the second support wall 7.
  • the second support wall 7 is integrally provided with an overall cylindrical (boss-like) cylindrical portion 7a extending in the axial direction at the radially inner end thereof, and the inner portion of the cylindrical portion 7a
  • the peripheral surface defines the outer edge of the through hole formed in the second support wall 7.
  • the cylindrical portion 7a functions as a resolver fixing portion for fixing the sensor stator of the resolver 19, and also causes the pump case 8 (the pump body 90 in this example) of the oil pump 18 in the radial direction. It also functions as a positioning part for positioning.
  • the second support wall 7 is disposed adjacent to the clutch case CH at a predetermined interval on one side in the axial direction.
  • the oil pump 18 is provided inside the second support wall 7 in the radial direction with respect to the radial direction.
  • the oil pump 18 is provided between the speed change mechanism TM and the clutch case CH in the axial direction, in other words, between the speed change mechanism TM and the rotating electrical machine MG.
  • the oil pump 18 is disposed coaxially with the input shaft I and the intermediate shaft M.
  • the clutch case CH is also arranged coaxially with the input shaft I and the intermediate shaft M.
  • the speed change mechanism TM is arranged on one side in the axial direction with respect to the clutch case CH. Therefore, it can be said that the oil pump 18 is disposed coaxially with the clutch case CH on one side in the axial direction with respect to the clutch case CH.
  • the oil pump 18 is fixed to the case 2 and includes a pump case 8 that forms a pump chamber 18a therein, an inner rotor 18b that is rotatably disposed in the pump chamber 18a, and a rotatably disposed in the pump chamber 18a.
  • the pump case 8 is formed by joining a pump body 90 disposed on the other side in the axial direction and a pump cover 91 disposed on the one side in the axial direction.
  • An axial through hole is formed in the pump case 8 (specifically, both the pump body 90 and the pump cover 91), and the intermediate shaft M inserted through the through hole is connected to the pump case 8 ( It penetrates the oil pump 18).
  • the inner rotor 18b corresponds to the “pump rotor” in the present invention.
  • the pump body 90 is an annular plate-like member extending in the radial direction and the circumferential direction, and a cylindrical (boss-like) axial protruding portion 90b that protrudes on the other side in the axial direction is formed at the other end in the axial direction.
  • the pump body 90 has a shape in which the other side in the axial direction bulges out in a cylindrical shape as a whole, and has a shape protruding toward the clutch case CH and the rotating electrical machine MG in the axial direction.
  • a recess for forming the pump chamber 18a is formed in a circular cross section when viewed from the axial direction on one end face in the axial direction of the pump body 90.
  • the pump body 90 is positioned in the radial direction by fitting the outer peripheral surface of the pump body 90 to the inner peripheral surface of the cylindrical portion 7 a of the second support wall 7. Specifically, the pump body 90 is disposed so that the outer peripheral surface of the pump body 90 and the inner peripheral surface of the cylindrical portion 7a face each other, and the outer peripheral surface of the pump body 90 and the inner peripheral surface of the cylindrical portion 7a.
  • a fourth seal member 64 is interposed therebetween.
  • the fourth seal member 64 is an O-ring, and is attached to a concave groove formed in the outer peripheral surface of the pump body 90 and extending in the circumferential direction.
  • the space between the outer peripheral surface of the pump body 90 and the inner peripheral surface of the cylindrical portion 7a of the second support wall 7 is oil-tight (liquid-tight). It will be sealed. That is, the pump body 90 is oil-tightly fitted to the cylindrical portion 7 a via the fourth seal member 64 and is positioned and held on the second support wall 7.
  • the pump cover 91 is an annular plate member extending in the radial direction and the circumferential direction. And the axial direction one side end surface of the pump body 90 and the axial direction other side end surface of the pump cover 91 are joined, so that the inner rotor 18b and the outer rotor 18c are accommodated inside the pump body 90 and the pump cover 91.
  • a pump chamber 18a is formed. Specifically, the pump chamber 18 a is formed by the concave portion having the circular cross section provided in the pump body 90 and the other end surface in the axial direction of the pump cover 91.
  • the pump body 90 and the pump cover 91 are fastened and fixed to each other by a fastening bolt (not shown). Further, the pump case 91 is fixed to the case 2 by the pump cover 91 being fastened and fixed to the case 2 by the fastening bolts 81.
  • the oil pump 18 is an inscribed gear pump having an inner rotor 18b and an outer rotor 18c.
  • the inner rotor 18b and the outer rotor 18c are accommodated in the pump chamber 18a so as to be rotatable in an eccentric manner.
  • the inner rotor 18b is a pump gear arranged coaxially with the intermediate shaft M, and is drivingly connected so as to rotate integrally with a pump drive shaft 10 to be described later at a central portion in the radial direction.
  • the inner rotor 18b and the pump drive shaft 10 are drivingly connected.
  • the inner rotor 18b and the pump drive shaft 10 may be spline-connected.
  • the pump drive shaft 10 is provided integrally with a member (one-side radial extending portion 45) constituting the clutch case CH, and rotates integrally with the clutch case CH.
  • the oil pump 18 draws oil from the suction chamber 92 into the pump chamber 18a to generate hydraulic pressure, and discharges the oil into a discharge chamber (not shown).
  • the oil discharged into the discharge chamber is supplied to the clutch CL, the speed change mechanism TM, and the like. That is, the oil pump 18 generates hydraulic pressure for operating the clutch CL and the speed change mechanism TM.
  • oil passages are formed in the pump case 8 (pump body 90, pump cover 91), the intermediate shaft M, and the like, respectively, and the oil discharged by the oil pump 18 is supplied to a hydraulic control device (not shown) and It distributes through these oil passages and is supplied to each part to be supplied with oil.
  • the second support wall 7 extending in the radial direction and the circumferential direction, and the pump case 8 (the pump body 90, the pump cover extending in the radial direction and the circumferential direction) are also provided. 91), the space in the case 2 is partitioned in the axial direction. That is, the second support wall 7 and the pump case 8 cooperate to form a wall portion extending in the radial direction and the circumferential direction, and the space in the case 2 is partitioned in the axial direction by the wall portion.
  • the transmission mechanism TM is accommodated in the second chamber.
  • the first chamber Oil is basically prohibited from passing through the oil passage between the first chamber and the second chamber.
  • the pump case 8 (pump body 90) supports the clutch case CH via the first bearing 51.
  • the first bearing 51 is supplied with oil leaking from the pump chamber 18a to the other side in the axial direction through the space between the pump body 90 and the pump drive shaft 10.
  • the pump body 90 and the pump cover 91 are formed with a discharge oil passage 9 for discharging the oil that has lubricated the first bearing 51.
  • the amount of oil discharged from the oil pump 18 through a discharge chamber decreases according to the amount of oil leaking from the pump chamber 18a to the other side in the axial direction, oil leakage from the pump chamber 18a. It is desirable that the amount be limited to an amount that can adequately lubricate the first bearing 51.
  • 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 the other 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 the other axial side 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 one 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 the other side in the axial direction (damper D and internal combustion engine E side) between them.
  • a member 63 is provided.
  • a shaft end hole portion 12 extending in the axial direction is formed in the inner diameter portion of one end portion in the axial direction of the input shaft I.
  • the other end portion in the axial direction of the intermediate shaft M enters the shaft end hole portion 12 in the axial direction.
  • the input shaft I is integrally provided with a flange portion 11 extending radially from the main body portion (portion extending in the axial direction) of the input shaft I at one end portion in the axial direction thereof.
  • the flange portion 11 enters the clutch case CH and is connected to the clutch hub 21 of the clutch CL accommodated in the clutch case CH.
  • a fourth bearing 54 is disposed on the other axial side of the flange 11, and a third bearing is provided on the outer side in the radial direction of the flange 11 and on the one axial side of the clutch hub 21 of the clutch CL.
  • a bearing 53 is provided.
  • 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 transmission mechanism TM, and is splined to the clutch case CH. As shown in FIG. 2, the intermediate shaft M is disposed so as to penetrate the oil pump 18. As described above, an axial through hole is formed in the central portion of the pump case 8 in the radial direction, and the intermediate shaft M passes through the oil pump 18 through the through hole.
  • the intermediate shaft M is supported in the radial direction so as to be rotatable with respect to the oil pump 18.
  • the pump case 8 of the oil pump 18 rotatably supports the intermediate shaft M that is an input shaft (transmission input shaft) of the transmission mechanism TM.
  • 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 the other axial side 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 discharge oil passage 16 extends in the axial direction at a position different from the supply oil passage 15 in the axial direction on the other side in the axial direction of the intermediate shaft M, and opens to the end surface on the other side in the axial direction.
  • 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 that operates in a space to which oil is supplied. As shown in FIG. 2, the clutch CL includes a clutch hub 21 that is an input side member, a clutch drum 26 that is an output side member, a plurality of friction plates 31, and a piston 36.
  • the clutch hub 21 is formed in a cylindrical shape and holds a plurality of friction plates 31 from the radially inner side, and an annular plate shape extending radially inward from the other axial end of the cylindrical portion 22. Part 24.
  • the clutch hub 21 is connected to the flange portion 11 of the input shaft I so as to rotate integrally with the input shaft I, and is disposed radially inward with respect to the clutch drum 26.
  • the input shaft I is drivingly connected to the internal combustion engine E. Therefore, the clutch hub 21 is drivingly connected to the internal combustion engine E via the input shaft I.
  • the clutch drum 26 is formed in a cylindrical shape and holds a plurality of friction plates 31 from the outside in the radial direction.
  • the clutch drum 26 is connected so as to rotate integrally with the intermediate shaft M via the clutch case CH.
  • the intermediate shaft M is drivingly connected to the speed change mechanism TM. Therefore, the clutch drum 26 is drivingly connected to the speed change mechanism TM via the clutch case CH and the intermediate shaft M.
  • the intermediate shaft M drives and connects the clutch drum 26 and the speed change mechanism TM.
  • a plurality of friction plates 31 are slidably held in the axial direction on the clutch hub 21 and the clutch drum 26.
  • a backing plate 32 that functions as a pressing member when the friction plates 31 are engaged with each other is held on the other axial side of the plurality of friction plates 31.
  • the backing plate 32 is held in a state where movement in the axial direction is restricted by the snap ring 33.
  • the piston 36 is arranged on one axial side with respect to the plurality of friction plates 31 in a state where it is urged to one axial side by a return spring.
  • a fluid-tight hydraulic oil chamber 37 is formed between the clutch case CH integrated with the clutch drum 26 and the piston 36.
  • the hydraulic oil chamber 37 is an oil chamber for controlling the engagement state (complete engagement, complete release, or partial engagement therebetween) of the clutch CL.
  • 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 case CH. Supplied through the connecting oil passage 48.
  • the hydraulic pressure in the hydraulic oil chamber 37 increases and becomes larger than the urging force of the return spring, the piston 36 moves in the direction of expanding the volume of the hydraulic oil chamber 37 (in this example, the other side in the axial direction), and the backing plate 32.
  • a circulating oil chamber 38 is formed on the opposite side of the piston 36 from the hydraulic oil chamber 37.
  • the circulating oil chamber 38 is an oil chamber in which oil for mainly cooling the clutch CL circulates.
  • the pressure oil discharged by the oil pump 18 and adjusted to a predetermined hydraulic pressure by a hydraulic control device is continuously supplied to both the clutch case CH and the pump drive shaft 10 in the axial direction. It is supplied through the formed circulating oil passage 47. That is, the pump drive shaft 10 includes a circulating oil passage 47 that is an oil passage for supplying oil to the clutch CL.
  • the circulating oil passage 47 corresponds to the “supply oil passage” in the present invention.
  • the clutch case CH is a case that accommodates the clutch CL, and includes a pump drive shaft 10 that extends to one side in the axial direction and is drivingly connected to the inner rotor 18b.
  • the clutch case 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. That is, in the present embodiment, the clutch case CH is drivingly connected to the intermediate shaft M of the input shaft I and the intermediate shaft M.
  • the clutch case CH surrounds both the axial direction both sides and the radially outer side of the clutch CL on the radially outer side of the input shaft I and the intermediate shaft M arranged on the same axis and accommodates the clutch CL.
  • the clutch case CH is disposed on the other side in the axial direction of the clutch CL and extends in the radial direction on the other side, and the one side diameter is disposed on the one side in the axial direction of the clutch CL and extends in the radial direction.
  • a direction extending portion 45 and a cylindrical axial extending portion 49 that is disposed on the radially outer side of the clutch CL and extends in the axial direction are configured.
  • the axially extending portion 49 connects the one side radially extending portion 45 and the other side radially extending portion 41 in the axial direction at these radially outer ends.
  • the other-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.
  • the other-side radial extending portion 41 defines the other axial side of the circulating oil chamber 38.
  • An axial through hole is formed in the radial center of the other side radially extending portion 41, and the input shaft I inserted through this through hole penetrates the other side radially extending portion 41 to clutch. It is inserted in the case CH.
  • the other-side radial extending portion 41 is integrally provided with a cylindrical (boss-shaped) axial projecting portion 42 projecting toward the other axial end at the radially inner end thereof.
  • 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 portion excluding the axial protrusion 42 in the other-side radial extending portion 41 is a main body portion, in this example, the main body portion of the other-side radial extending portion 41 has a radially inner portion as a whole in the radial direction.
  • the member has a dish-like shape that is convex toward one side in the axial direction so as to be positioned on one side in the axial direction with respect to the outer portion.
  • the other-side radial extending portion 41 is adjacent to the first support wall 4 at a predetermined interval on one side in the axial direction, and the axial protrusion 42 is connected to the axial protrusion 5 of the first support wall 4. 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 41 is disposed adjacent to the clutch hub 21 and the flange portion 11 of the input shaft I at a predetermined interval on the other side in the axial direction.
  • the 2nd bearing 52 and the space between these are made into a liquid-tight state to the axial direction one side (rotary electrical machine MG side).
  • a second seal member 62 for suppressing oil leakage is disposed. That is, the second bearing 52 supports the other-side radial extending portion 41 constituting the clutch case CH so as to be rotatable relative to the case 2 that is a non-rotating member. As shown in FIG. 2, the second bearing 52 is disposed in a state of coming into contact with a stepped portion 42 a (a portion where the outer diameter changes) formed on the outer peripheral surface of the axial protruding portion 42 from the other side in the axial direction. Yes.
  • the second bearing 52 is a bearing (rolling bearing) including an outer ring, an inner ring, and rolling elements interposed between the outer ring and the inner ring.
  • the second bearing 52 is a ball bearing whose rolling element is a ball, and is configured to receive both a radial load and an axial load. That is, the hybrid drive device 1 according to the present embodiment includes the second bearing 52 that supports the clutch case CH in the radial direction and the axial direction with respect to the case 2 on the other axial side. As shown in FIG. 2, the second bearing 52 overlaps the other side radial extending portion 41 (specifically, the radially outer portion of the other side radial extending portion 41) in the axial direction. Has been placed.
  • the second bearing 52 is disposed so as to overlap with the other-side radially extending portion 41 (specifically, the radially outer portion of the other-side radially extending portion 41) when viewed from the radial direction. .
  • the second bearing 52 only needs to support at least the clutch case CH in the radial direction on the other side in the axial direction, and may be a bearing other than the ball bearing.
  • the second bearing 52 can be a roller bearing using a rolling element as a roller.
  • 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 axially extending portion 49 has a cylindrical shape that surrounds the radially outer side of the clutch CL.
  • the axially extending portion 49 extends from the radially outer end of the other radial extending portion 41 toward the one axial side. It is extended.
  • the axially extending portion 49 defines the radially outer side of the circulating oil chamber 38.
  • the axially extending portion 49 is formed integrally with the other side radially extending portion 41.
  • the axially extending portion 49 is disposed on the outer side in the radial direction of the clutch drum 26 with a predetermined gap between the axially extending portion 49 and the clutch drum 26. That is, the axially extending portion 49 is disposed so that the inner peripheral surface of the axially extending portion 49 and the outer peripheral surface of the clutch drum 26 are opposed to each other with a predetermined interval in the radial direction.
  • the axially extending portion 49 is formed in a stepped shape that gradually goes outward in the radial direction as it goes toward one side in the axial direction. And the outer peripheral surface of the part located in the axial direction other side in the axial direction extension part 49 is made into the 1st contact part 49a which contacts and supports the internal peripheral surface of rotor Ro of the rotary electric machine MG from radial inside. Yes. That is, in this example, the rotor Ro of the rotating electrical machine MG is supported by the clutch case CH.
  • the second contact where the inner peripheral surface of the axially extending portion 49 located on one side in the axial direction with respect to the first contact portion 49 a contacts the outer peripheral surface of the one-side radial extending portion 45.
  • a portion 49b is provided.
  • the second contact portion 49b is located on the radially outer side with respect to the first contact portion 49a.
  • the one-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 one side radially extending portion 45 is a radially inner portion of the piston 36 and a radially outer portion of the hydraulic oil chamber 37 and defines one axial side of the circulating oil chamber 38.
  • An axial through hole is formed in the radial center of the one side radially extending portion 45, and the intermediate shaft M inserted through the through hole penetrates the one side radially extending portion 45 to engage the clutch. It is inserted in the case CH.
  • the one-side radial extending portion 45 is integrally provided with a cylindrical (boss-shaped) axial projecting portion 46 projecting to one axial side at the radially inner end thereof.
  • the axial protruding portion 46 is formed so as to surround the periphery of the intermediate shaft M.
  • the radially extending portion 45 (axially projecting portion 46) is in contact with the outer peripheral surface of the intermediate shaft M over the entire circumferential direction at the radially inner end.
  • a portion excluding the axial protrusion 46 in the one-side radial extending portion 45 is a main body portion
  • the main body portion of the one-side radial extending portion 45 has a radially inner portion as a whole in the radial direction.
  • the radially inner portion is a plate-like member having a shape offset to the other axial side with respect to the radially outer portion so as to be positioned on the other axial side with respect to the outer portion.
  • the pump drive shaft 10 that extends to one side in the axial direction and is drivingly connected to the inner rotor 18b is provided at the radially inner end of the one side radially extending portion 45.
  • the pump drive shaft 10 is formed integrally with the one-side radial extending portion 45, specifically, the other end portion in the axial direction of the pump drive shaft 10.
  • one axial end of the axial protrusion 46 are integrally connected.
  • the pump drive shaft 10 is splined to rotate integrally with the intermediate shaft M.
  • the outer diameter of the axial protrusion 46 is larger than the outer diameter of the pump drive shaft 10.
  • an annular surface formed by one axial end surface of the axial projection 46 and an outer peripheral surface of the pump drive shaft 10 are formed at the connecting portion that is a boundary between the axial projection 46 and the pump drive shaft 10. are formed in a positional relationship orthogonal to each other, and the first bearing 51 described later can be appropriately fixed.
  • the one side radial extending portion 45 is adjacent to the second support wall 7 and the oil pump 18 (pump body 90) on the other side in the axial direction with a predetermined interval, and the axial protrusion 46 and the pump drive shaft. 10 is arranged in a state of being adjacent to the axial projecting portion 90b included in the pump body 90 at a predetermined interval radially inward. Further, the one-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 predetermined interval on one side in the axial direction at the radially inner portion. .
  • the 1st bearing 51 is arrange
  • a first seal member 61 is disposed to prevent the oil from leaking to the other side in the axial direction (rotating electrical machine MG side). That is, the pump drive shaft 10 is supported by the pump body 90 (pump case 8) via the first bearing 51. As described above, the pump case 8 is fixed to the case 2. Therefore, the pump drive shaft 10 is supported by the case 2 via the first bearing 51 and the pump case 8. As shown in FIG. 2, the first bearing 51 is disposed in a state in which the first bearing 51 is in contact with the end surface on one side in the axial direction of the axial protrusion 46 from the one side in the axial direction.
  • the pump drive shaft 10 is formed integrally with the one-side radial extending portion 45 constituting the clutch case CH, the one-side radial extending portion 45 is the first bearing.
  • the pump body 90 (pump case 8) is supported via 51. That is, the first bearing 51 can rotate the one side radial direction extending portion 45 constituting the clutch case CH relative to the pump case 8 which is a non-rotating member and the case 2 to which the pump case 8 is fixed. I support it.
  • the first bearing 51 is a bearing (rolling bearing) including an outer ring 51a, an inner ring 51b, and rolling elements 51c interposed between the outer ring 51a and the inner ring 51b (see FIG. 3). ).
  • the first bearing 51 is a ball bearing whose rolling elements are balls, and is configured to receive both a radial load and an axial load. That is, the hybrid drive device 1 according to the present embodiment includes the first bearing 51 that supports the clutch case CH in the radial direction and the axial direction with respect to the case 2 on one side in the axial direction.
  • the clutch case CH is supported by the first bearing 51 and the second bearing 52 in the radial direction and the axial direction with respect to the case 2 on both sides in the axial direction. And both the 1st bearing 51 and the 2nd bearing 52 are made into the rolling bearing (this example ball bearing) provided with the outer ring
  • the clutch case CH can be accurately supported in the radial direction, and the radial displacement of the outer peripheral surface of the pump drive shaft 10 provided in the clutch case CH is suppressed within a relatively narrow range. Is an easy configuration.
  • the outer ring 51a of the first bearing 51 is fitted to the inner peripheral surface of the axial projecting portion 90b (in this example, an interference fit by press-fitting) and is positioned and fixed in the radial direction.
  • the inner ring 51b It is fitted to the outer peripheral surface of the drive shaft 10 (in this example, it is an interference fit with a small interference or a clearance fit compared to the fitting of the outer ring 51a) and is positioned and fixed in the radial direction.
  • the first bearing 51 overlaps in the axial direction with the one side radially extending portion 45 (specifically, the radially outer portion of the one side radially extending portion 45). Has been placed.
  • the first bearing 51 is disposed so as to overlap with the one side radial extending portion 45 (specifically, the radially outer portion of the one side radial extending portion 45) when viewed from the radial direction.
  • the first bearing 51 may be any bearing that can support at least the clutch case CH in the radial direction on one axial side, and may be a rolling bearing other than a ball bearing.
  • the first bearing 51 can be a roller bearing using a rolling element as a roller.
  • the one side radially extending portion 45 is connected to a portion on the one axial side of the axial extending portion 49 in the vicinity of the radially outer end portion.
  • the one-side radial extending portion 45 is fitted to the second contact portion 49 b of the axial extending portion 49 (in this example, an interference fit by press fitting). In this state, they are joined by welding. That is, the one-side radial extending portion 45 and the axial extending portion 49 are joined and integrated by welding. In addition, welding is performed from one axial direction side with respect to the contact portion between the inner peripheral surface (second contact portion 49b) of the axially extending portion 49 and the outer peripheral surface of the one-side radial extending portion 45.
  • the welded joint portion 85 is formed around the same radial position as the second contact portion 49b.
  • the second contact portion 49b is positioned on the radially outer side with respect to the first contact portion 49a that contacts and supports the inner peripheral surface of the rotor Ro from the radially inner side. Therefore, the joining portion 85 is located on the radially outer side than the inner peripheral surface of the rotor Ro.
  • the joint part 85 by welding can be made into the position away from the pump drive shaft 10 in the radial direction, and the pump drive shaft 10 and the pump drive shaft 10 are provided at the radially inner end by heat during welding. It is suppressed that the formed one side radial direction extension part 45 deform
  • the radially outer portion of the one-side radially extending portion 45 and the axially one-side portion of the axially extending portion 49 face each other in the radial direction. And the surfaces facing each other in the axial direction are joined by welding in a state where both surfaces are in contact with each other. Thereby, it is suppressed that the heat at the time of welding is concentrated and transmitted only to any one member of the one side radial direction extension part 45 and the axial direction extension part 49, and the one side diameter direction It is suppressed that the temperature of the extension part 45 and the axial direction extension part 49 becomes excessive, and deform
  • the clutch drum 26 is integrally formed with the one side radially extending portion 45. More specifically, a cylindrical clutch drum extends in the vicinity of the radially outer end portion of the one side radial extension portion 45 from the one side radial extension portion 45 toward the other side in the axial direction. 26 is integrally formed.
  • a hydraulic oil chamber 37 is formed between the radially inner portion of the one-side radially extending portion 45 and the piston 36.
  • the one-side radial extending portion 45 as a whole is radially inclined while being slightly inclined toward the other side in the axial direction with respect to the radial direction so as to communicate the supply oil passage 15 and the hydraulic oil chamber 37.
  • a communication oil passage 48 is formed in the axial protrusion 46.
  • the space that occupies most of the space excluding the hydraulic oil chamber 37 is the circulating oil chamber 38 described above.
  • the oil that is discharged by the oil pump 18 and adjusted to a predetermined hydraulic pressure is a circulating oil passage 47 formed so as to extend in the axial direction in the pump drive shaft 10 and the axial protrusion 46.
  • the fifth bearing 55 disposed between the axial projecting portion 42 formed on the other radial extension portion 41 and the input shaft I can ensure a certain degree of liquid tightness.
  • the bearing with a sealing function is configured (here, a needle bearing with a seal ring).
  • the inner peripheral surface of the one-side radial extending portion 45 (axial protruding portion 46) is in contact with the outer peripheral surface of the intermediate shaft M over the entire circumferential direction at the radially inner end portion. 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 case CH is basically always filled with oil.
  • the oil basically circulates in the circulating oil chamber 38 while maintaining a state always filled with oil. This flow is indicated by broken-line arrows in FIG. That is, the oil supplied to the circulating oil chamber 38 from the circulating oil passage 47 first passes between the one-side radial extending portion 45 and the flange portion 11 and between the piston 36 and the clutch hub 21 in the radial direction. It flows toward the outside and cools the plurality of friction plates 31. Then, the oil that has cooled the plurality of friction plates 31 flows between the clutch hub 21 and the flange portion 11 and the other side radially extending portion 41 toward the radially inner side, and the base of the flange portion 11 Reach the end.
  • the oil is discharged from the circulating oil chamber 38.
  • 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 cylindrical portion 22 of the clutch hub 21 has a diameter in order to efficiently introduce oil supplied from the radially inner side into the gap between the friction plates 31.
  • a through hole 23 (a slit-like through hole in this example) penetrating in the direction is formed.
  • the clutch drum 26 is formed with a through hole 27 (a slit-like through hole in this example) that penetrates in the radial direction. Yes.
  • the oil supplied from the radially inner side is efficiently introduced into the gap between the friction plates 31, and the cooling efficiency of the plurality of friction plates 31 can be improved.
  • the oil may flow in the circumferential direction at the same time, but the main flow of the oil is 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 other end portion 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 other end surface and the surface defining the axial bottom 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 case CH and the first support wall 4. It is defined by a second seal member 62 disposed between the axial projection 5.
  • the rotating electrical machine MG is arranged coaxially with the intermediate shaft M on the radially outer side of the clutch case 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. That is, the rotating electrical machine includes the rotor Ro on the radially inner side with respect to 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 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 coaxially with the clutch case CH so as to overlap the clutch case CH in the axial direction. That is, the rotating electrical machine MG is disposed so as to overlap with the clutch case CH when viewed from the radial direction.
  • the rotor Ro of the rotating electrical machine MG is fixed to the outer peripheral portion of the axially extending portion 49 constituting the clutch case CH.
  • the rotor Ro of the rotating electrical machine MG is fixed to the first contact portion 49 a included in the axially extending portion 49.
  • the clutch case CH also functions as a rotor support member that supports the rotor Ro, and in this embodiment, the clutch case CH and the rotor support member are formed in common.
  • the clutch case CH is supported by the first bearing 51 and the second bearing 52 in the radial direction and the axial direction with respect to the case 2 on both sides in the axial direction.
  • both the first bearing 51 and the second bearing 52 are rolling bearings (in this example, ball bearings) each including an outer ring, an inner ring, and rolling elements.
  • rolling bearings in this example, ball bearings
  • the clutch drum 26 is thus integrally formed on the clutch case CH that rotates integrally with the rotor Ro of the rotating electrical machine MG. That is, the rotating electrical machine MG is drivingly connected to the clutch drum 26 that is an output side member of the clutch CL via the clutch case CH.
  • the damper D is disposed with a predetermined gap on the other axial side of the first support wall 4.
  • the damper D is in a space in which the first support wall 4 formed to have a dish-like shape that is convex toward one side in the axial direction is retracted to one side in the axial direction when viewed from the other side in the axial direction.
  • the damper D is further arranged in the radial direction inside of the coil end portion Ce on the other axial side (internal combustion engine E side) of the stator St of the rotating electrical machine MG, overlapping with the coil end portion Ce in the axial direction.
  • the damper D is disposed so as to overlap with the coil end portion Ce as viewed from the radial direction.
  • a resolver 19 (an example of a rotation sensor) that is a sensor for detecting the rotation angle (rotation phase) of the rotor Ro relative to the stator St of the rotating electrical machine MG is disposed in the case 2.
  • the resolver 19 is adjacent to both the second support wall 7 and the one-side radial extending portion 45 of the case 2 on one axial side of the clutch case CH. Has been placed.
  • the resolver 19 is an outer rotor type resolver provided with a sensor stator radially inward with respect to the sensor rotor.
  • the sensor stator of the resolver 19 is fixed to the cylindrical part 7a with which the 2nd support wall 7 is provided, and the sensor rotor of the resolver 19 is fixed to the internal peripheral surface of the axial direction one side edge part of the axial direction extension part 49. Yes.
  • the first bearing 51 that supports the clutch case CH in the radial direction (in this example, the radial direction and the axial direction) on one side in the axial direction includes the pump chamber 18a. Oil leaked to the other side in the axial direction passes between the pump body 90 and the pump drive shaft 10, but in the present invention, a dedicated member (such as a seal member) for limiting oil leakage is disposed. Without this, it is possible to limit the amount of oil leaking from the pump chamber 18a to the other axial side.
  • the oil leakage suppression structure from the pump chamber 18a according to the present embodiment will be described in detail with reference to FIG.
  • the pump case 8 (in this example, the pump body 90) includes a partition wall 90a that partitions the first bearing 51 and the inner rotor 18b. That is, the pump chamber 18a is partitioned on the other side in the axial direction by the partition wall 90a. Further, one axial side of the pump chamber 18a is partitioned by a partition wall 91a provided in the pump case 8 (in this example, the pump cover 91). The partition wall 91a is disposed on the side opposite to the partition wall 90a in the axial direction with respect to the inner rotor 18b.
  • the partition wall 90a includes a drive shaft insertion hole 90c through which the pump drive shaft 10 is inserted.
  • the diameter (diameter) of the inner peripheral surface of the drive shaft insertion hole 90c is “ ⁇ c”.
  • a gap between the outer peripheral surface of the pump drive shaft 10 and the inner peripheral surface of the drive shaft insertion hole 90 c is an oil flow passage L that flows from the pump chamber 18 a to the first bearing 51. That is, the flow path L is a flow path for oil that leaks from the pump chamber 18 a to the other axial side along the outer peripheral surface of the pump drive shaft 10.
  • the pump drive shaft 10 has one axial side to reduce the drag distance when the first bearing 51 is assembled to the pump drive shaft 10 from one axial direction.
  • the small diameter part 10a and the other axial side are formed in the step shape which becomes the large diameter part 10b.
  • the diameter (diameter) of the outer peripheral surface of the small diameter portion 10a is “ ⁇ a”
  • the diameter (diameter) of the outer peripheral surface of the large diameter portion 10b is “ ⁇ b”.
  • a key groove 10d that engages with a key 18d provided in the inner rotor 18b is formed at one end in the axial direction of the small diameter portion 10a.
  • the pump drive shaft 10 is arrange
  • the 1st bearing 51 is arrange
  • the axial widths of the inner rotor 18b and the outer rotor 18c are set slightly smaller than the axial width of the pump chamber 18a so that the inner rotor 18b and the outer rotor 18c can be rotated in the pump chamber 18a. Therefore, as shown in FIG. 3, there is a gap between the inner rotor 18b and the outer rotor 18c and the walls (partition wall 90a and partition wall 91a) that partition the pump chamber 18a. Therefore, not all of the oil whose pressure has been increased in the pump chamber 18a is discharged through the discharge chamber (not shown), but a part of the oil passes through this gap and becomes a lower pressure portion in the pump chamber 18a. Will flow. That is, the gap in the pump forms an oil passage in the pump chamber 18a.
  • the pump internal flow path formed by the gap between the partition wall 90a and the inner rotor 18b is referred to as a first pump internal flow path L1.
  • a flow path in the pump formed by a gap between the partition wall 91a and the inner rotor 18b is referred to as a second flow path L2 in the pump.
  • the first pump internal flow path L ⁇ b> 1 has an axial width of “ ⁇ ” and communicates with the flow path L at the radially inner end thereof.
  • the first pump internal flow path L1 also communicates with a space (hereinafter referred to as “target space”) formed radially inward with respect to the inner peripheral surface of the inner rotor 18b.
  • the first pump internal flow path L1 located near the discharge port (discharge chamber) (not shown), as shown in FIG. 3, the first pump internal flow path L1.
  • the flow path of the oil toward the flow path L through the target space is formed.
  • the first pump internal flow path L1 corresponds to the “pump internal flow path” in the present invention.
  • the second pump flow path L2 communicates with a space (a space indicated by a symbol L3 in FIG. 3) formed on one axial side of the pump drive shaft 10.
  • This space is formed in an annular shape and communicates with the circulation oil passage 47 as shown in FIG. That is, this space is a communication path L3 that communicates the second pump internal flow path L2 and the circulating oil path 47.
  • the second pump internal flow path L2 communicates with the circulating oil path 47 via the communication path L3.
  • the communication path L3 is a low-pressure space with respect to the second pump internal flow path L2 located near a discharge port (discharge chamber) (not shown), and therefore, as shown in FIG.
  • the circulating oil passage 47 is basically supplied with pressure oil discharged by the oil pump 18 and adjusted to a predetermined oil pressure by a hydraulic control device (not shown), but leaked from the pump chamber 18a. The oil is also supplied together.
  • the second pump internal flow path L2 corresponds to the “partition wall side pump internal flow path” in the present invention.
  • the axial widths of the first pump internal flow path L1 and the second pump internal flow path L2 change according to the axial position of the inner rotor 18b in the pump chamber 18a.
  • the inner rotor 18b may be positioned outside the axial direction with respect to the axial center position of the pump chamber 18a, but in a steady state, Located near the axial center position. Therefore, the axial width of the second pump internal flow path L2 is the same as or close to the axial width ⁇ of the first pump internal flow path L1.
  • the flow path diameter difference is set.
  • the small diameter portion 10a of the pump drive shaft 10 faces the inner peripheral surface of the drive shaft insertion hole 90c
  • the outer peripheral surface of the pump drive shaft 10 in the flow path L is the outer periphery of the small diameter portion 10a. It becomes a surface. Therefore, in this example, the flow path diameter difference is “ ⁇ c ⁇ a”.
  • the difference between the diameter of the large-diameter portion 10b and the diameter of the small-diameter portion 10a of the pump drive shaft 10 is set as a pump shaft step width, and the flow passage diameter difference is set to a value smaller than the pump shaft step width.
  • the flow passage diameter difference can be set to a value that is 1/2 or 1/4 of the pump shaft step width. Since the pump shaft step width is expressed as “ ⁇ b ⁇ a”, “ ⁇ c ⁇ a” (flow path diameter difference) is smaller than “ ⁇ b ⁇ a” (pump shaft step width). That is, the flow path diameter difference is set so that the relationship “ ⁇ b> ⁇ c> ⁇ a” is satisfied.
  • the flow path diameter difference is set so that the flow path cross-sectional area of the flow path L is smaller than the flow path cross-sectional area of the first pump internal flow path L1.
  • the flow path cross-sectional area of the flow path L can be set to a value that is 1/2 or 1/4 of the flow path cross-sectional area of the first pump internal flow path L1.
  • the flow path cross-sectional area of the first pump internal flow path L1 is The area of the cylindrical surface having the diameter “ ⁇ d” and the axial width “ ⁇ ” can be simplified as “ ⁇ ⁇ ⁇ d ⁇ ⁇ ”. Further, the cross-sectional area of the flow path L is the axial cross-sectional area “ ⁇ ⁇ ⁇ c ⁇ ⁇ c / 4 ⁇ ⁇ ⁇ a ⁇ ⁇ a / 4” of a cylinder having an inner diameter “ ⁇ a” and an outer diameter “ ⁇ c”. "Can be simplified.
  • the flow path diameter difference is set so that “ ⁇ ⁇ ⁇ c ⁇ ⁇ c / 4 ⁇ ⁇ ⁇ a ⁇ ⁇ a / 4” is smaller than “ ⁇ ⁇ ⁇ d ⁇ ⁇ ”.
  • the flow path L functions appropriately as a constricted portion, and is not discharged from the discharge chamber. Only a part of the oil flowing through the first pump flow path L1 can be guided into the flow path L.
  • the amount of oil leaking in the axial direction from the pump chamber 18a along the outer peripheral surface of the pump drive shaft 10 can be limited, and the amount of oil discharged from the pump chamber 18a through a discharge chamber (not shown) is appropriately set. It is possible to secure it.
  • the second pump internal flow path L2 is formed on the opposite side of the first pump internal flow path L1 in the axial direction with respect to the inner rotor 18b.
  • the first pump inner flow path L1 and the second pump inner flow path L2 communicate with each other via a gap between the outer teeth of the inner rotor 18b and the inner teeth of the outer rotor 18c.
  • the target space and the communication path L3 communicate with each other via a gap between the inner rotor 18b and the pump drive shaft 10 (such as a gap between the key 18d and the key groove 10d).
  • the oil that has not been discharged to the flow passage L when the flow passage L functions as a throttle portion flows to the communication passage L3 via the second pump internal flow passage L2 and the gap, and is supplied to the circulation oil passage 47.
  • the thereby, the structure in which the flow passage L functions as a constriction part, and the oil that has not been discharged to the flow passage L can be actively guided to the circulation oil passage 47 for supplying oil to the clutch CL. It has become.
  • the flow path diameter difference ( ⁇ c ⁇ a) is set to be larger than the maximum value of the amount by which the pump drive shaft 10 supported by the first bearing 51 can be displaced in the radial direction.
  • the flow path diameter difference can be set to a value that is substantially the same as the maximum value, or can be set to a value that is twice the maximum value.
  • the displacement amount (runout amount) in the radial direction of the pump drive shaft 10 is at least fixed between the large-diameter portion 10b of the pump drive shaft 10 and the axial protruding portion 90b of the pump body 90.
  • the radial clearance of the first bearing 51 is the amount of relative displacement in the radial direction between the outer ring 51a and the inner ring 51b that is allowed by the clearance existing inside the first bearing 51.
  • the amount of displacement in the radial direction of the pump drive shaft 10 also depends on the amount by which the first bearing 51 itself can be displaced in the radial direction. For example, a gap between the outer peripheral surface of the outer ring 51a of the first bearing 51 and the inner peripheral surface of the axial protrusion 90b that fits and supports the outer ring 51a, or the inner peripheral surface of the inner ring 51b of the first bearing 51
  • the first bearing 51 itself can be displaced in the radial direction by a gap between the inner ring 51b and the outer peripheral surface of the large-diameter portion 10b that fits and supports the inner ring 51b.
  • the degree of each factor that causes the radial displacement of the pump drive shaft 10 is determined according to the dimensional tolerance of each member, the tolerance of the mounting position, and the like.
  • the clutch case CH is supported by the first bearing 51 and the second bearing 52 in the radial direction and the axial direction with respect to the case 2 on both sides in the axial direction. And both the 1st bearing 51 and the 2nd bearing 52 are made into the rolling bearing (this example ball bearing) provided with the outer ring
  • the flow path diameter difference is set to a small value that allows the flow path L to function properly as a throttle portion while suppressing contact between the outer peripheral surface of the pump drive shaft 10 and the inner peripheral surface of the drive shaft insertion hole 90c. Is an easy configuration.
  • the flow passage diameter difference is set to a value smaller than the pump shaft step width, and the flow passage cross-sectional area of the flow passage L is the flow passage cross-sectional area of the first pump internal flow passage L1.
  • the embodiment of the present invention is not limited to this, and the flow path diameter difference can be changed as appropriate according to the amount of oil required for the first bearing 51 to lubricate.
  • the flow path diameter difference is set to a value smaller than the pump shaft step width, and the flow path diameter difference is set so that the flow path cross-sectional area of the flow path L is larger than the flow path cross-sectional area of the first pump internal flow path L1. be able to.
  • the flow passage diameter difference is set to a value larger than the pump shaft step width, and the flow passage diameter difference is set so that the flow passage cross-sectional area of the flow passage L is smaller than the flow passage cross-sectional area of the first pump internal flow passage L1. You can also. Further, the flow passage diameter difference is set to a value larger than the pump shaft step width, and the flow passage diameter difference is set so that the flow passage cross-sectional area of the flow passage L is larger than the flow passage cross-sectional area of the first pump internal flow passage L1. It is also possible.
  • the flow passage diameter difference is set to be larger than the maximum value of the amount that the pump drive shaft 10 supported by the first bearing 51 can be displaced in the radial direction.
  • the embodiment of the present invention is not limited to this, and the flow path diameter difference depends on the amount of oil required for lubrication of the first bearing 51 and the pump drive shaft 10 in the usage state of the hybrid drive device 1. Depending on the tendency of the radial direction position, etc., it can be appropriately changed.
  • the flow path diameter difference can be set smaller than the maximum value of the amount by which the pump drive shaft 10 supported by the first bearing 51 can be displaced in the radial direction.
  • the flow path diameter difference can be set to a value that is 1/2 or 1/4 of the maximum value of the amount that the pump drive shaft 10 supported by the first bearing 51 can be displaced in the radial direction.
  • the pump drive shaft 10 has been described as an example in which the pump drive shaft 10 is formed in a stepped shape having the small diameter portion 10a on one side in the axial direction and the large diameter portion 10b on the other side in the axial direction.
  • the embodiment of the present invention is not limited to this, and the pump drive shaft 10 may be configured such that the outer diameter is uniformly formed in the axial direction.
  • the portion of the pump drive shaft 10 that contacts the first bearing 51 from the radially inner side and the portion that defines the radially inner side of the flow passage L in the pump drive shaft 10 are located at the same radial position. Will do.
  • the circulating oil chamber 38 which occupies most of the space formed inside the clutch case CH, excluding the hydraulic oil chamber 37, is basically always filled with oil.
  • the case where the state has been achieved has been described as an example.
  • the embodiment of the present invention is not limited to this, and the space excluding the hydraulic oil chamber 37 in the clutch case CH is configured as a space that is supplied with oil but not necessarily filled with oil. This is also one of the preferred embodiments of the present invention.
  • the space excluding the hydraulic oil chamber 37 in the clutch case CH is not necessarily partitioned in an oil-tight manner.
  • the case where the second pump flow path L2 communicates with the circulating oil path 47 has been described as an example.
  • the embodiment of the present invention is not limited to this, and the configuration in which the second pump internal flow path L2 communicates with an oil path other than the circulation oil path 47, or the second pump internal flow path L2 is the circulation oil path. It is also possible to adopt a configuration that does not communicate with 47 and is sealed or drained.
  • the embodiment of the present invention is not limited to this, and the joining portion 85 may be configured to be located radially inward from the inner peripheral surface of the rotor Ro.
  • the one side radial direction extension part 45 and the axial direction extension part 49 demonstrated as an example the case where they were joined and integrated by welding, one side radial direction extension was demonstrated.
  • the portion 45 and the axially extending portion 49 may be integrated by a fixing method other than welding (fastening and fixing by a fastening member, fixing by a caulking structure, or the like).
  • the oil pump 18 is an inscribed gear pump
  • the embodiment of the present invention is not limited to this, and the oil pump 18 may be an oil pump having a configuration other than an inscribed gear pump such as an outer gear pump or a vane pump.
  • the rotor can be configured so as to be coaxial with the intermediate shaft M in the pump chamber of the oil pump, and the rotor is the “pump rotor” in the present invention.
  • the present invention includes a first shaft that is drivingly connected to the internal combustion engine, a second shaft that is drivingly connected to the speed change mechanism, a clutch that selectively drives and connects the first shaft and the second shaft, a rotating electrical machine, It can utilize suitably for the hybrid drive device provided with the case which accommodates a clutch and a rotary electric machine.

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Abstract

La présente invention se rapporte à un dispositif d'entraînement hybride qui est pourvu d'un premier palier (51) pour supporter un carter d'embrayage dans une direction radiale sur un côté dans une direction axiale, et d'un second palier pour supporter le carter d'embrayage dans une direction radiale sur l'autre côté dans la direction axiale. Un rotor d'une machine électrique rotative est supporté par le carter d'embrayage. Le premier palier (51) est pourvu d'un chemin de roulement externe (51a), d'un chemin de roulement interne (51b) et d'éléments de roulement (51c) intercalés entre le chemin de roulement externe (51a) et le chemin de roulement interne (51b). Un espace entre une face périphérique externe d'un arbre d'entraînement de pompe (10) et une face périphérique interne d'un trou traversant d'arbre d'entraînement (90c) fait office de canal d'écoulement (L) pour que l'huile s'écoule depuis une chambre de pompage (18a) vers le premier palier (51). Une différence de diamètre de canal d'écoulement qui représente la différence entre le diamètre (φa) de la face périphérique externe de l'arbre d'entraînement de pompe (10) et le diamètre (φc) de la face périphérique interne du trou traversant d'arbre d'entraînement (90c) dans le canal d'écoulement (L) est déterminée de telle sorte que le canal d'écoulement (L) serve de section d'étranglement pour limiter le débit de l'huile.
PCT/JP2011/067707 2010-08-06 2011-08-02 Dispositif d'entraînement hybride Ceased WO2012018027A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2010-177818 2010-08-06
JP2010-177817 2010-08-06
JP2010177818A JP5278774B2 (ja) 2010-08-06 2010-08-06 車両用駆動装置
JP2010177817A JP5471955B2 (ja) 2010-08-06 2010-08-06 回転電機及び車両用駆動装置

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WO2012018027A1 true WO2012018027A1 (fr) 2012-02-09

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JP2013248913A (ja) * 2012-05-30 2013-12-12 Aisin Seiki Co Ltd ハイブリッド車両用駆動装置
WO2013187837A3 (fr) * 2012-06-12 2014-02-20 Husqvarna Ab Système de coupe électrique
CN107407397A (zh) * 2015-06-08 2017-11-28 株式会社小松制作所 动力传递装置及具备动力传递装置的作业车辆
CN115217935A (zh) * 2021-04-28 2022-10-21 广州汽车集团股份有限公司 一种机电耦合变速器组件及具有其的车辆

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JP2009001127A (ja) * 2007-06-20 2009-01-08 Toyota Motor Corp ハイブリッド駆動装置
JP2009208702A (ja) * 2008-03-06 2009-09-17 Nissan Motor Co Ltd ハイブリッド駆動装置
JP2010105450A (ja) * 2008-10-28 2010-05-13 Aisin Aw Co Ltd 車両用駆動装置

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JP2009001127A (ja) * 2007-06-20 2009-01-08 Toyota Motor Corp ハイブリッド駆動装置
JP2009208702A (ja) * 2008-03-06 2009-09-17 Nissan Motor Co Ltd ハイブリッド駆動装置
JP2010105450A (ja) * 2008-10-28 2010-05-13 Aisin Aw Co Ltd 車両用駆動装置

Cited By (7)

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Publication number Priority date Publication date Assignee Title
JP2013248913A (ja) * 2012-05-30 2013-12-12 Aisin Seiki Co Ltd ハイブリッド車両用駆動装置
WO2013187837A3 (fr) * 2012-06-12 2014-02-20 Husqvarna Ab Système de coupe électrique
US9656336B2 (en) 2012-06-12 2017-05-23 Husqvarna Ab Electric cutting system
US10486250B2 (en) 2012-06-12 2019-11-26 Husqvarna Ab Electric cutting system
CN107407397A (zh) * 2015-06-08 2017-11-28 株式会社小松制作所 动力传递装置及具备动力传递装置的作业车辆
EP3258135A4 (fr) * 2015-06-08 2019-02-27 Komatsu Ltd. Dispositif de transmission de puissance et véhicule de travail avec un dispositif de transmission de puissance
CN115217935A (zh) * 2021-04-28 2022-10-21 广州汽车集团股份有限公司 一种机电耦合变速器组件及具有其的车辆

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