WO2017217067A1 - トランスアクスル装置 - Google Patents
トランスアクスル装置 Download PDFInfo
- Publication number
- WO2017217067A1 WO2017217067A1 PCT/JP2017/012274 JP2017012274W WO2017217067A1 WO 2017217067 A1 WO2017217067 A1 WO 2017217067A1 JP 2017012274 W JP2017012274 W JP 2017012274W WO 2017217067 A1 WO2017217067 A1 WO 2017217067A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- gear
- shaft
- electrical machine
- rotating electrical
- transaxle
- Prior art date
Links
- 230000007246 mechanism Effects 0.000 claims abstract description 110
- 230000005540 biological transmission Effects 0.000 claims abstract description 69
- 230000004048 modification Effects 0.000 description 114
- 238000012986 modification Methods 0.000 description 114
- 239000003921 oil Substances 0.000 description 28
- 230000000694 effects Effects 0.000 description 14
- 230000006870 function Effects 0.000 description 14
- 230000007935 neutral effect Effects 0.000 description 9
- 230000001276 controlling effect Effects 0.000 description 4
- 238000010248 power generation Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 230000001172 regenerating effect Effects 0.000 description 3
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 230000006872 improvement Effects 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 230000003313 weakening effect Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 230000007659 motor function Effects 0.000 description 1
- 230000008929 regeneration Effects 0.000 description 1
- 238000011069 regeneration method Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
- 238000004904 shortening Methods 0.000 description 1
- 239000007858 starting material Substances 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/50—Architecture of the driveline characterised by arrangement or kind of transmission units
- B60K6/54—Transmission for changing ratio
- B60K6/547—Transmission for changing ratio the transmission being a stepped gearing
-
- 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
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/02—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of clutch
-
- 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
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
- B60K6/36—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
- B60K6/38—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the driveline clutches
- B60K6/387—Actuated clutches, i.e. clutches engaged or disengaged by electric, hydraulic or mechanical actuating means
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
- B60K6/40—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the assembly or relative disposition of components
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
- B60K6/40—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the assembly or relative disposition of components
- B60K6/405—Housings
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
- B60K6/44—Series-parallel type
- B60K6/442—Series-parallel switching type
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
- B60L50/00—Electric propulsion with power supplied within the vehicle
- B60L50/10—Electric propulsion with power supplied within the vehicle using propulsion power supplied by engine-driven generators, e.g. generators driven by combustion engines
- B60L50/16—Electric propulsion with power supplied within the vehicle using propulsion power supplied by engine-driven generators, e.g. generators driven by combustion engines with provision for separate direct mechanical propulsion
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- 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
- B60W30/00—Purposes of road vehicle drive control systems not related to the control of a particular sub-unit, e.g. of systems using conjoint control of vehicle sub-units
- B60W30/18—Propelling the vehicle
- B60W30/188—Controlling power parameters of the driveline, e.g. determining the required power
-
- 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
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/089—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears all of the meshing gears being supported by a pair of parallel shafts, one being the input shaft and the other the output shaft, there being no countershaft involved
-
- 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
- B60W2710/00—Output or target parameters relating to a particular sub-units
- B60W2710/02—Clutches
- B60W2710/021—Clutch engagement state
- B60W2710/022—Clutch actuator position
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
- B60Y2200/00—Type of vehicle
- B60Y2200/90—Vehicles comprising electric prime movers
- B60Y2200/92—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
- Y02T10/62—Hybrid vehicles
Definitions
- the present invention relates to a transaxle device used in a hybrid vehicle equipped with an engine and two rotating electric machines.
- the driving mode includes EV mode in which only the motor is driven using the battery charging power, series mode in which the generator is driven by the engine and only the motor is driven while generating power, and parallel driving in which the engine and the motor are used in combination. Mode etc. are included.
- Switching of the running mode is performed by controlling a mechanism such as a sleeve or a clutch interposed on a power transmission path in the transaxle device. This mechanism is disposed, for example, on an axis in a power transmission path between the engine and the generator or on an axis in a power transmission path between the engine and the drive wheels (see Patent Documents 1 and 2).
- a power transmission path from the engine to the drive wheels and a power transmission path from the motor to the drive wheels are provided separately.
- a traveling mode parallel mode
- the motor rotates with the drive wheels while the vehicle is running only with the engine. If the induced voltage generated by the rotation of the motor at this time exceeds the voltage of the driving battery, a regenerative brake is applied to the vehicle, which may give the driver a feeling of strangeness. Therefore, conventionally, field weakening control is performed to prevent unintended regenerative braking during high-speed driving.
- the present case has been devised in view of such problems, and an object thereof is to provide a transaxle device that can improve power consumption.
- the present invention is not limited to this purpose, and is a function and effect derived from each configuration shown in the embodiment for carrying out the invention described later, and has another function and effect that cannot be obtained by conventional techniques. is there.
- a transaxle device disclosed herein includes an engine, a first rotating electrical machine, and a second rotating electrical machine, and individually supplies the power of the engine and the first rotating electrical machine to an output shaft on a drive wheel side.
- a transaxle device for a hybrid vehicle that transmits the power of the engine to the second rotating electrical machine as well as being transmitted on a power transmission path from the first rotating electrical machine to the output shaft,
- a connection / disconnection mechanism for connecting / disconnecting power transmission of the first rotating electrical machine is provided.
- the first rotating electric machine means a motor generator (motor generator) or an electric motor having a rotating armature or field and at least an electric function.
- the second rotating electric machine means a motor generator (motor generator) or a generator having a rotating armature or a magnetic field and having at least a power generation function.
- the first rotating electrical machine shaft On the power transmission path from the first rotating electrical machine to the output shaft, the first rotating electrical machine shaft connected coaxially with the rotating shaft of the first rotating electrical machine, and the first It is preferable that a counter shaft positioned between the rotating electrical machine shaft and the output shaft is provided, and the connection / disconnection mechanism is interposed in the counter shaft.
- the fixed gear on the first rotating electrical machine shaft and the idle gear on the counter shaft are always meshed, and the number of teeth of the idle gear is greater than the number of teeth of the fixed gear. It is also preferable that there are many.
- the first rotating electrical machine shaft connected coaxially with the rotating shaft of the first rotating electrical machine, and It is preferable that a counter shaft positioned between the first rotating electrical machine shaft and the output shaft is provided, and the connection / disconnection mechanism is interposed in the first rotating electrical machine shaft.
- a differential gear interposed in the output shaft is provided, and the connection / disconnection mechanism is interposed in a position overlapping the differential gear in a direction orthogonal to the axial direction of the output shaft. Is preferred.
- the connecting / disconnecting mechanism for connecting / disconnecting the power of the first rotating electrical machine Since the connecting / disconnecting mechanism for connecting / disconnecting the power of the first rotating electrical machine is provided, it is possible to prevent the drive wheel from being rotated when the first rotating electrical machine is off. For this reason, the field-weakening control that has been conventionally performed becomes unnecessary, and the electric power consumed by the field-weakening control can be used for traveling. In other words, by providing a connection / disconnection mechanism, power consumption can be improved.
- transaxle device as an embodiment will be described with reference to the drawings.
- Each embodiment shown below is only an example, and there is no intention of excluding various modifications and application of technology that are not clearly shown in each of the following embodiments.
- Each configuration of the present embodiment can be implemented with various modifications without departing from the spirit thereof. Further, they can be selected as necessary, or can be appropriately combined.
- the transaxle 1 (transaxle device) of the present embodiment is applied to the vehicle 10 shown in FIG.
- This vehicle 10 is a hybrid vehicle equipped with an engine 2, a traveling motor 3 (electric motor, first rotating electrical machine), and a generator 4 for power generation (generator, second rotating electrical machine).
- the generator 4 is connected to the engine 2 and can be operated independently of the operating state of the motor 3.
- the vehicle 10 is prepared with three types of travel modes, EV mode, series mode, and parallel mode. These travel modes are alternatively selected by an electronic control unit (not shown) according to the vehicle state, the travel state, the driver's request output, etc., and the engine 2, motor 3 and generator 4 are used properly according to the type. It is done.
- the motor 3 may have a power generation function (generator function), and the generator 4 may have an electric function (motor function).
- Engine 2 is an internal combustion engine (gasoline engine, diesel engine) that burns gasoline or light oil.
- the engine 2 is a so-called horizontal engine that is disposed sideways so that the direction of the crankshaft 2 a (rotating shaft) coincides with the vehicle width direction of the vehicle 10, and is fixed to the right side surface of the transaxle 1. .
- the crankshaft 2 a is disposed in parallel to the drive shaft 9 of the drive wheel 8.
- the operating state of the engine 2 is controlled by an electronic control unit.
- the casing 1C when the casing 1C is provided so that the casing side surface 1b in which the opening of the output shaft 12 is formed is positioned on the radially outer side between the large-diameter idle gear 15L and the small-diameter idle gear 15H. Since the cylindrical portion 1a is positioned on the left side in FIG. 3 with respect to the large-diameter idle gear 15L, the cylindrical portion 1a can be made smaller overall. With such a configuration, a space for connecting the drive shaft 9 is secured on the extended line of the output shaft 12 outside the casing 1C.
- the low-side fixed gear 11L is always meshed with a fixed gear 14a provided on the generator shaft 14. That is, the input shaft 11 and the generator shaft 14 are connected via the two fixed gears 11L and 14a, so that power can be transmitted between the engine 2 and the generator 4.
- the idle gear 15H has a tooth surface portion that meshes with the fixed gear 11H on the left side, and has a dog gear 15d coupled to a contact portion protruding on the right side of the tooth surface portion.
- the idle gear 15 ⁇ / b> L has a tooth surface portion that meshes with the fixed gear 11 ⁇ / b> L on the right side, and has a dog gear 15 e that is coupled to a contact portion that protrudes on the left side of the tooth surface portion.
- Dog teeth (not shown) are provided at the distal end portions (radially outer end portions) of the dog gears 15d and 15e.
- the second counter shaft 16 is provided with two fixed gears 16a and 16b.
- the fixed gear 16a closer to the right side surface has a tooth surface portion that always meshes with an idler gear 13b provided on the motor shaft 13, and a parking gear 19 is integrated on the right side of the tooth surface portion.
- the idle gear 13b has a smaller diameter than the fixed gear 16a. That is, the number of teeth of the idle gear 13b is smaller than the number of teeth of the fixed gear 16a.
- the fixed gear 16b closer to the left side always meshes with the ring gear 18a of the differential 18.
- a pressure regulator comprising a plurality of solenoid valves (on / off solenoid valves, linear solenoid valves, etc.) is provided on the hydraulic circuit, and the clutch 21 is disconnected by regulating the oil pumped from the pump 5 to an appropriate hydraulic pressure.
- a configuration in which contact is controlled may be employed.
- an electric coupling instead of the pump 5 and the multi-plate clutch 21, an electric coupling may be provided, and the transmission of power may be controlled to be connected / disconnected by the electronic control unit. That is, the connection / disconnection mechanism 20 may have an electric control coupling and an idler gear 13b.
- the parking gear 19 is an element constituting a parking lock device.
- the parking gear 19 is engaged with a parking sprag (not shown) to rotate the second counter shaft 16 (that is, the output shaft 12).
- Ban As shown in FIG. 3, the differential 18 transmits the power transmitted to the ring gear 18a to the output shaft 12 via the differential case 18b, the pinion shaft 18c, the differential pinion 18d, and the side gear 18e.
- the motor shaft 13 is provided only with a gear (gear corresponding to the idle gear 13b) for transmitting the power of the motor 3, and the space around the motor shaft 13 becomes a dead space. It was.
- the connecting / disconnecting mechanism 20 is interposed in the motor shaft 13, it becomes possible to use a dead space and improve the space efficiency in the casing 1C. it can.
- connection / disconnection mechanism 20 since the connection / disconnection mechanism 20 is interposed at a position overlapping the differential 18 in the width direction, no dead space is created around the motor shaft 13. That is, the space around the motor shaft 13 (the space that has conventionally been a dead space) can be effectively used, and the space efficiency can be further improved. Thereby, the connection / disconnection mechanism 20 can be provided without enlarging the axial dimension of the transaxle 1. (4) Further, in the transaxle 1 described above, since the connecting / disconnecting mechanism 20 includes the idler gear 13b and the clutch 21, the power transmission of the motor 3 can be easily performed only by controlling the connecting / disconnecting of the clutch 21. Can be connected or disconnected.
- the switching mechanism 30 is provided on the power transmission path (second path 52) from the engine 2 to the output shaft 12, and when traveling in the parallel mode, the travel state, the required output, etc. Accordingly, the high gear stage and the low gear stage are switched. In other words, in the parallel mode, the power of the engine 2 can be switched (transmitted) in two stages, so that the driving pattern can be increased, and effects such as improved drive feeling and improved fuel efficiency can be obtained. Can be improved.
- the switching mechanism 30 described above switches the high-side idle gear 15H and the low-side idle gear 15L by the sleeve 32, there is no restriction on the gear ratio. That is, each gear ratio of the high gear stage and the low gear stage can be set freely. Furthermore, in the vehicle 10 described above, the power of the engine 2 and the motor 3 can be output individually, so that torque loss during high / low switching can be covered by the power of the motor 3. As a result, the shift shock can be suppressed, and the necessity of quickly switching between high and low is reduced, so that the configuration of the switching mechanism 30 can be simplified.
- the high gear stage (fixed gear 11H, idle gear 15H) is different from the low gear stage (fixed gear 11L, idle gear 15L).
- a large-diameter gear (idling gear 15L) is disposed on the side close to the differential 18 and a small-diameter gear is located away from the differential 18. Since (the idle gear 15H) is arranged, the diameter of the portion of the casing 1C along the first counter shaft 15 is reduced toward the outside (in the direction away from the differential 18), for example, or reduced overall. be able to. Thereby, the space for connecting the drive shaft 9 can be ensured on the extension line of the output shaft 12 outside the casing 1C while avoiding the enlargement of the casing 1C.
- the inverter on the generator 4 side is controlled so that the rotational speed of the input shaft 11 matches the rotational speed on the drive wheel 8 side. Smooth engagement between the sleeve 32 and any one of the idle gears 15H and 15L (ie, selection of the high gear stage or the low gear stage or switching between the high gear stage and the low gear stage) can be performed smoothly. it can.
- FIGS. 5 to 14 are skeleton diagrams showing a powertrain 7 including the transaxle 1 according to first to tenth modifications.
- symbol (different alphabet etc. to the same number) is attached
- the overlapping description is omitted.
- the transaxle 1 according to the first modification has a configuration in which the input shaft 11 and the generator shaft 14 are connected, and a connection / disconnection mechanism 20 ′ is disposed on the second counter shaft 16. Except for, the configuration is the same as in the above-described embodiment.
- a fixed gear 11a that is always meshed with the fixed gear 14a of the generator 14 is provided on the input shaft 11, and between the engine 2 and the generator 4 by these fixed gears 11a and 14a. Power transmission is possible.
- the fixed gear 11L described above is always meshed only with the idle gear 15L of the first countershaft 15.
- connection / disconnection mechanism 20 ′ of the present modification includes a free-wheeling gear 16 c provided on the second counter shaft 16 and a clutch 21 ′ interposed on the second counter shaft 16.
- the idle gear 16c has a larger diameter than the fixed gear 13a provided on the motor shaft 13 (that is, has a larger number of teeth), and always meshes with the fixed gear 13a.
- the clutch 21 ′ is a multi-plate clutch that controls the power connection / disconnection state of the motor 3, as in the above-described embodiment, and includes a first engagement element 22 ′ fixed to the second counter shaft 16 and an idle rotation. And a second engagement element 23 'fixed to the gear 16c.
- the second counter shaft 16 rotates in conjunction with the rotation of the output shaft 12, according to the transaxle 1 of the present modified example in which the connection / disconnection mechanism 20 ′ is interposed in the second counter shaft 16, Oil can be easily supplied from the end of the two counter shaft 16 (oil passage inlet 5c) to the inside of the second counter shaft 16 (the idle gear 16c on the second counter shaft 16).
- the idler gear 16c having a larger number of teeth (larger diameter) than the fixed gear 13a is provided on the second countershaft 16, so that a smaller-diameter idler gear is disposed on the motor shaft 13.
- the rotation speed of the idle gear 16c can be made low.
- the needle bearing of the idle gear 16c can be used within the allowable rotational speed.
- the transaxle 1 according to the present modification can improve the power consumption as in the above-described embodiment. Furthermore, the same effect can be obtained from the same configuration as the above-described embodiment.
- the input shaft 11 of this modification is provided with a fixed gear 11L that transmits power to the output shaft 12 side and a fixed gear 11a that transmits power to the generator 4 separately from the input shaft 11, so that the axial direction It is possible to easily design each gear ratio to a desired value while shortening the dimension in the direction orthogonal to (the gear radial direction).
- the transaxle 1 according to the second modified example is the first modified example (FIG. 5) except that the positional relationship between the high gear stage and the low gear stage and the configuration of the switching mechanism 30 ′ are different. ).
- the high gear stage (fixed gear 11H, fixed gear 15H ') is arranged on the right side (difference 18 side) in the casing 1C, and the low gear stage (fixed gear 11L, idle gear 15L) is on the left side in the casing 1C. Placed in.
- the fixed gear 15H ′ provided on the first counter shaft 15 is always meshed with the fixed gear 11H of the input shaft 11 to form a high gear stage.
- the input shaft 11 of this modification is provided with a fixed gear 11a similar to that of the first modification between the two fixed gears 11L and 11H.
- the first counter shaft 15 is provided with a high-side fixed gear 15H ′, an output idle gear 15b, a low-side idle gear 15L, and a switching mechanism 30 ′ in order from the right side.
- the switching mechanism 30 ′ is provided so as to be rotatable relative to the first counter shaft 15, and is not rotatable relative to the hub 31 ′, and slides in the axial direction of the first counter shaft 15. And an annular sleeve 32 'freely coupled thereto.
- Dog gears 15d 'and 15e that engage with the spline teeth of the sleeve 32' are provided on the left and right sides of the sleeve 32 '.
- the dog gear 15 d ′ on the left side of the sleeve 32 ′ is fixed to the first counter shaft 15, and can be rotated integrally with the high-side fixed gear 15 H ′ via the first counter shaft 15.
- the right dog gear 15e is configured in the same manner as in the above-described embodiment.
- a tooth surface portion that meshes with the ring gear 18a of the differential 18 is provided at the right portion of the idle gear 15b, and a switching mechanism is provided at the tip of a cylindrical portion that protrudes to the left of the tooth surface portion (that is, the left portion of the idle gear 15b).
- 30 'hub 31' is coupled.
- the low-side idle gear 15L is pivotally supported on the outer periphery of the cylindrical portion of the idle gear 15b so as to be relatively rotatable. That is, these two idle gears 15L and 15b have a double tube structure.
- the output idle gear 15 b is idled, so that the power transmission of the engine 2 is interrupted.
- the sleeve 32 'moves from the neutral position to either the left or right and engages with one of the dog gears 15d' and 15e either the rotation of the fixed gear 15H 'or the rotation of the idle gear 15L becomes the idle gear 15b. introduce. That is, if the sleeve 32 'moves to the right and engages with the dog gear 15e of the idle gear 15L, the low gear stage is selected. Conversely, if the sleeve 32' moves to the left and engages with the dog gear 15d ', the high gear is selected. A stage is selected.
- the casing 1C of the present modification is formed in a cylindrical shape in which the periphery of the first counter shaft 15 protrudes outward (left side) along the axial direction.
- This cylindrical projecting portion (hereinafter referred to as “cylindrical portion 1D”) is arranged and shaped so as not to interfere with either the motor 3 or the generator 4 when the motor 3 and the generator 4 are attached to the casing 1C.
- the cylindrical portion 1D is located in a region between the rotation shaft 3a (motor shaft 13) of the motor 3 and the rotation shaft 4a (generator shaft 14) of the generator 4 when the powertrain 7 is viewed from the left side (in side view). Be placed.
- region between” here means the area
- the switching mechanism 30 ′ is built in the cylindrical portion 1D.
- the casing 1C is partially enlarged only at the place where the switching mechanism 30 ′ is disposed, so that an increase in size of the transaxle 1 can be avoided. Further, by arranging the cylindrical portion 1D in the region between the rotary shafts 3a and 4a of the motor 3 and the generator 4, it is possible to avoid an increase in the size of the power train 7 including the transaxle 1. In addition, the same effect can be acquired from the structure similar to embodiment mentioned above and a 1st modification.
- the first counter shaft 15 is provided with the fixed gear 15a, the high-side idle gear 25H, the low-side idle gear 25L, and the switching mechanism 40 in order from the right side.
- the switching mechanism 40 of the present modification controls the connection / disconnection state of the power of the engine 2 and switches between the high gear stage and the low gear stage. Similar to the second modification described above, the cylindrical portion 1D of the casing 1C. Built in.
- the switching mechanism 40 includes a high-side multi-plate clutch (high-side clutch) that connects and disconnects the high gear stage to the second path 52 and a low-side multi-plate clutch that connects and disconnects the low gear stage to the second path 52. It is provided as an integrated combination with a plate clutch (low side clutch).
- the hydraulic pressure of each clutch is supplied from two oil passage inlets 5 a and 5 a ′ provided on the first counter shaft 15.
- the switching mechanism 40 has two engagement elements 41H and 42H that constitute a high-side clutch, and two engagement elements 41L and 42L that constitute a low-side clutch.
- the driving-side engaging elements 41H and 41L are fixed to the two idle gears 25H and 25L, respectively, and the power from the engine 2 is input thereto.
- the driven-side engagement elements 42H and 42L are respectively fixed to the first counter shaft 15 and output power to the drive wheel 8 side.
- the two idle gears 25H and 25L are both arranged on the first counter shaft 15 to form a double pipe structure, and are arranged coaxially with these. Since the high / low switching is performed by the two switching mechanisms 40, the transaxle 1 can be made compact. Further, in the transaxle 1 of this modification, as in the second modification described above, the casing 1C only needs to be partially enlarged at the place where the switching mechanism 40 is disposed, and therefore the enlargement of the transaxle 1 is avoided. be able to.
- connection / disconnection mechanism 20 of the above-described embodiment is interposed in the motor shaft 13.
- connection / disconnection mechanism 20 of this modification is interposed on the right side of the ring gear 18a of the differential 18.
- the trunk axle 1 of this modification is different from the above-described embodiment and each modification in that the power transmission path from the input shaft 11 to the output shaft 12 is different between the high gear stage and the low gear stage.
- the broken line in a figure represents that the gear is meshing.
- the switching mechanism of the present modification has a high side clutch 40H and a low side clutch 40L as in the third modification, but differs in that these are provided separately.
- the high-side clutch 40H is interposed on the second counter shaft 16 as described above, and the low-side clutch 40L is interposed on the first counter shaft 15.
- the high side clutch 40H is disposed on the right side of the ring gear 18a of the differential 18 and at a position overlapping the clutch 21 on the motor shaft 13 in the width direction.
- the low-side clutch 40L is disposed in the cylindrical portion 1D.
- the high clutch 40H is a multi-plate clutch having two engagement elements 41H and 42H, as in the third modification described above, and is supplied with hydraulic pressure supplied from an oil passage inlet 5c provided on the second countershaft 16. Accordingly, they are driven in a direction of separating (cutting) and approaching (engaging) each other.
- the low-side clutch 40L is also a multi-plate clutch having two engaging elements 41L and 42L, and is driven in a direction of separating (disconnecting) and approaching (engaging) each other according to the hydraulic pressure supplied from the oil passage inlet 5a. .
- the casing 1C only needs to be partially enlarged only at a location (cylindrical portion 1D) where the low-side clutch 40L is disposed, so that enlargement of the transaxle 1 can be avoided.
- an increase in the size of the power train 7 including the transaxle 1 can be avoided.
- the high side clutch 40H and the clutch 21 so as to overlap each other in the width direction, it is possible to prevent an increase in the axial dimension, and it is also possible to avoid an increase in size.
- the same effect can be acquired from the structure similar to embodiment mentioned above.
- the transaxle 1 according to the fifth modification is different from the above-described fourth modification (FIG. 8) in that a connection / disconnection mechanism 20 ′ is provided on the second counter shaft 16.
- the transaxle 1 of this modification is similar to the above-described first modification in that the motor 3 is connected to the motor 3 by the connecting / disconnecting mechanism 20 'having the idler gear 16c and the clutch 21' provided on the second countershaft 16.
- the power connection / disconnection state is controlled.
- the second countershaft 16 is provided with oil passage inlets 5c and 5c 'for supplying hydraulic pressure to the clutch 21' and the high side clutch 40H, respectively. Even with such a configuration, the same effect can be obtained from the configuration similar to the above-described embodiment and the first and fourth modifications.
- the high gear stage of this modification is formed from a high-side fixed gear 11H provided on the input shaft 11 and a high-side idler gear 15H provided on the first counter shaft 15 as in the above-described embodiment. Is done.
- the high-side clutch 40H ′ connects and disconnects the idle gear 15H with respect to the first countershaft 15, and is disposed on the first countershaft 15 and in the cylindrical portion 1D.
- the high side clutch 40H ′ is a multi-plate clutch having two engagement elements 41H ′ and 42H ′, and is separated (disconnected) and approached (engaged) in accordance with the hydraulic pressure supplied from the oil passage inlet 5a. Driven by.
- the low gear stage of this modification is formed by a low-side fixed gear 11L provided on the input shaft 11 and a low-side idler gear 16L provided on the second counter shaft 16. That is, the low gear stage is provided on a path from the input shaft 11 to the output shaft 12 via the second counter shaft 16.
- the fixed gear 11L and the idle gear 16L are always meshed, and the idle gear 16L is connected to and disconnected from the second counter shaft 16 by a low-side clutch 40L ′ interposed in the second counter shaft 16.
- the low-side clutch 40L ′ is a multi-plate clutch having two engagement elements 41L ′ and 42L ′, and is separated (disconnected) and approached (engaged) in accordance with the hydraulic pressure supplied from the oil passage inlet 5c. Driven by.
- the input shaft 11 of this modification is provided with a high-side fixed gear 11H at the left end, and a low-side fixed gear 11L is provided adjacent to the right side of the fixed gear 11H.
- the low-side clutch 40L ′ is disposed on the left side of the fixed gear 16b that meshes with the ring gear 18a of the differential 18.
- connection / disconnection mechanism 20 is interposed on the motor shaft 13 as in the above-described embodiment (FIGS. 3 and 4).
- the point that the clutch 21 is provided on the right side of the idle gear 13b and the timing at which the clutch 21 is engaged are different from those of the above-described embodiment.
- the transaxle 1 is provided so that the power transmission path from the input shaft 11 to the output shaft 12 is different between the high gear stage and the low gear stage, as in the above-described fourth modification (FIG. 8).
- the power transmission path of the high gear stage is different from that of the fourth modification.
- the high gear stage of this modification includes a high-side fixed gear 11H provided on the input shaft 11, a high-side idler gear 13H provided on the motor shaft 13, and an idle gear 17a provided therebetween.
- the idle gear 17a is a gear for adjusting the rotation direction, and is arranged in parallel with the six shafts 11 to 16 and fixed to an intermediate shaft 17 provided between the input shaft 11 and the motor shaft 13. Both the fixed gear 11H and the idle gear 13H are always meshed with the idle gear 17a.
- the motor shaft 13 is provided with a high-side clutch 43H on the left side of the connection / disconnection mechanism 20.
- the high-side clutch 43H connects and disconnects the idle gear 13H with respect to the motor shaft 13, and is disposed at a position overlapping the ring gear 18a of the differential 18 in the width direction. That is, the high gear stage of this modification is provided on a path from the input shaft 11 to the output shaft 12 via the intermediate shaft 17, the motor shaft 13, and the second counter shaft 16.
- the high-side clutch 43H is also a multi-plate clutch having two engaging elements 44H and 45H, and is separated (disconnected) and approached (closed) according to the hydraulic pressure supplied from the oil passage inlet 5b 'provided in the motor shaft 13. Driven in the direction of engagement).
- the clutch 21 of the present modification is hydraulically controlled so as to be engaged when the high gear is selected even when the motor 3 is stopped, even when the motor 3 is stopped (OFF state). Thereby, the power of the engine 2 is transmitted to the output shaft 12.
- the clutch 21 is disengaged when at least the low gear is selected.
- the power transmission path of the motor 3 is disconnected by the connection / disconnection mechanism 20 while the motor 3 is stopped and the low gear stage is selected. This can be prevented and can contribute to an improvement in power consumption. Also in this modification, since the dead space can be used effectively, the high gear stage or the low gear stage can be set without increasing the axial dimension of the transaxle 1. In addition, the same effect can be acquired from the structure similar to embodiment mentioned above and each modification.
- connection / disconnection mechanism 20 similar to that in the seventh modification described above is interposed in the motor shaft 13. Further, the present transaxle 1 differs from the above-described seventh modification (FIG. 11) in that the positional relationship between the high gear stage and the low gear stage and that the switching mechanism 43L is provided on the intermediate shaft 17.
- the low gear stage is arranged on the right side and the high gear stage is arranged on the left side as in the above-described embodiment.
- the configuration of the high gear stage is the same as that of the sixth modification.
- the low gear stage of the present modification includes a low-side fixed gear 11L provided on the input shaft 11, a low-side fixed gear 13L provided on the motor shaft 13, and an idle gear 17b provided therebetween. It is formed.
- the idle gear 17b is a gear provided in the intermediate shaft 17 for adjusting the rotation direction, as in the seventh modification.
- the idle gear 17b is provided as an idle gear unlike the seventh modification.
- the fixed gears 11L and 13L are always meshed with the idle gear 17b.
- the low-side clutch 43L interposed in the intermediate shaft is a multi-plate clutch having two engaging elements 44L and 45L, and is separated from each other according to the hydraulic pressure supplied from the oil passage inlet 5d provided in the intermediate shaft 17. It is driven in the direction of (cutting) and approaching (engaging).
- the idle gear 17b is fixed to the engaging element 44L, and the low-side clutch 43L connects and disconnects the idle gear 17b with respect to the intermediate shaft 17.
- the clutch 21 of the present modification is hydraulically controlled so that it engages when the low gear is selected even when the motor 3 is stopped, even when the motor 3 is stopped (off state). Thereby, the power of the engine 2 is transmitted to the output shaft 12.
- the clutch 21 is disengaged when at least the high gear stage is selected.
- the power transmission path of the motor 3 is disconnected by the connecting / disconnecting mechanism 20 while the motor 3 is stopped and the high gear stage is selected. This can be prevented and can contribute to an improvement in power consumption. Also in this modification, since the dead space can be used effectively, the high gear stage or the low gear stage can be set without increasing the axial dimension of the transaxle 1. In addition, the same effect can be acquired from the structure similar to embodiment mentioned above and each modification.
- the transaxle 1 according to the ninth modified example has the same configuration as that of the first modified example (FIG. 5) described above except that the configuration of the switching mechanism and the configuration of the connecting / disconnecting mechanism are different. Is done.
- the switching mechanism includes two selection mechanisms 30A and 30B that select a high gear stage and a low gear stage, respectively.
- One selection mechanism 30 ⁇ / b> A is interposed in the input shaft 11, and the other selection mechanism 30 ⁇ / b> B is interposed in the first counter shaft 15. Further, these selection mechanisms 30A and 30B are arranged at positions overlapping each other in the width direction.
- the selection mechanism 30A has a hub 31A fixed to the input shaft 11 and an annular shape that is not rotatable relative to the hub 31A (input shaft 11) and is slidably coupled in the axial direction of the input shaft 11. And a sleeve 32A.
- the selection mechanism 30B is not rotatable relative to the hub 31B fixed to the first countershaft 15 and the hub 31B (first countershaft 15), and in the axial direction of the first countershaft 15.
- an annular sleeve 32B slidably coupled.
- These sleeves 32A and 32B also have spline teeth (not shown) on the radially inner side.
- the input shaft 11 is provided with a fixed gear 11H on the left side of the selection mechanism 30A, and on the right side of the selection mechanism 30A is provided an idler gear 11L ′ having a smaller number of teeth than the fixed gear 11H.
- the first countershaft 15 is provided with the above-described idle gear 15H on the left side of the selection mechanism 30B, and on the right side of the selection mechanism 30B is a fixed gear 15L 'having more teeth than the idle gear 15H. .
- the fixed gear 11L ′ and the idle gear 15L ′ are always meshed.
- the idle gear 11L ′ has a tooth surface portion that meshes with the fixed gear 15L ′ on the right side, and a dog gear 11e that is coupled to a contact portion that protrudes on the left side of the tooth surface portion.
- the dog gear 11e also has dog teeth (not shown) at the tip.
- the power of the engine 2 is output to the output shaft via the fixed gear 11H and the idle gear 15H. 12 is transmitted. That is, in this case, the high-gear idle gear 15 ⁇ / b> H is in a rotationally connected state with respect to the first counter shaft 15.
- one of the two selection mechanisms 30A and 30B constituting the switching mechanism is disposed on the input shaft 11, thereby suppressing loss due to the oil bath. Can do. Further, since the two selection mechanisms 30A and 30B can be operated simultaneously to perform the high / low switching, the time required for the high / low switching can be shortened compared to the case of the single switching mechanism 20, and the high / low switching can be performed. Can be implemented promptly.
- connection / disconnection mechanism 20 ′′ of the present modification rotates relative to the hub 27 fixed to the second counter shaft 16 and the hub 27 (second counter shaft 16). And an annular sleeve 28 that is slidably coupled in the axial direction. Spline teeth (not shown) are provided on the radially inner side of the sleeve 28.
- the second countershaft 16 is provided with an idle gear 16d on the right side of the connection / disconnection mechanism 20 ′′.
- the idle gear 16d has more teeth than the fixed gear 13a of the motor shaft 13 and has a tooth on the right side thereof.
- the dog gear 16e has a tooth surface portion that always meshes with the fixed gear 13a, and is coupled to a contact portion protruding on the left side of the tooth surface portion. Have teeth.
- the idle gear 16d When the sleeve 28 is in the neutral position, the idle gear 16d is idling, and the power transmission of the first path 51 is cut off.
- the sleeve 28 moves in the axial direction (right side) and engages with the dog gear 16e of the idle gear 16d, the idle gear 16d is in a rotationally connected state with respect to the second counter shaft 16, and the power transmission of the first path 51 is transmitted. It becomes possible. That is, the power of the motor 3 is transmitted to the output shaft 12.
- the power connection and disconnection are switched by the sleeve 28, so there is no restriction on the gear ratio and the degree of freedom in design can be increased.
- the connecting / disconnecting mechanism 20 ′′ and the idle gear 16d are interposed in the second countershaft 16. Therefore, even if the second countershaft 16 rotates as the output shaft 12 rotates, Therefore, even if a part or all of the idle gear 16d is bathed in oil, the oil in the transaxle 1 is not stirred, so that the efficiency of the transaxle 1 is reduced. There is no.
- connection / disconnection mechanism 20 ′′ is interposed in the second counter shaft 16
- connection / disconnection mechanism having the hub 27 and the sleeve 28 is connected to the shaft (for example, the motor) It may be provided on the shaft 13).
- the transaxle 1 according to the tenth modified example is the above-described ninth modified example (except for the positional relationship between the connecting / disconnecting mechanism 20 ′′ on the second countershaft 16 and the idle gear 16d). 13)
- the idle gear 16d is arranged on the left side (side closer to the differential 18) of the connection / disconnection mechanism 20 ′′.
- the transaxle 1 having such an arrangement since the position of the fixed gear 13a on the motor shaft 13 is closer to the motor 3 than in the case of FIG. 13, the length of the motor shaft 13 can be shortened. It is possible to reduce the size of the casing 1C.
- the same effect can be acquired from the structure similar to embodiment mentioned above and each modification.
- the switching mechanism (or a part of the switching mechanism) that switches between the high gear stage and the low gear stage is exemplified as the transaxle 1 interposed in the first counter shaft 15.
- the arrangement is not particularly limited, and may be interposed on the input shaft 11, for example. Note that the switching mechanism is not an essential configuration and can be omitted.
- connection / disconnection mechanism 20 is disposed at a position overlapping the ring gear 18a of the differential 18 in the width direction, but the position of the connection / disconnection mechanism 20 is not limited thereto.
- it may be arranged at a position overlapping with the elements other than the ring gear 18a (diff case 18b, differential pinion 18d, etc.) of the differential 18 in the width direction, or may be arranged so as not to overlap the differential 18.
- connection / disconnection mechanism 20, 20 ′ is configured to include an idle gear and a clutch is illustrated, but the above-described embodiment and the first embodiment
- the connecting / disconnecting mechanisms 20 and 20 ′ of the eighth modification may be replaced with the connecting / disconnecting mechanism 20 ′′ of the ninth and tenth modifications (that is, using a sleeve instead of a clutch).
- the relative positions of the engine 2, the motor 3, the generator 4, and the pump 5 with respect to the transaxle 1 are not limited to those described above.
- the arrangement of the six shafts 11 to 16 in the transaxle 1 may be set according to these relative positions.
- the arrangement of gears provided on each shaft in the transaxle 1 is an example, and is not limited to the above.
- Transaxle Transaxle device
- Engine Motor (electric motor, first rotating electrical machine) 3a Rotating shaft 4 Generator (generator, second rotating electrical machine) 8 Drive wheel 10 Vehicle 12 Output shaft 13 Motor shaft (first rotating electrical machine shaft) 13a Fixed gear (first gear) 13b idle gear (first gear) 16 Second counter axis (counter axis) 16a Fixed gear (second gear) 16b fixed gear 16c idle gear (second gear) 16d idle gear (second gear) 16H, 16L idler gear 18 differential (differential gear) 20, 20 ', 20 "disconnection mechanism 21, 21' clutch 22, 22 'first engagement element 23, 23' second engagement element 28 sleeve 30, 30 ', 40 switching mechanism 32, 32', 32A, 32B Sleeve 40H, 40H ', 43H High side clutch (switching mechanism) 40L, 40L ', 43L Low side clutch (switching mechanism) 51 First path (first power transmission path) 52 Second path (second power transmission path)
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transportation (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- General Engineering & Computer Science (AREA)
- Power Engineering (AREA)
- Automation & Control Theory (AREA)
- Hybrid Electric Vehicles (AREA)
- Electric Propulsion And Braking For Vehicles (AREA)
- Arrangement Of Transmissions (AREA)
- Structure Of Transmissions (AREA)
Abstract
Description
本件は、このような課題に鑑み案出されたもので、電費を向上させることができるようにした、トランスアクスル装置を提供することを目的の一つとする。なお、この目的に限らず、後述する発明を実施するための形態に示す各構成により導かれる作用効果であって、従来の技術によっては得られない作用効果を奏することも本件の他の目的である。
(3)この場合、前記第一の回転電機軸上の固定ギヤと前記カウンタ軸上の遊転ギヤとが常時噛合しているとともに、前記遊転ギヤの歯数が前記固定ギヤの歯数よりも多いことが好ましい。
(5)この場合、前記出力軸に介装されたデファレンシャルギヤを備え、前記断接機構が、前記出力軸の軸方向に直交する方向において、前記デファレンシャルギヤと重なる位置に介装されていることが好ましい。
(8)前記エンジンから前記出力軸までのエンジン動力伝達経路上に介装されたスリーブ又はクラッチを有し、ハイギヤ段とローギヤ段とを切り替える切替機構を備えていることが好ましい。
本実施形態のトランスアクスル1(トランスアクスル装置)は、図1に示す車両10に適用される。この車両10は、エンジン2と走行用のモータ3(電動機,第一の回転電機)と発電用のジェネレータ4(発電機,第二の回転電機)とを装備したハイブリッド車両である。ジェネレータ4はエンジン2に連結され、モータ3の作動状態とは独立して作動可能とされる。また、車両10にはEVモード,シリーズモード,パラレルモードの三種類の走行モードが用意される。これらの走行モードは、図示しない電子制御装置によって、車両状態や走行状態,運転者の要求出力等に応じて択一的に選択され、その種類に応じてエンジン2,モータ3,ジェネレータ4が使い分けられる。なお、モータ3は発電機能(ジェネレータの機能)を有していてもよいし、また、ジェネレータ4は電動機能(モータの機能)を有していてもよい。
図3は、本実施形態のトランスアクスル1を動力伝達経路に沿って軸方向に切断した断面図であり、図4はこのトランスアクスル1を備えたパワートレイン7のスケルトン図である。なお、図4以降のスケルトン図では、ポンプ5とトランスアクスル1とを一体化させて(ポンプ5をケーシング1Cに内蔵させて)図示する。
入力軸11には、二つの固定ギヤ11H,11Lが設けられる。二つの固定ギヤ11H,11Lは、互いに異なる歯数を持ち、第一カウンタ軸15に設けられた互いに歯数の異なる二つの遊転ギヤ15H,15Lのそれぞれと常時噛合している。
なお、デフ18は、図3に示すように、リングギヤ18aに伝達された動力を、デフケース18b,ピニオンシャフト18c,デフピニオン18d,サイドギヤ18eを介して出力軸12に伝達する。
(1)上述したトランスアクスル1には、モータ3の動力を断接する断接機構20が設けられることから、モータ3がオフの状態で駆動輪8の回転に連れ回されることを防ぐことができる。このため、従来実施していた弱め界磁制御が不要となることから、弱め界磁制御の実施により消費していた電力を走行のために用いることができる。すなわち、断接機構20を設けることで、電費を向上させることができる。
(4)また、上述したトランスアクスル1では、断接機構20が遊転ギヤ13bとクラッチ21とを有しているため、クラッチ21の断接を制御するだけで簡単にモータ3の動力伝達を断接することができる。
上述したトランスアクスル1は一例であって、その構成は上述したものに限られない。以下、トランスアクスル1の変形例について、図5~図14を用いて説明する。図5~図14は、第一変形例~第十変形例に係るトランスアクスル1を備えたパワートレイン7を示すスケルトン図である。なお、上述した実施形態やそれまでに説明した変形例と同様の構成については、上述した実施形態や変形例の符号と同一の符号又は同様の符号(同一の数字に異なるアルファベット等)を付し、重複する説明は省略する。
図5に示すように、第一変形例に係るトランスアクスル1は、入力軸11とジェネレータ軸14とを連結する構成と、断接機構20′が第二カウンタ軸16に配置されている点とを除いて、上述した実施形態と同様に構成される。本変形例のトランスアクスル1には、ジェネレータ14の固定ギヤ14aと常時噛合する固定ギヤ11aが入力軸11に設けられており、これらの固定ギヤ11a,14aによってエンジン2とジェネレータ4との間で動力伝達可能とされる。なお、上述した固定ギヤ11Lは、第一カウンタ軸15の遊転ギヤ15Lのみと常時噛合している。
図6に示すように、第二変形例に係るトランスアクスル1は、ハイギヤ段,ローギヤ段の位置関係と切替機構30′の構成とが異なる点を除いて、上述した第一変形例(図5)と同様に構成される。本変形例では、ハイギヤ段(固定ギヤ11H,固定ギヤ15H′)がケーシング1C内の右側(デフ18側)に配置され、ローギヤ段(固定ギヤ11L,遊転ギヤ15L)がケーシング1C内の左側に配置される。なお、本変形例では、第一カウンタ軸15に設けられた固定ギヤ15H′が、入力軸11の固定ギヤ11Hと常時噛合することでハイギヤ段を形成する。
図7に示すように、第三変形例に係るトランスアクスル1は、ハイギヤ段,ローギヤ段の位置関係と切替機構40の構成とが異なる点を除いて、上述した第一変形例(図5)と同様に構成される。本変形例では、ハイギヤ段(固定ギヤ11H,遊転ギヤ25H)がケーシング1C内の右側(デフ18側)に配置され、ローギヤ段(固定ギヤ11L,遊転ギヤ25L)がケーシング1C内の左側に配置される。なお、本変形例の入力軸11には、ハイ側の固定ギヤ11Hの右側に、第一変形例と同様の固定ギヤ11aが設けられる。
図8に示すように、第四変形例に係るトランスアクスル1では、上述した実施形態の断接機構20がモータ軸13に介装される。ただし、本変形例の断接機構20は、デフ18のリングギヤ18aよりも右側に介装される。また、本変形例のトランクアクスル1は、上述した実施形態及び各変形例に対し、入力軸11から出力軸12に至る動力伝達経路が、ハイギヤ段とローギヤ段とで相違する点で異なる。なお、図中の破線はギヤが噛み合っていることを表す。
図9に示すように、第五変形例に係るトランスアクスル1は、上述した第四変形例(図8)に対し、断接機構20′が第二カウンタ軸16に設けられている点で異なる。すなわち、本変形例のトランスアクスル1は、上述した第一変形例と同様に、第二カウンタ軸16に設けられた遊転ギヤ16c及びクラッチ21′を有する断接機構20′により、モータ3の動力の断接状態が制御される。なお、第二カウンタ軸16には、クラッチ21′とハイ側クラッチ40Hとにそれぞれ作動油圧を供給するための油路入口5c,5c′が設けられる。このような構成であっても、上述した実施形態及び第一,第四変形例と同様の構成からは同様の効果を得ることができる。
図10に示すように、第六変形例に係るトランスアクスル1では、上述した第一変形例(図5)の断接機構20′が第二カウンタ軸16に介装される。また、本トランスアクスル1は、上述した第四変形例(図8)と同様に、入力軸11から出力軸12に至る動力伝達経路がハイギヤ段とローギヤ段とで相違するように設けられるが、その配置が第四変形例のものと異なる。なお、本変形例の切替機構は、上記の第四変形例と同様に、ハイ側クラッチ40H′とロー側クラッチ40L′とが別体で設けられる。
図11に示すように、第七変形例に係るトランスアクスル1では、上述した実施形態(図3,図4)と同様に、モータ軸13に断接機構20が介装される。ただし、遊転ギヤ13bの右側にクラッチ21が設けられる点とクラッチ21が係合されるタイミングとが上述した実施形態のものと異なる。また、本トランスアクスル1は、上述した第四変形例(図8)と同様に、入力軸11から出力軸12に至る動力伝達経路がハイギヤ段とローギヤ段とで相違するように設けられる。ただし、ハイギヤ段の動力伝達経路が第四変形例のものと異なる。
図12に示すように、第八変形例に係るトランスアクスル1では、上述した第七変形例と同様の断接機構20がモータ軸13に介装される。また、本トランスアクスル1は、上述した第七変形例(図11)に対し、ハイギヤ段,ローギヤ段の位置関係と、中間軸17に切替機構43Lが設けられる点とが異なる。
図13に示すように、第九変形例に係るトランスアクスル1は、切替機構の構成と断接機構の構成とが異なる点を除いて、上述した第一変形例(図5)と同様に構成される。
まず、本変形例の切替機構について説明する。本切替機構は、ハイギヤ段及びローギヤ段のそれぞれを選択する二つの選択機構30A,30Bから構成される。一方の選択機構30Aは入力軸11に介装され、他方の選択機構30Bは第一カウンタ軸15に介装される。また、これらの選択機構30A,30Bは、幅方向において互いに重なる位置に配置される。
図14に示すように、第十変形例に係るトランスアクスル1は、第二カウンタ軸16上の断接機構20″と遊転ギヤ16dとの位置関係を除いて、上述した第九変形例(図13)と同様に構成される。すなわち、本変形例では、断接機構20″の左側(デフ18に近い側)に遊転ギヤ16dが配置される。このような配置のトランスアクスル1によれば、図13のものと比較して、モータ軸13上の固定ギヤ13aの位置がモータ3により近くなるため、モータ軸13の長さを短くすることができ、ケーシング1Cのサイズを小さくすることができる。なお、上述した実施形態及び各変形例と同様の構成からは、同様の効果を得ることができる。
以上、本発明の実施形態及び変形例を説明したが、本発明は上述した実施形態等に限定されるものではなく、本発明の趣旨を逸脱しない範囲で種々変形することが可能である。
上述した実施形態及び各変形例では、ハイギヤ段とローギヤ段とを切り替える切替機構(または切替機構の一部)が第一カウンタ軸15に介装されたトランスアクスル1を例示したが、切替機構の配置は特に限られず、例えば入力軸11に介装されていてもよい。なお、切替機構は必須の構成ではなく、省略可能である。
2 エンジン
3 モータ(電動機,第一の回転電機)
3a 回転軸
4 ジェネレータ(発電機,第二の回転電機)
8 駆動輪
10 車両
12 出力軸
13 モータ軸(第一の回転電機軸)
13a 固定ギヤ(第一ギヤ)
13b 遊転ギヤ(第一ギヤ)
16 第二カウンタ軸(カウンタ軸)
16a 固定ギヤ(第二ギヤ)
16b 固定ギヤ
16c 遊転ギヤ(第二ギヤ)
16d 遊転ギヤ(第二ギヤ)
16H,16L 遊転ギヤ
18 デフ(デファレンシャルギヤ)
20,20′,20″ 断接機構
21,21′ クラッチ
22,22′ 第一係合要素
23,23′ 第二係合要素
28 スリーブ
30,30′,40 切替機構
32,32′,32A,32B スリーブ
40H,40H′,43H ハイ側クラッチ(切替機構)
40L,40L′,43L ロー側クラッチ(切替機構)
51 第一経路(第一動力伝達経路)
52 第二経路(第二動力伝達経路)
Claims (8)
- エンジン、第一の回転電機及び第二の回転電機を装備し、前記エンジン及び前記第一の回転電機の動力を互いに異なる動力伝達経路から個別に駆動輪側の出力軸に伝達するとともに前記エンジンの動力を前記第二の回転電機にも伝達するハイブリッド車両のトランスアクスル装置であって、
前記第一の回転電機から前記出力軸までの第一動力伝達経路上に設けられ、前記第一の回転電機の動力の伝達を断接する断接機構を備えた
ことを特徴とする、トランスアクスル装置。 - 前記第一動力伝達経路上には、前記第一の回転電機の回転軸と同軸上に接続された第一の回転電機軸と、前記第一の回転電機軸と前記出力軸との間に位置するカウンタ軸とが設けられ、
前記断接機構は、前記カウンタ軸に介装された
ことを特徴とする、請求項1記載のトランスアクスル装置。 - 前記第一の回転電機軸上の固定ギヤと前記カウンタ軸上の遊転ギヤとが常時噛合しているとともに、前記遊転ギヤの歯数が前記固定ギヤの歯数よりも多い
ことを特徴とする、請求項2記載のトランスアクスル装置。 - 前記第一動力伝達経路上には、前記第一の回転電機の回転軸と同軸上に接続された第一の回転電機軸と、前記第一の回転電機軸と前記出力軸との間に位置するカウンタ軸とが設けられ、
前記断接機構は、前記第一の回転電機軸に介装された
ことを特徴とする、請求項1記載のトランスアクスル装置。 - 前記出力軸に介装されたデファレンシャルギヤを備え、
前記断接機構が、前記出力軸の軸方向に直交する方向において、前記デファレンシャルギヤと重なる位置に介装された
ことを特徴とする、請求項4記載のトランスアクスル装置。 - 前記断接機構は、前記第一動力伝達経路上に設けられた軸に対して相対回転不能であって前記軸方向に摺動自在に結合された環状のスリーブを有し、
前記スリーブは、前記軸方向へ移動することで前記軸に対して相対回転可能な遊転ギヤを当該軸に対して回転連結状態とする
ことを特徴とする、請求項1~5のいずれか1項に記載のトランスアクスル装置。 - 前記断接機構は、
前記第一動力伝達経路上に設けられた軸に対して相対回転可能に枢支された遊転ギヤと、
前記軸に固定された第一係合要素と前記遊転ギヤに固定された第二係合要素とを持つクラッチと、を有する
ことを特徴とする、請求項1~5のいずれか1項に記載のトランスアクスル装置。 - 前記エンジンから前記出力軸までの第二動力伝達経路上に介装されたスリーブ又はクラッチを有し、ハイギヤ段とローギヤ段とを切り替える切替機構を備えた
ことを特徴とする、請求項1~7のいずれか1項に記載のトランスアクスル装置。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP17812973.0A EP3453548A4 (en) | 2016-06-13 | 2017-03-27 | BOX-BRIDGE DEVICE |
CN201780036635.9A CN109311378B (zh) | 2016-06-13 | 2017-03-27 | 变速驱动桥装置 |
US16/302,246 US10807457B2 (en) | 2016-06-13 | 2017-03-27 | Transaxle device for hybrid vehicle having connection/disconnection mechanism that enables or disables transmission of power of electric machine |
JP2018523329A JPWO2017217067A1 (ja) | 2016-06-13 | 2017-03-27 | トランスアクスル装置 |
KR1020187035801A KR102142390B1 (ko) | 2016-06-13 | 2017-03-27 | 트랜스액슬 장치 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2016117008 | 2016-06-13 | ||
JP2016-117008 | 2016-06-13 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2017217067A1 true WO2017217067A1 (ja) | 2017-12-21 |
Family
ID=60664468
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2017/012274 WO2017217067A1 (ja) | 2016-06-13 | 2017-03-27 | トランスアクスル装置 |
Country Status (6)
Country | Link |
---|---|
US (1) | US10807457B2 (ja) |
EP (1) | EP3453548A4 (ja) |
JP (2) | JPWO2017217067A1 (ja) |
KR (1) | KR102142390B1 (ja) |
CN (1) | CN109311378B (ja) |
WO (1) | WO2017217067A1 (ja) |
Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2019189460A1 (ja) * | 2018-03-30 | 2019-10-03 | 日本電産株式会社 | モータユニット |
WO2020070882A1 (ja) * | 2018-10-05 | 2020-04-09 | 日産自動車株式会社 | ハイブリッド車両 |
JP2020100268A (ja) * | 2018-12-21 | 2020-07-02 | スズキ株式会社 | ハイブリッド車両用駆動装置 |
WO2020148973A1 (ja) * | 2019-01-18 | 2020-07-23 | 三菱自動車工業株式会社 | 車両の制御装置 |
CN111655525A (zh) * | 2018-05-16 | 2020-09-11 | 舍弗勒技术股份两合公司 | 混合动力变速器和车辆 |
JP2021054289A (ja) * | 2019-09-30 | 2021-04-08 | アイシン・エィ・ダブリュ株式会社 | 車両用駆動伝達装置 |
CN112955338A (zh) * | 2018-10-30 | 2021-06-11 | 采埃孚股份公司 | 车辆的电驱动车桥 |
WO2022074413A1 (ja) * | 2020-10-09 | 2022-04-14 | 日産自動車株式会社 | トランスアクスル装置 |
WO2023166572A1 (ja) * | 2022-03-01 | 2023-09-07 | 三菱自動車工業株式会社 | 車両の制御装置 |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP6819083B2 (ja) * | 2016-06-13 | 2021-01-27 | 三菱自動車工業株式会社 | トランスアクスル装置 |
WO2018008141A1 (ja) * | 2016-07-08 | 2018-01-11 | Gkn ドライブライン ジャパン株式会社 | 動力伝達装置 |
WO2020070881A1 (ja) * | 2018-10-05 | 2020-04-09 | 日産自動車株式会社 | ハイブリッド車両 |
JP7230451B2 (ja) * | 2018-11-19 | 2023-03-01 | トヨタ自動車株式会社 | ハイブリッド車両の前部空間のレイアウト構造 |
CN109866597B (zh) * | 2019-03-29 | 2021-03-02 | 重庆长安汽车股份有限公司 | 一种多模混合动力传动系统及其控制方法 |
CN114008350B (zh) * | 2019-06-26 | 2024-06-11 | 日产自动车株式会社 | 车辆用变速装置 |
JP7078179B2 (ja) * | 2019-06-26 | 2022-05-31 | 日産自動車株式会社 | 車両の駆動装置 |
KR102239269B1 (ko) * | 2019-12-09 | 2021-04-12 | 주식회사 카펙발레오 | 하이브리드 구동 모듈 |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH11170877A (ja) * | 1997-12-09 | 1999-06-29 | Kyowa Gokin Kk | 自動車用変速機 |
JP2008239124A (ja) * | 2007-03-29 | 2008-10-09 | Daihatsu Motor Co Ltd | ハイブリッド自動車の駆動装置 |
JP2013154683A (ja) * | 2012-01-27 | 2013-08-15 | Fuji Heavy Ind Ltd | ハイブリッド車両の駆動装置およびその制御方法 |
JP2013180680A (ja) * | 2012-03-02 | 2013-09-12 | Mitsubishi Motors Corp | ハイブリッド車用トランスアクスル装置 |
Family Cites Families (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4636651B2 (ja) * | 2000-04-07 | 2011-02-23 | Gknドライブラインジャパン株式会社 | 動力伝達装置 |
JP4144570B2 (ja) * | 2004-06-10 | 2008-09-03 | トヨタ自動車株式会社 | ハイブリッド車両の制御方法 |
JP4145849B2 (ja) * | 2004-07-30 | 2008-09-03 | 本田技研工業株式会社 | ハイブリッド車両におけるパーキング装置 |
JP3985832B2 (ja) * | 2005-11-02 | 2007-10-03 | トヨタ自動車株式会社 | ハイブリッド車両の制御装置 |
JP2009067091A (ja) * | 2007-09-10 | 2009-04-02 | Toyota Motor Corp | ハイブリッド駆動装置 |
DE102008032320A1 (de) * | 2008-07-09 | 2010-01-14 | Magna Steyr Fahrzeugtechnik Ag & Co Kg | Hybridantriebsstrang für ein Kraftfahrzeug |
JP5257118B2 (ja) * | 2009-02-17 | 2013-08-07 | 日産自動車株式会社 | ハイブリッド車両の駆動装置 |
FR2958883B1 (fr) * | 2010-04-16 | 2014-02-14 | Renault Sa | Systeme de motorisation hybride |
FR2958882B1 (fr) * | 2010-04-16 | 2014-10-24 | Renault Sa | Systeme de motorisation hybride |
DE102011102277B4 (de) * | 2011-05-23 | 2017-03-23 | Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg | Antriebsstrang für ein Kraftfahrzeug |
DE102011102267A1 (de) * | 2011-05-23 | 2012-11-29 | Getrag Ford Transmissions Gmbh | Antriebsstrang für ein Kraftfahrzeug |
JP2014185742A (ja) * | 2013-03-25 | 2014-10-02 | Mitsubishi Motors Corp | 変速装置 |
CN104290588B (zh) * | 2014-01-30 | 2015-09-02 | 比亚迪股份有限公司 | 用于车辆的动力传动系统及具有其的车辆 |
CN103921666A (zh) * | 2014-04-01 | 2014-07-16 | 中国第一汽车股份有限公司 | 一种电动汽车动力系统 |
CN105644335B (zh) * | 2014-11-14 | 2020-02-28 | 上海汽车集团股份有限公司 | 车辆用双电机动力系统和双电机混合动力系统 |
CN104842766B (zh) * | 2015-01-16 | 2016-04-13 | 比亚迪股份有限公司 | 变速器、动力传动系统和车辆 |
JP6287994B2 (ja) * | 2015-08-05 | 2018-03-07 | トヨタ自動車株式会社 | 車両 |
-
2017
- 2017-03-27 US US16/302,246 patent/US10807457B2/en active Active
- 2017-03-27 WO PCT/JP2017/012274 patent/WO2017217067A1/ja unknown
- 2017-03-27 KR KR1020187035801A patent/KR102142390B1/ko active IP Right Grant
- 2017-03-27 JP JP2018523329A patent/JPWO2017217067A1/ja active Pending
- 2017-03-27 CN CN201780036635.9A patent/CN109311378B/zh active Active
- 2017-03-27 EP EP17812973.0A patent/EP3453548A4/en active Pending
-
2020
- 2020-11-24 JP JP2020194055A patent/JP7060066B2/ja active Active
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH11170877A (ja) * | 1997-12-09 | 1999-06-29 | Kyowa Gokin Kk | 自動車用変速機 |
JP2008239124A (ja) * | 2007-03-29 | 2008-10-09 | Daihatsu Motor Co Ltd | ハイブリッド自動車の駆動装置 |
JP2013154683A (ja) * | 2012-01-27 | 2013-08-15 | Fuji Heavy Ind Ltd | ハイブリッド車両の駆動装置およびその制御方法 |
JP2013180680A (ja) * | 2012-03-02 | 2013-09-12 | Mitsubishi Motors Corp | ハイブリッド車用トランスアクスル装置 |
Non-Patent Citations (1)
Title |
---|
See also references of EP3453548A4 * |
Cited By (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2019189460A1 (ja) * | 2018-03-30 | 2019-10-03 | 日本電産株式会社 | モータユニット |
CN111655525A (zh) * | 2018-05-16 | 2020-09-11 | 舍弗勒技术股份两合公司 | 混合动力变速器和车辆 |
WO2020070882A1 (ja) * | 2018-10-05 | 2020-04-09 | 日産自動車株式会社 | ハイブリッド車両 |
CN112955338A (zh) * | 2018-10-30 | 2021-06-11 | 采埃孚股份公司 | 车辆的电驱动车桥 |
JP2020100268A (ja) * | 2018-12-21 | 2020-07-02 | スズキ株式会社 | ハイブリッド車両用駆動装置 |
JP7211065B2 (ja) | 2018-12-21 | 2023-01-24 | スズキ株式会社 | ハイブリッド車両用駆動装置 |
JP7024889B2 (ja) | 2019-01-18 | 2022-02-24 | 三菱自動車工業株式会社 | 車両の制御装置 |
JPWO2020148973A1 (ja) * | 2019-01-18 | 2021-10-07 | 三菱自動車工業株式会社 | 車両の制御装置 |
WO2020148973A1 (ja) * | 2019-01-18 | 2020-07-23 | 三菱自動車工業株式会社 | 車両の制御装置 |
US11981321B2 (en) | 2019-01-18 | 2024-05-14 | Mitsubishi Jidosha Kogyo Kabushiki Kaisha | Controller for vehicle |
JP2021054289A (ja) * | 2019-09-30 | 2021-04-08 | アイシン・エィ・ダブリュ株式会社 | 車両用駆動伝達装置 |
JP7490937B2 (ja) | 2019-09-30 | 2024-05-28 | 株式会社アイシン | 車両用駆動伝達装置 |
WO2022074413A1 (ja) * | 2020-10-09 | 2022-04-14 | 日産自動車株式会社 | トランスアクスル装置 |
JPWO2022074413A1 (ja) * | 2020-10-09 | 2022-04-14 | ||
JP7351422B2 (ja) | 2020-10-09 | 2023-09-27 | 日産自動車株式会社 | トランスアクスル装置 |
WO2023166572A1 (ja) * | 2022-03-01 | 2023-09-07 | 三菱自動車工業株式会社 | 車両の制御装置 |
Also Published As
Publication number | Publication date |
---|---|
CN109311378B (zh) | 2022-03-08 |
US20190270373A1 (en) | 2019-09-05 |
JP7060066B2 (ja) | 2022-04-26 |
EP3453548A1 (en) | 2019-03-13 |
EP3453548A4 (en) | 2019-05-15 |
JPWO2017217067A1 (ja) | 2019-04-11 |
US10807457B2 (en) | 2020-10-20 |
KR20190005976A (ko) | 2019-01-16 |
JP2021049980A (ja) | 2021-04-01 |
CN109311378A (zh) | 2019-02-05 |
KR102142390B1 (ko) | 2020-08-28 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP7060066B2 (ja) | トランスアクスル装置 | |
JP6812835B2 (ja) | トランスアクスル装置 | |
CN109311379B (zh) | 变速驱动桥装置 | |
WO2017217065A1 (ja) | トランスアクスル装置 | |
WO2017217066A1 (ja) | トランスアクスル装置 | |
JP5884916B2 (ja) | ハイブリッド車両用駆動装置 | |
JP2010058695A (ja) | 動力装置 | |
US20220161652A1 (en) | Front-and-rear-wheel-drive vehicle | |
JP5115465B2 (ja) | 駆動装置 | |
JP2018154208A (ja) | ハイブリッド車両の駆動装置 | |
CN111433065B (zh) | 变速驱动桥的控制装置 | |
JP7107350B2 (ja) | トランスアクスル装置 | |
JP2018052143A (ja) | 変速機 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
ENP | Entry into the national phase |
Ref document number: 2018523329 Country of ref document: JP Kind code of ref document: A |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 17812973 Country of ref document: EP Kind code of ref document: A1 |
|
ENP | Entry into the national phase |
Ref document number: 20187035801 Country of ref document: KR Kind code of ref document: A |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
ENP | Entry into the national phase |
Ref document number: 2017812973 Country of ref document: EP Effective date: 20181205 |