WO2012127656A1 - 車両用駆動装置 - Google Patents
車両用駆動装置 Download PDFInfo
- Publication number
- WO2012127656A1 WO2012127656A1 PCT/JP2011/056999 JP2011056999W WO2012127656A1 WO 2012127656 A1 WO2012127656 A1 WO 2012127656A1 JP 2011056999 W JP2011056999 W JP 2011056999W WO 2012127656 A1 WO2012127656 A1 WO 2012127656A1
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- WIPO (PCT)
- Prior art keywords
- range
- gear
- gear piece
- clutch sleeve
- motor generator
- Prior art date
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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
- B60K1/00—Arrangement or mounting of electrical propulsion units
- B60K1/02—Arrangement or mounting of electrical propulsion units comprising more than one electric motor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
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- F16H61/12—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures
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- B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
- B60K17/344—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear
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- F16H61/04—Smoothing ratio shift
- F16H61/0437—Smoothing ratio shift by using electrical signals
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- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
- F16H37/10—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing at both ends of intermediate shafts
- F16H2037/101—Power split variators with one differential at each end of the CVT
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/04—Smoothing ratio shift
- F16H2061/047—Smoothing ratio shift by preventing or solving a tooth butt situation upon engagement failure due to misalignment of teeth
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/202—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set
- F16H2200/2023—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set using a Ravigneaux set with 4 connections
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2094—Transmissions using gears with orbital motion using positive clutches, e.g. dog clutches
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
- F16H3/727—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously with at least two dynamo electric machines for creating an electric power path inside the gearing, e.g. using generator and motor for a variable power torque path
- F16H3/728—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously with at least two dynamo electric machines for creating an electric power path inside the gearing, e.g. using generator and motor for a variable power torque path with means to change ratio in the mechanical gearing
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/62—Hybrid vehicles
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/64—Electric machine technologies in electromobility
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/70—Energy storage systems for electromobility, e.g. batteries
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/7072—Electromobility specific charging systems or methods for batteries, ultracapacitors, supercapacitors or double-layer capacitors
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/72—Electric energy management in electromobility
Definitions
- the present invention controls a transmission mechanism that selectively establishes one of a low range and a high range, a range switching mechanism that switches a range of the transmission mechanism, a motor generator that inputs driving force to the transmission mechanism, and the range switching.
- the present invention relates to a vehicle drive device including a control device.
- a speed change mechanism provided in a conventional vehicle drive device can switch between a low range (L) and a high range (H) in accordance with, for example, an operation of a range changeover switch by a driver (for example, Patent Document 1). 2).
- This range change of the speed change mechanism is performed, for example, by sliding the clutch sleeve, which is integrally rotatable with respect to the output shaft of the speed change mechanism and displaceable in the axial direction, to be connected to the low gear or the high gear. It has become.
- a plurality of teeth (splines) are provided on the outer periphery of the low gear and the high gear at equal intervals around the circumference, and a plurality of teeth that can mesh with the teeth (splines) of the two gears are provided on the inner periphery of the clutch sleeve. Teeth (splines) are provided. When the inner teeth (splines) of the clutch sleeve and the outer teeth (splines) of the low gear or the high gear are engaged (spline fitting), the clutch sleeve is connected to the low gear or the high gear.
- chamfers called chamfers are provided at the tooth tips of the clutch sleeve, low gears, and high gears, and the chamfers facilitate meshing of the teeth.
- each tooth tip is chamfered in a sharp shape like an isosceles triangle in a plan view, and each tooth tip is a right triangle in a plan view, as is well known.
- the tip of the clutch sleeve is moved to the low gear.
- it may come into contact with the tooth tip of the high gear, and the clutch sleeve can no longer be slid, and the target range cannot be switched.
- Patent Document 1 As shown in paragraphs 0031 to 0037, when the clutch sleeve becomes non-slidable and stops, it is not allowed to leave the clutch sleeve for a long time. The slide is made to return to the range position.
- Patent Document 2 as shown in FIGS. 3 and 4 and paragraphs 0014 to 0019, the purpose is to prevent the sleeve from stopping between the high speed side and the low speed side (neutral position) when the range is switched.
- the sleeve is slid, energy necessary for moving the sleeve from the high speed side to the low speed side or from the low speed side to the high speed side is accumulated, and the sleeve is slid with a large amount of energy.
- JP 2006-007989 A Japanese Patent Laid-Open No. 10-109558
- Patent Document 1 when the clutch sleeve becomes non-slidable and stops, the clutch sleeve is slid back to the range position before switching for the purpose of preventing it from being left as it is for a long time. Therefore, it is not possible to switch to the target range.
- Patent Document 2 even if the sleeve is slid with a large amount of accumulated energy, if the tooth tip of the sleeve and the tooth tip of the low gear or high gear are arranged in the same phase, these tooth tips The sleeves may come into contact with each other and the sleeve cannot be slid.
- the present invention provides a transmission mechanism that selectively establishes one of a low range and a high range, a range switching mechanism that switches a range of the transmission mechanism, a motor generator that inputs driving force to the transmission mechanism,
- the vehicle drive device comprising the control device for controlling the range switching, when the clutch sleeve becomes non-slidable during the range switching process, the clutch sleeve can be slid as soon as possible to complete the range switching. The goal is to make it possible.
- the present invention controls a transmission mechanism that selectively establishes one of a low range and a high range, a range switching mechanism that switches a range of the transmission mechanism, a motor generator that inputs driving force to the transmission mechanism, and the range switching.
- a vehicle drive device including a control device is characterized by adopting the following configuration.
- the range switching mechanism includes a low gear piece and a high gear piece that are arranged apart from each other in the axial direction, a clutch sleeve that is slidably arranged in the axial direction so as to be engaged with one of the two gear pieces, and the clutch sleeve.
- a shift actuator that is slid in any one of the axial directions and coupled to any one of the gear pieces, and a low-range power transmission path is established when the clutch sleeve is coupled to the low gear piece. Is connected to the high gear piece, the high range power transmission path is established.
- the control device rotates the gear piece to be connected in the same direction as the input rotation direction with respect to the speed change mechanism, and slides the clutch sleeve, and a sliding process of the clutch sleeve
- a coping unit that rotates in a direction opposite to the direction of the.
- the cause of the non-sliding of the clutch sleeve is, for example, that the tooth tips of the clutch sleeve and the target gear piece are in contact with each other, the target gear piece is connected with the reverse rotation.
- the tooth tip is shifted in the circumferential direction from the tooth tip of the clutch sleeve.
- the clutch sleeve can be slid as quickly as possible, and the clutch sleeve and the gear piece to be connected can be engaged with each other, so that the range switching can be completed.
- the operation processing unit causes the motor generator to rotate the connection target gear piece in the same direction as an input rotation direction with respect to the transmission mechanism, and then causes the clutch actuator to rotate the clutch sleeve. Slide.
- a second motor generator and a main transmission mechanism are provided between the motor generator and an input shaft of the transmission mechanism, and further between the second motor generator and the motor generator.
- An engine can be provided via a power split mechanism.
- the vehicle drive device in addition to including a motor generator (being a first motor generator), a speed change mechanism (being an auxiliary speed change mechanism), a range switching mechanism, and a control device, It is specified that the second motor generator, the main transmission mechanism, the power split mechanism, and the engine are provided.
- a main transmission mechanism with a torque converter is provided between an input shaft of the transmission mechanism and an output shaft of the motor generator, and an engine is connected to the upstream side of the motor generator via a clutch. It can be set as the structure provided.
- the configuration of the vehicle drive device includes a motor generator, a speed change mechanism, a range switching mechanism, and a control device, and further includes a main speed change mechanism with a torque converter, a clutch, and an engine. I have specified that.
- the operation processing unit causes the gear piece of the connection target to be in the same direction as the direction of the input rotation with respect to the transmission mechanism by the drag torque by the torque converter in response to the range switching request. It is preferable that the clutch sleeve is slid by the shift actuator after being rotated to the right.
- the operating source of the gear piece and the operating source of the clutch sleeve are specified. This specification makes the embodiment clear. In order to generate the drag torque of the torque converter, it is necessary to operate the engine, connect the clutch, and set the main transmission mechanism with the torque converter to the travel range.
- the shift actuator includes a shift fork shaft for sliding the clutch sleeve, a shift motor that generates rotational power, and the shift fork shaft that is displaced in the axial direction by the rotational power generated by the shift motor.
- a power transmission mechanism a low range detection element that outputs low range establishment information when a rotation angle of an output shaft of the shift motor reaches an angle at which the clutch sleeve is connected to the low gear piece, and an output shaft of the shift motor
- a high range detection element that outputs high range establishment information when the rotation angle of the clutch sleeve reaches an angle for completing the connection of the clutch sleeve to the high gear piece.
- the speed change mechanism includes a sun gear that receives an input rotation, a ring gear that is arranged in a non-rotating manner, a plurality of pinion gears that are interposed between the sun gear and the ring gear, and each pinion gear.
- a planetary gear including a carrier that is rotatably supported and arranged to rotate in synchronization with the revolving motion of each pinion gear, and the carrier is integrally rotatable with the low gear piece. It is possible to rotate integrally with the high gear piece.
- the structure of the transmission mechanism is specified.
- the pinion gear revolves while rotating in the same direction as the sun gear, and accordingly, the carrier and the low gear piece rotate in the revolving direction of the pinion gear. Rotate in sync with.
- the low gear piece is an internal gear
- the high gear piece is an external gear and is arranged in a non-contact manner on the inner diameter side of the low gear piece
- the clutch sleeve can mesh with the internal teeth of the low gear piece.
- External teeth and internal teeth that can mesh with the external teeth of the high gear piece are provided.
- the present invention controls a transmission mechanism that selectively establishes one of a low range and a high range, a range switching mechanism that switches a range of the transmission mechanism, a motor generator that inputs driving force to the transmission mechanism, and the range switching.
- a vehicle drive device including a control device, when the clutch sleeve becomes non-slidable during the range switching process, the clutch sleeve can be slid as soon as possible to complete the range switching.
- FIG. 3 is a cross-sectional view showing a specific structure of a subtransmission mechanism and a range switching mechanism of the transfer shown in FIGS.
- FIG. 4 is an enlarged view of the auxiliary transmission mechanism and the range switching mechanism of FIG. 3, showing a state where the clutch sleeve is positioned at a neutral position (neutral range).
- FIG. 4 shows a state where the range switching mechanism is in the low range.
- FIG. 4 shows a state where the range switching mechanism is in the high range.
- transmits a partial structure of a transfer shift actuator, and shows typically.
- FIG. 9 is a table showing a relationship between an on / off combination pattern of first to third contacts of the limit switch of FIG. 8 and an established range of the auxiliary transmission mechanism.
- FIG. 3 is a flowchart for explaining range switching control of the auxiliary transmission mechanism of FIG. 1.
- FIG. 5 is a plan view of the inner teeth of the low gear piece and the outer teeth of the clutch sleeve as viewed from the outer diameter side in FIG. 4 and shows the initial stage of switching to the low range.
- FIG. 5 is a plan view of the outer teeth of the high gear piece and the inner teeth of the clutch sleeve as viewed from the outer diameter side in FIG. 4 and shows the initial stage of switching to the high range.
- FIG. 1 to 17 show an embodiment of the present invention.
- a schematic configuration of an embodiment of a vehicle drive device according to the present invention will be described.
- This hybrid vehicle drive device is based on an FR (front engine / rear drive) drive vehicle drive device.
- 1, 1 is an engine
- 2 is a hybrid transmission
- 5 is a transfer
- 6F is a front propeller shaft
- 6R is a rear propeller shaft
- 7F is a front differential
- 7R is a rear differential
- 8F is a front wheel
- 8R Is the rear wheel.
- the engine 1 is a known drive source that outputs power by burning fuel such as a gasoline engine or a diesel engine.
- the operation state of the engine 1 controls the throttle opening (intake amount), fuel injection amount, ignition timing, and the like. It is controlled by being managed by the computer 100.
- the crankshaft (output shaft) 11 of the engine 1 is connected to the power split mechanism 3 via a damper 12.
- the damper 12 is a device for absorbing torque fluctuations of the engine 1.
- the hybrid transmission 2 includes a first motor generator MG1, a second motor generator MG2, a power split mechanism 3, a main transmission mechanism 4, and the like.
- Both the first motor generator MG1 and the second motor generator MG2 are AC synchronous motors, which function as electric motors and act as generators.
- the first motor generator MG1 and the second motor generator MG2 are each connected to a battery (power storage device) via an inverter, although not shown.
- each motor generator MG1, MG2 is brought into a regenerative or power running (assist) state.
- the regenerative power is charged into the battery via the inverter.
- the driving power for the first motor generator MG1 and the second motor generator MG2 is supplied from the battery via the inverter.
- the power split mechanism 3 is mainly composed of a single pinion type planetary gear, and includes a sun gear 31 of an external gear, a ring gear 32 of an internal gear, a plurality of pinion gears 33 of an external gear, a carrier 34, and the like.
- the ring gear 32 is concentrically spaced from the outer diameter side of the sun gear 31.
- the plurality of pinion gears 33 are disposed in opposed annular spaces between the sun gear 31 and the ring gear 32 and meshed with each other.
- the carrier 34 rotatably supports the plurality of pinion gears 33 and is rotatable in synchronization with the revolution operation of each pinion gear 33.
- the carrier 34 is connected to the crankshaft 11 of the engine 1 via the damper 12.
- Sun gear 31 is connected to the rotor of first motor generator MG1.
- the power transmission shaft 13 is connected to the ring gear 32.
- the power transmission shaft 13 is connected to the second motor generator MG2 via the main transmission mechanism 4. Further, the power transmission shaft 13 is connected to the transfer input shaft 51.
- first motor generator MG1 acts as a generator
- the motive power input from engine 1 to carrier 34 is driven through sun gear 31 to drive first motor generator MG1 as a generator, and through ring gear 32 to the wheels (front wheels). 8F and rear wheel 8R).
- first motor generator MG1 acts as an electric motor
- the power input from engine 1 to carrier 34 and the power input from first motor generator MG1 to sun gear 31 are integrated and output to ring gear 32.
- the main transmission mechanism 4 is a high-low two-stage reduction mechanism mainly composed of a Ravigneaux planetary gear.
- the main transmission mechanism 4 includes an external gear front sun gear 41, an external gear rear sun gear 42, an external gear short pinion gear 43, an external gear long pinion gear 44, an internal gear ring gear 45, a carrier 46, and the like. ing.
- the front sun gear 41 is meshed with a short pinion gear 43.
- the short pinion gear 43 is meshed with the long pinion gear 44.
- Long pinion gear 44 is engaged with ring gear 45 and rear sun gear 42, respectively.
- the ring gear 45 is concentrically spaced from the front sun gear 41 and the rear sun gear 42.
- the carrier 46 rotatably supports the short pinion gear 43 and the long pinion gear 44, and rotates in synchronization with the revolution operation of the short pinion gear 43 and the long pinion gear 44.
- the carrier 46 is connected to the power transmission shaft 13 and the transfer input shaft 51.
- Rear sun gear 42 is coupled to the rotor of second motor generator MG2.
- the front sun gear 41 is supported by the transmission case 10 via the first brake B1.
- the ring gear 45 is supported by the transmission case 10 via the second brake B2.
- the main transmission mechanism 4 is provided with a first brake B1 and a second brake B2 as switching elements for switching the gear ratio between a low range (low gear ratio) and a high range (high gear ratio).
- These brakes B1 and B2 are, for example, multi-plate or band-type hydraulic friction engagement elements that generate an engagement force by the hydraulic pressure of the hydraulic oil, and are applied to an engagement pressure generated by a hydraulic actuator (not shown). Accordingly, the torque capacity is configured to change continuously.
- the front sun gear 41 When the first brake B1 is released as non-actuated, the front sun gear 41 is separated from the non-rotating transmission case 10 so as to be relatively rotatable. On the other hand, when activated and engaged, the front sun gear 41 is integrated with the transmission case 10. Connect non-rotatable.
- the second brake B2 When the second brake B2 is released as non-actuated, the ring gear 45 is separated from the transmission case 10 so as to be relatively rotatable, and when activated and engaged, the ring gear 45 is integrated with the transmission case 10 so as not to rotate. To do.
- the transfer 5 includes a transfer input shaft 51, a rear output shaft 52, a front output shaft 53, an auxiliary transmission mechanism 54, a range switching mechanism 55, a mode switching mechanism 56, and the like.
- the transfer input shaft 51 is rotatably supported by a transfer case 545 via a rolling bearing (not shown). Rotational power output from the main transmission mechanism 4 is input to the transfer input shaft 51.
- the rear output shaft 52 is arranged coaxially with the transfer input shaft 51 and outputs rotational power to the rear wheel 8R side.
- the front output shaft 53 is arranged in parallel with the rear output shaft 52 and outputs rotational power to the front wheel 8F side.
- a drive gear 57 is externally mounted on the rear output shaft 52 via a rolling bearing (not shown) called a cage and roller, and a driven gear 58 is integrally formed on the outer diameter side of the front output shaft 53. Is formed.
- An endless member 59 such as a drive chain or a drive belt is wound around the drive gear 57 and the driven gear 58.
- the auxiliary transmission mechanism 54 is a high and low two-stage reduction mechanism mainly composed of a single pinion type planetary gear.
- the auxiliary transmission mechanism 54 includes an internal gear ring gear 541, an external gear sun gear 542, a plurality of external gear pinion gears 543, a carrier 544, and the like.
- the ring gear 541 is fixed to the transfer case 545 in a non-rotating and axially stationary manner.
- the sun gear 542 is spaced from the inner diameter side of the ring gear 541 and is connected to the transfer input shaft 51 so as to be integrally rotatable.
- the plurality of pinion gears 543 are arranged so as to mesh with the opposed annular spaces of the ring gear 541 and the sun gear 542, respectively.
- the carrier 544 rotatably supports each pinion gear 543 and rotates in synchronization with the revolution operation of each pinion gear 543.
- the mode switching mechanism 56 switches between a four-wheel drive mode (4WD) and a two-wheel drive mode (2WD) according to an operation by a driver such as a drive mode switching switch installed in the vicinity of the driver's seat (not shown). It is established selectively.
- a driver such as a drive mode switching switch installed in the vicinity of the driver's seat (not shown). It is established selectively.
- the four-wheel drive mode (4WD) is a form that secures a power transmission path for outputting the rotational power input to the transfer input shaft 51 from both the rear output shaft 52 and the front output shaft 53.
- the two-wheel drive mode (2WD) is a form that secures a power transmission path for outputting the rotational power input to the transfer input shaft 51 only from the rear output shaft 52.
- the range switching mechanism 55 is, for example, the sub-transmission mechanism 54 of the low range (L) and the high range (H) according to an operation by a driver such as a speed range switching switch installed in the vicinity of the driver's seat (not shown). One of the above is selectively established.
- the high range (H) is a state in which a power transmission path for transmitting the rotational power input to the transfer input shaft 51 from the sun gear 542 of the auxiliary transmission mechanism 54 to the rear output shaft 52 is secured, that is, the transfer input shaft 51 and the rear output shaft 52. Are directly connected to each other.
- the low range (L) is a state in which a power transmission path for transmitting the rotational power input to the transfer input shaft 51 from the carrier 544 of the auxiliary transmission mechanism 54 to the rear output shaft 52 is secured, that is, the revolution speed of the carrier 544 is the rear output shaft. This is the state output to 52.
- the reduction ratio in the low range is appropriately determined according to the diameter size and gear ratio of each part of the subtransmission mechanism 54.
- the neutral range (N) is a neutral state that is neither low range nor high range, that is, a state in which the rotational power input to the transfer input shaft 51 is not transmitted to the rear output shaft 52.
- the range switching mechanism 55 includes a low gear piece 551, a high gear piece 552, a clutch sleeve 553, a shift fork 554, a synchronizer ring 555, a sync key 556, and the like.
- the operation of the range switching mechanism 55 is controlled by the transfer shift actuator 60 and the 4WD control computer 300.
- the low gear piece 551 is coupled to the carrier 544 of the auxiliary transmission mechanism 54 so as to be integrally rotatable.
- the low gear piece 551 is an internal gear. That is, a plurality of internal teeth 551a are provided at equal intervals around the inner peripheral surface of the low gear piece 551 at the downstream end in the input direction of the rotational power.
- the high gear piece 552 is integrally formed so as to protrude from the side surface of the sun gear 542 of the auxiliary transmission mechanism 54.
- the high gear piece 552 is an external gear.
- a plurality of external teeth 552a are provided at equal intervals around the sun gear 542 on the outer peripheral surface of the high gear piece 552.
- the clutch sleeve 553 is externally mounted on the rear output shaft 52 via the hub sleeve 558 so as to be integrally rotatable and axially displaceable.
- a plurality of external teeth 553a meshed with the internal teeth 551a of the low gear piece 551 are provided at equal intervals on the outer peripheral surface of the clutch sleeve 553 in the input direction of the rotational power.
- a plurality of internal teeth 553b meshed with the external teeth 552a of the high gear piece 552 are provided at equal circumferential intervals at the upstream end portion in the input direction of the rotational power on the inner peripheral surface of the clutch sleeve 553.
- the teeth 551a, 552a, 553a, and 553b are also called splines.
- the gear pieces 551 and 552 are also called spline pieces.
- the low gear piece 551 has a cylindrical shape, and the high gear piece 552 is disposed in a non-contact state on the inner diameter side thereof.
- the internal teeth 551a of the low gear piece 551 and the external teeth 552a of the high gear piece 552 are arranged apart from each other in the axial direction.
- the outer teeth 553a and the inner teeth 553b of the clutch sleeve 553 are disposed in the axial separation space between the inner teeth 551a of the low gear piece 551 and the outer teeth 552a of the high gear piece 552, and the inner teeth 551a and the high gear piece 552 of the low gear piece 551 are arranged.
- the state that is not meshed with the external teeth 552a is the neutral range.
- both chamfers are provided on the front end side in the meshing direction of the internal teeth 551a group of the low gear piece 551, the external teeth 552a group of the high gear piece 552, the external teeth 553a group and the internal teeth 553b group of the clutch sleeve 553,
- both chamfers are those where the tooth tips are sharply chamfered like an isosceles triangle in plan view.
- the inner teeth 551a of the low gear piece 551, the outer teeth 553a and inner teeth 553b of the clutch sleeve 553, and the outer teeth 552a of the high gear piece 552 can be provided with a so-called single chamfer instead of the both chamfers.
- This single chamfer is, for example, a chamfered tooth tip shaped like a right triangle in plan view.
- FIG. 12 shows a state where the inner teeth 551a of the low gear piece 551 and the outer teeth 553a of the clutch sleeve 553 are viewed from the outer diameter side.
- FIG. 15 is a developed view of the outer teeth 552a of the high gear piece 552 and the inner teeth 553b of the clutch sleeve 553 as viewed from the outer diameter side.
- the shift fork 554 displaces the clutch sleeve 553 in the axial direction in parallel with the rear output shaft 52.
- the synchronizer ring 555 is pressed against the tapered outer peripheral surface of the high gear piece 552 by being pressed by the synchronizer key 556 interlocked with the axial slide of the clutch sleeve 553 when the clutch sleeve 553 is engaged with the high gear piece 552.
- the high gear piece 552 and the clutch sleeve 553 are rotationally synchronized by generating a friction torque on the sliding contact surface.
- the transfer shift actuator 60 drives the shift fork 554 and is provided with a shift fork shaft 61, a shift motor 62, a power transmission mechanism 63 and the like as shown in FIG. .
- the shift fork shaft 61 is provided to displace the shift fork 554 in parallel with the central axis of the clutch sleeve 553.
- the shift motor 62 generates rotational power.
- the power transmission mechanism 63 decelerates the rotational power generated by the shift motor 62 and transmits it to the shift fork shaft 61 to slide the shift fork shaft 61 in the axial direction.
- the power transmission mechanism 63 includes a plurality of gears 631, 632, 633. It is set as the combination etc.
- the shift fork shaft 61 is provided with spur teeth that mesh with the final gear 633.
- the final gear 633 and the flat teeth convert the rotational power into a linear driving force.
- the transfer shift actuator 60 is provided with a limit switch 64 for confirming the completion of switching when the range of the auxiliary transmission mechanism 54 is switched.
- This limit switch 64 is in a state where the rotation angle of the output shaft 65 of the shift motor 62 has reached the angle at which the clutch sleeve 553 is engaged with the low gear piece 551 [low range (L)], and the clutch sleeve 553 is moved to the high gear piece 552.
- a state in which the angle for completion of meshing has been reached (high range (H)), a state in which the clutch sleeve 553 has reached an intermediate angle in which the low gear piece 551 and the high gear piece 552 are not meshed (neutral range (N)), and a neutral range
- the state where the angle reached in the region between (N) and the low range (L) and the state where the angle reached in the region between the neutral range (N) and the high range (H) are individually Output a signal that represents
- the limit switch 64 has a configuration in which one common line 641, three signal lines 642 to 644, and a contact spring 645 form three contacts HL1 to HL3. It has become.
- the one common line 641 and the three signal lines 642 to 644 are made of a conductive film formed on the surface of the printed wiring board 646, and are fixed to the case 65 of the transfer shift actuator 60 or the like.
- the contact spring 645 is made of a conductive material, and is fixed to one surface of the second gear 632 of the power transmission mechanism 63.
- the contact spring 645 rotates integrally with the second gear 632 to selectively conduct the common line 641 and the first to third signal lines 642 to 644 in accordance with the rotation angle of the second gear 632. It has become.
- FIG. 7 in order to facilitate understanding of the relative positional relationship between the lines 641 to 644 and the contact spring 645, the printed wiring board 646 is omitted and only the lines 641 to 644 are shown.
- the common line 641, the first signal line 642, and the contact spring 645 form a first contact HL1
- the common line 641, the second signal line 643, and the contact spring 645 form a second contact HL2.
- 641, the third signal line 644, and the contact spring 645 constitute a third contact HL3.
- the first contact HL1 When the common line 641 and the first signal line 642 are made conductive by the contact spring 645, the first contact HL1 is turned on, and when the common line 641 and the first signal line 642 are made non-conductive, the first contact HL1 is turned off.
- the second contact HL2 When the common line 641 and the second signal line 643 are made conductive by the contact spring 645, the second contact HL2 is turned “ON”, and when the common line 641 and the second signal line 643 are made non-conductive, the second contact HL2 is turned “OFF”.
- the third contact HL3 When the common line 641 and the third signal line 644 are made conductive by the contact spring 645, the third contact HL3 is turned on, and when the common line 641 and the third signal line 644 are made non-conductive, the third contact HL3 is turned off.
- the 4WD control computer 300 sets “neutral range N and low range (L)”. It is determined that the area is between.
- the 4WD control computer 300 sets the “neutral range N and high range (L)”. It is determined that the area is between.
- Such a combination pattern of ON / OFF of the three contacts HL1 to HL3 becomes the low range establishment information and the high range establishment information described in the claims.
- the limit switch 64 corresponds to a low range detection element and a high range detection element described in the claims.
- the engine control computer 100, the power management control computer 200, and the 4WD control computer 300 are a CPU (central processing unit), ROM (program memory), RAM (data memory), backup RAM (nonvolatile memory), and the like. It is set as the well-known structure provided with.
- the ROM stores various control programs and maps that are referred to when the various control programs are executed.
- the CPU executes arithmetic processing based on various control programs and maps stored in the ROM.
- the RAM is a memory for temporarily storing calculation results in the CPU, data input from each sensor, and the like.
- the backup RAM is a non-volatile memory for storing data to be saved when the engine 1 is stopped. is there.
- the 4WD control computer 300 responds to the input of a range switching signal according to the operation of the speed range switching switch (not shown) by the driver, and switches between the high range (H) and low range (L) of the auxiliary transmission mechanism 54.
- Two-wheel drive mode (2WD) and four-wheel drive mode (4WD) in response to the input of a mode switching signal according to the range switching control related to switching and the operation of a drive mode switching switch (not shown) by the driver For example, mode switching control related to switching is performed.
- the speed range can be switched when the range switching permission condition is satisfied.
- Examples of the range switching permission condition include that the four-wheel drive mode (4WD) is set, the main transmission mechanism 3 is in the travel range, and the vehicle is stopped.
- the 4WD control computer 300 operates the transfer shift actuator 60 to move the shift fork 554 in the direction indicated by the arrow X in FIG.
- the clutch sleeve 553 is slid in the same direction by being displaced toward the right)
- the external teeth 553a of the clutch sleeve 553 are engaged with the internal teeth 551a of the low gear piece 551 as shown in FIG.
- the 4WD control computer 300 operates the transfer shift actuator 60 to move the shift fork 554 in the direction indicated by the arrow Y in FIG.
- the clutch sleeve 553 is slid in the same direction by being displaced to the left)
- the inner teeth 553b of the clutch sleeve 553 are engaged with the outer teeth 552a of the high gear piece 552 as shown in FIG.
- the synchronizer key 556 presses the synchronizer ring 555 so as to press the taper surface of the high gear piece 552, so that frictional torque is generated on the sliding contact surface, and the clutch sleeve 553.
- the high gear piece 552 are rotationally synchronized, so that the inner teeth 553b of the clutch sleeve 553 and the outer teeth 552a of the high gear piece 552 are engaged relatively smoothly.
- the external teeth 553a or the internal teeth 553b of the clutch sleeve 553 come into contact with the internal teeth 551a of the low gear piece 551 or the external teeth 552a of the high gear piece 552.
- the clutch sleeve 553 becomes non-slidable, the clutch sleeve 553 is made slidable as soon as possible so that the range switching is completed quickly and reliably.
- the flowchart in FIG. 11 is processing mainly performed by the 4WD control computer 300.
- the processing of this flowchart is started when the 4WD control computer 300 receives a range switching request, on condition that the range switching permission condition is satisfied.
- the range switching request is made, for example, when the driver selects a low range (L) or a high range (H) with a speed range switching switch (not shown).
- step S1 a timer (time measurement process) of the 4WD control computer 300 is started, and the clutch sleeve 553 is slid toward the gear piece (551 or 552) to be connected by the shift fork actuator 60.
- the set value of the time measured by the timer is a time required for the range switching to be normally completed, and is set empirically based on an experiment or the like.
- the gear piece (551 or 552) to be connected is rotated, for example, in the forward rotation direction.
- the 4WD control computer 300 transmits an operation command for rotating the second motor generator MG2 in the forward rotation direction to the power management control computer 200, whereby the transfer input shaft 51 is rotated forward by the second motor generator MG2. Rotate in the direction.
- the positive rotational power of the transfer input shaft 51 is transmitted to the connection target gear piece (551 or 552) via the auxiliary transmission mechanism 54, and the connection target gear piece (551 or 552) is rotated in the positive rotation direction.
- the forward rotation direction is the direction of input rotation (forward drive force) to the subtransmission mechanism 54.
- the target range is set to the low range (L)
- the speed is reduced via the sun gear 542, the pinion gear 543, and the carrier 544 of the auxiliary transmission mechanism 54. This is transmitted to the low gear piece 551, and the low gear piece 551 is rotated in the forward rotation direction.
- the target range is set to the high range (H)
- the transmission is transmitted to the high gear piece 552 via the sun gear 542 of the auxiliary transmission mechanism 54 without being shifted.
- the high gear piece 552 is rotated in the forward rotation direction.
- step S3 it is determined whether or not the timer started in step S1 has expired.
- step S4 If a negative determination is made in step S3, that is, if the time is not up, it is determined in step S4 whether switching to the target range is completed. The determination in step S4 is performed based on the determination logic (see FIG. 10) based on the combination pattern of the on / off states of the three contacts HL1 to HL3 of the limit switch 64 provided in the transfer shift actuator 60.
- step S4 When an affirmative determination is made in step S4, that is, when the switching to the target range is completed, this flowchart is ended, but when a negative determination is made in step S4, that is, when the switching to the target range is not completed. Returns to step S3.
- step S3 if an affirmative determination is made in step S3, that is, if the time is up, the process proceeds to step S5.
- step S5 the target gear piece (551 or 552) is rotated, for example, in the reverse rotation direction.
- an operation command for rotating the second motor generator MG2 in the reverse rotation direction is transmitted from the 4WD control computer 300 to the power management control computer 200, whereby the transfer input shaft 51 is rotated in the reverse direction by the second motor generator MG2. Rotate in the direction.
- the reverse rotation power of the transfer input shaft 51 is transmitted to the connection target gear piece (551 or 552) via the auxiliary transmission mechanism 54, and the connection target gear piece (551 or 552) is rotated in the reverse rotation direction.
- the reverse rotation direction is the direction opposite to the direction of the input rotation (forward drive force) to the subtransmission mechanism 54.
- the target range is the low range (L)
- the speed is decelerated via the sun gear 542, the pinion gear 543, and the carrier 544 of the auxiliary transmission mechanism 54. It is transmitted to the low gear piece 551, and the low gear piece 551 is rotated in the reverse rotation direction.
- the target range is set to the high range (H)
- the transfer input shaft 51 is rotated in the reverse rotation direction by the second motor generator MG2
- it is transmitted to the high gear piece 552 via the sun gear 542 of the auxiliary transmission mechanism 54 without being shifted.
- the high gear piece 552 is rotated in the reverse rotation direction.
- the range switching control when the switching to the target range is completed before the timer expires (a negative determination in step S3 and an affirmative determination in step S4), the range switching can be completed normally. As a result, the range switching control can be immediately terminated.
- step S3 if the clutch sleeve 553 becomes non-slidable during the range switching process and the range switching cannot be completed even if the timer expires (positive determination in step S3), the range switching is completed normally. Since it is no longer possible, the clutch sleeve 553 is slidably returned by reversely rotating the gear pieces 551 and 552 to be connected in step S5.
- the reason why the clutch sleeve 553 cannot be slid as described above is, for example, when the target range is set to the low range (L), the chamfer of the external teeth 553a of the clutch sleeve 553 is, as shown in FIG. In the case where the target range is set to the high range (H), the chamfer of the internal teeth 553b of the clutch sleeve 553 is placed outside the high gear piece 552 as shown in FIG. Abutting against the chamfer of the tooth 552a.
- step S5 when the low gear piece 551 or the high gear piece 552 is rotated in the reverse direction in step S5, the internal teeth 551a of the low gear piece 551 or the external teeth 552a of the high gear piece 552 are clutch sleeves as indicated by the white arrows in FIG.
- the outer teeth 553a or the inner teeth 553b of the 553 are forcibly shifted in the circumferential direction.
- the clutch sleeve 553 is slidable, so that the external teeth 553a or the internal teeth 553b of the clutch sleeve 553 are connected to the internal teeth 551a of the low gear piece 551 or the external teeth 552a of the high gear piece 552 as shown in FIG. It becomes to mesh. If it is confirmed in step S4 that this engagement has been achieved, this range switching control can be terminated.
- the cause of the non-slidable clutch sleeve 553 is, for example, that the external teeth 553a or the internal teeth 553b of the clutch sleeve 553 contact the internal teeth 551a of the low gear piece 551 or the external teeth 552a of the high gear piece 552. If this is the case, the tooth tip of the gear piece 551 or 552 to be connected is shifted in the circumferential direction from the tooth tip of the clutch sleeve 553 with the reverse rotation of the clutch sleeve 553.
- the clutch sleeve 553 can be slid as quickly as possible, and the requested range can be established. As a result, the reliability of the range switching operation can be improved.
- the auxiliary transmission mechanism 54 of the transfer 5 corresponds to the transmission mechanism described in claim 1
- the range switching mechanism 55 corresponds to the range switching mechanism described in claim 1
- the second motor generator MG2 is described in claim 1.
- the 4WD control computer 300 and the power management control computer 200 correspond to the control device according to claim 1.
- the single computer corresponds to the control device according to the first aspect.
- the operation processing unit according to claim 1 corresponds to steps S1 and S2 shown in FIG. 11
- the determination processing unit according to claim 1 corresponds to steps S3 and S4 shown in FIG.
- the handling unit described corresponds to step S5 shown in FIG.
- the vehicle drive device including the two motor generators MG1, MG2 is taken as an example, but the present invention is not limited to this.
- the present invention can also be applied to a vehicle drive device including one motor generator, and can also be applied to a vehicle drive device including only a motor generator by omitting the engine 1 as a drive source. .
- the gear piece 551 or 552 that is the switching target is rotated forward and backward by the second motor generator MG2 when dealing with the clutch sleeve 553 becoming non-slidable in the range switching process.
- the present invention is not limited to this.
- the present invention also includes a form in which the gear piece 551 or 552 to be connected is rotated forward and backward by the first motor generator MG1 during the handling.
- a vehicle drive device having a configuration in which the engine 1 and the hybrid transmission 2 are connected via the damper 12 is described as an example, but the present invention is not limited to this.
- the present invention can be applied to, for example, a four-wheel drive vehicle drive device as shown in FIG.
- a motor generator 620 is connected to a crankshaft 601 of an engine 600 via a clutch 610, and an input shaft (pump impeller shaft) of a main transmission mechanism 630 with a torque converter 640 is connected to a rotor of the motor generator 620.
- a transfer 650 is connected to the output shaft of the main transmission mechanism 630.
- a driving force is transmitted from the transfer 650 to the front wheel 663 side via the front propeller shaft 661 and the front differential 662, and the rear propeller shaft 671 is connected.
- the driving force is transmitted to the rear wheel 673 via the rear differential 672.
- the transfer 650 includes the auxiliary transmission mechanism 54 and the range switching mechanism 55 described in the above embodiment.
- the output shaft of the main transmission mechanism 630 is connected to the input shaft of the auxiliary transmission mechanism 54.
- the second motor generator MG2 is operated as shown in step S2 of the flowchart shown in FIG. 11 to connect the low gear piece (551) or the high gear piece (552) to be connected. ), It is not necessary to perform the process of inputting the positive rotational power. Instead, it is necessary to perform processing for operating the engine 600, connecting the clutch 610, and setting the main transmission mechanism 630 to the travel range.
- step S5 of the flowchart shown in FIG. 11 the motor generator 620 is used as an operation source for rotating the gear piece 551 or 552 to be connected.
- the motor generator 620 generates rotational power that is in the opposite direction to the drag torque and overcomes the drag torque, so that the sub-transmission mechanism (54) of the transfer 650 has a target gear piece (551 or 552). To be input.
- the vehicle drive device having the configuration in which the engine 1 and the hybrid transmission 2 are connected via the damper 12 is taken as an example, but the present invention is not limited to this.
- the present invention can be applied to, for example, a four-wheel drive type vehicle drive device as shown in FIG.
- a motor generator 620 is connected to a crankshaft 601 of an engine 600 via a clutch 610, an input shaft of a main transmission mechanism 630 is connected to a rotor of the motor generator 620, and the main transmission mechanism 630 is connected.
- a transfer 650 is connected to the output shaft, and driving force is transmitted from the transfer 650 to the front wheel 663 side through the front propeller shaft 661 and the front differential 662, and the rear wheel 673 is connected through the rear propeller shaft 671 and the rear differential 672. The driving force is transmitted to the side.
- the transfer 650 includes the auxiliary transmission mechanism 54 and the range switching mechanism 55 described in the above embodiment.
- the motor generator 620 is used as an operation source for rotating the gear piece 551 or 552 to be connected in steps S2 and S5 of FIG.
- the present invention controls a transmission mechanism that selectively establishes one of a low range and a high range, a range switching mechanism that switches a range of the transmission mechanism, a motor generator that inputs driving force to the transmission mechanism, and the range switching. It can utilize suitably for a vehicle drive device provided with a control device.
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Abstract
Description
エンジン1は、ガソリンエンジンやディーゼルエンジンなどの燃料を燃焼させて動力を出力する公知の駆動源であって、その運転状態がスロットル開度(吸気量)、燃料噴射量、点火時期などをエンジンコントロールコンピュータ100により管理することにより制御される。
ハイブリッドトランスミッション2は、図2に示すように、第1モータジェネレータMG1、第2モータジェネレータMG2、動力分割機構3、主変速機構4などを備えている。
第1モータジェネレータMG1及び第2モータジェネレータMG2は共に交流同期電動機であって、電動機として機能するとともに発電機として作用する。
動力分割機構3は、シングルピニオンタイプのプラネタリギヤを主体として構成されており、外歯歯車のサンギヤ31、内歯歯車のリングギヤ32、外歯歯車の複数のピニオンギヤ33、キャリア34などを備えている。
主変速機構4は、ラビニオ式プラネタリギヤを主体として構成される高低2段のリダクション機構とされている。この主変速機構4は、外歯歯車のフロントサンギヤ41、外歯歯車のリアサンギヤ42、外歯歯車のショートピニオンギヤ43、外歯歯車のロングピニオンギヤ44、内歯歯車のリングギヤ45、キャリア46などを備えている。
トランスファ5は、図2および図3に示すように、トランスファインプットシャフト51、リアアウトプットシャフト52、フロントアウトプットシャフト53、副変速機構54、レンジ切り替え機構55、モード切り替え機構56などを備えている。
副変速機構54は、図2から図4に示すように、シングルピニオンタイプのプラネタリギヤを主体として構成される高低2段のリダクション機構とされている。この副変速機構54は、内歯歯車のリングギヤ541、外歯歯車のサンギヤ542、外歯歯車の複数のピニオンギヤ543、キャリア544などを備えている。
モード切り替え機構56は、例えば図示していないが運転席近傍に設置される駆動モード切り替え用スイッチ等の運転者による操作に応じて、四輪駆動モード(4WD)と二輪駆動モード(2WD)とを選択的に成立するものである。
レンジ切り替え機構55は、例えば図示していないが運転席近傍に設置される速度レンジ切り替え用スイッチ等の運転者による操作に応じて、副変速機構54をローレンジ(L)、ハイレンジ(H)のうちの一つを選択的に成立するものである。
エンジンコントロールコンピュータ100、パワーマネジメントコントロールコンピュータ200ならびに4WDコントロールコンピュータ300は、図示していないが、CPU(中央処理装置)、ROM(プログラムメモリ)、RAM(データメモリ)、バックアップRAM(不揮発性メモリ)などを備える公知の構成とされる。
2 ハイブリッドトランスミッション
3 動力分割機構
4 主変速機構
5 トランスファ
51 トランスファインプットシャフト
52 リアアウトプットシャフト
53 フロントアウトプットシャフト
54 副変速機構
55 レンジ切り替え機構
551 ローギヤピース
551a ローギヤピースの内歯
552 ハイギヤピース
552a ハイギヤピースの外歯
553 クラッチスリーブ
553a クラッチスリーブの外歯
553b クラッチスリーブの内歯
554 シフトフォーク
558 ハブスリーブ
56 モード切り替え機構
60 トランスファシフトアクチュエータ
61 シフトフォークシャフト
62 シフトモータ
63 動力伝達機構
64 リミットスイッチ
100 エンジンコントロールコンピュータ
200 ハイブリッドコントロールコンピュータ
300 4WDコントロールコンピュータ
Claims (9)
- ローレンジおよびハイレンジの一方を選択的に成立する変速機構と、変速機構のレンジ切り替えを行うレンジ切り替え機構と、前記変速機構に駆動力を入力するモータジェネレータと、前記レンジ切り替えを制御する制御装置とを備える車両用駆動装置であって、
前記レンジ切り替え機構は、軸方向に離れて配置されるローギヤピースおよびハイギヤピースと、2つのギヤピースのいずれかに噛み合わされるように軸方向にスライド可能に配置されるクラッチスリーブと、このクラッチスリーブを軸方向いずれか一方にスライドさせて前記いずれかのギヤピースに連結させるシフトアクチュエータとを備え、かつ前記クラッチスリーブを前記ローギヤピースに連結させたときにローレンジ用動力伝達経路が成立する一方、前記クラッチスリーブを前記ハイギヤピースに連結させたときにハイレンジ用動力伝達経路が成立する構成とされ、
前記制御装置は、レンジ切り替え要求に応答して前記連結目標のギヤピースを変速機構に対する入力回転の方向と同方向に回転させるとともに、前記クラッチスリーブをスライドさせる作動処理部と、
前記クラッチスリーブのスライド過程において当該クラッチスリーブがスライド不可能になったか否かを判定する判定処理部と、
前記判定処理部でスライド不可能と判定したときに前記連結目標のギヤピースを前記モータジェネレータにより前記変速機構に対する入力回転の方向と逆方向に回転させる対処部とを含む、ことを特徴とする車両用駆動装置。 - 請求項1に記載の車両用駆動装置において、
前記作動処理部は、レンジ切り替え要求に応答して前記モータジェネレータにより前記連結目標のギヤピースを変速機構に対する入力回転の方向と同方向に回転させてから、前記シフトアクチュエータにより前記クラッチスリーブをスライドさせる、ことを特徴とする車両用駆動装置。 - 請求項2に記載の車両用駆動装置は、前記モータジェネレータと前記変速機構のインプットシャフトとの間に第2モータジェネレータと主変速機構とが設けられ、さらに前記第2モータジェネレータと前記モータジェネレータとの間に動力分割機構を介してエンジンが設けられる構成とされている、ことを特徴とする車両用駆動装置。
- 請求項1に記載の車両用駆動装置は、前記モータジェネレータと前記変速機構のインプットシャフトとの間に第2モータジェネレータと主変速機構とが設けられ、さらに前記第2モータジェネレータと前記モータジェネレータとの間に動力分割機構を介してエンジンが設けられる構成とされている、ことを特徴とする車両用駆動装置。
- 請求項1に記載の車両用駆動装置は、前記変速機構のインプットシャフトと前記モータジェネレータのアウトプットシャフトとの間にトルクコンバータ付き主変速機構が設けられ、さらに前記モータジェネレータの上流側にクラッチを介してエンジンが設けられる構成とされている、ことを特徴とする車両用駆動装置。
- 請求項5に記載の車両用駆動装置において、
前記作動処理部は、前記レンジ切り替え要求に応答して前記トルクコンバータによる引き摺りトルクにより前記連結目標のギヤピースを前記変速機構に対する入力回転の方向と同方向に回転させてから、前記シフトアクチュエータにより前記クラッチスリーブをスライドさせる、ことを特徴とする車両用駆動装置。 - 請求項1から6のいずれか1項に記載の車両用駆動装置において、
前記シフトアクチュエータは、前記クラッチスリーブをスライドさせるためのシフトフォークシャフトと、回転動力を発生するシフトモータと、このシフトモータで発生する回転動力でもって前記シフトフォークシャフトをその軸方向に変位させる動力伝達機構と、前記シフトモータの出力軸の回転角が前記クラッチスリーブを前記ローギヤピースに連結完了させる角度に到達したときにローレンジ成立情報を出力するローレンジ検知要素と、前記シフトモータの出力軸の回転角が前記クラッチスリーブを前記ハイギヤピースに連結完了させる角度に到達したときにハイレンジ成立情報を出力するハイレンジ検知要素とを備え、
前記判定処理部は、レンジ切り替え要求を受けてから所定時間が経過するまでに前記各検知要素からの出力情報に基づいて目標レンジが成立したか否かを判定し、否定判定したときに前記クラッチスリーブがスライド不可能になったと判定する、ことを特徴とする車両用駆動装置。 - 請求項1から6のいずれか1項に記載の車両用駆動装置において、
前記変速機構は、入力回転を受けるサンギヤと、非回転に配置されるリングギヤと、前記サンギヤと前記リングギヤとの間にそれぞれ噛み合うように介装される複数個のピニオンギヤと、各ピニオンギヤを回転自在に支持するとともに前記各ピニオンギヤの公転動作に同期して回転するように配置されるキャリアとを備えるプラネタリギヤとされ、
かつ、前記キャリアは前記ローギヤピースと一体回転可能とされ、前記サンギヤは前記ハイギヤピースと一体回転可能とされる、ことを特徴とする車両用駆動装置。 - 請求項1から6のいずれか1項に記載の車両用駆動装置において、
前記ローギヤピースは内歯歯車とされ、前記ハイギヤピースは外歯歯車とされて前記ローギヤピースの内径側に非接触に配置され、前記クラッチスリーブには前記ローギヤピースの内歯に噛合可能な外歯と前記ハイギヤピースの外歯に噛合可能な内歯とが設けられている、ことを特徴とする車両用駆動装置。
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US13/636,261 US8740745B2 (en) | 2011-03-23 | 2011-03-23 | Vehicle drive device |
JP2012532788A JP5316724B2 (ja) | 2011-03-23 | 2011-03-23 | 車両用駆動装置 |
PCT/JP2011/056999 WO2012127656A1 (ja) | 2011-03-23 | 2011-03-23 | 車両用駆動装置 |
DE112011100468.0T DE112011100468B4 (de) | 2011-03-23 | 2011-03-23 | Fahrzeugantriebsvorrichtung |
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PCT/JP2011/056999 WO2012127656A1 (ja) | 2011-03-23 | 2011-03-23 | 車両用駆動装置 |
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JP (1) | JP5316724B2 (ja) |
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JP6965792B2 (ja) * | 2018-02-28 | 2021-11-10 | トヨタ自動車株式会社 | 車両用駆動装置 |
US10703203B2 (en) * | 2018-06-27 | 2020-07-07 | Borgwarner Inc. | Vehicle driveline component having a two-speed transmission and a failsafe spring configured to urge the transmission into a desired speed ratio |
DE102018210897A1 (de) * | 2018-07-03 | 2020-01-09 | Zf Friedrichshafen Ag | Anordnung zum Antrieb eines Elektrofahrzeuges und Verfahren zum Betreiben |
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US8740745B2 (en) | 2014-06-03 |
DE112011100468T5 (de) | 2013-01-24 |
DE112011100468T8 (de) | 2013-08-29 |
DE112011100468B4 (de) | 2017-03-09 |
JPWO2012127656A1 (ja) | 2014-07-24 |
US20130066529A1 (en) | 2013-03-14 |
JP5316724B2 (ja) | 2013-10-16 |
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