WO2011158882A1 - ハイブリッド車両用駆動装置 - Google Patents
ハイブリッド車両用駆動装置 Download PDFInfo
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- WO2011158882A1 WO2011158882A1 PCT/JP2011/063744 JP2011063744W WO2011158882A1 WO 2011158882 A1 WO2011158882 A1 WO 2011158882A1 JP 2011063744 W JP2011063744 W JP 2011063744W WO 2011158882 A1 WO2011158882 A1 WO 2011158882A1
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- internal combustion
- combustion engine
- driving force
- engine
- cylinder operation
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- 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
- B60W20/00—Control systems specially adapted for hybrid vehicles
- B60W20/40—Controlling the engagement or disengagement of prime movers, e.g. for transition between prime movers
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- B—PERFORMING OPERATIONS; TRANSPORTING
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- 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
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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
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S903/00—Hybrid electric vehicles, HEVS
- Y10S903/902—Prime movers comprising electrical and internal combustion motors
- Y10S903/903—Prime movers comprising electrical and internal combustion motors having energy storing means, e.g. battery, capacitor
- Y10S903/904—Component specially adapted for hev
- Y10S903/905—Combustion engine
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S903/00—Hybrid electric vehicles, HEVS
- Y10S903/902—Prime movers comprising electrical and internal combustion motors
- Y10S903/903—Prime movers comprising electrical and internal combustion motors having energy storing means, e.g. battery, capacitor
- Y10S903/93—Conjoint control of different elements
Definitions
- the present invention relates to a hybrid vehicle drive device.
- a vehicle drive device including an internal combustion engine, an electric motor, first connection / disconnection means, and second connection / disconnection means is known (see, for example, Patent Document 1).
- the vehicle drive device 200 of Patent Document 1 is connected to an electric motor 210 and is selectively connected to an internal combustion engine output shaft 204 by a first connecting / disconnecting means 205.
- the second input shaft 202b selectively connected to the internal combustion engine output shaft 204 by the second connecting / disconnecting means 206, the output shaft 203 for outputting power to the driven part, and the first input shaft 202a are arranged on the first input shaft 202a.
- a first gear group composed of a plurality of gears selectively connected to the first input shaft 202a via the first synchronization device 230, 231 and a second synchronization device 216, 217 disposed on the second input shaft 202b.
- a second gear group comprising a plurality of gears selectively connected to the second input shaft 202b, and a plurality of gears disposed on the output shaft 203 and meshing with the gears of the first gear group and the second gear group.
- 3rd gi Having a twin clutch type transmission having a group, the.
- the present invention has been made in view of the above-described problems, and an object of the present invention is to provide a hybrid vehicle drive device that can achieve both quick response and improved fuel efficiency.
- an invention according to claim 1 is an internal combustion engine capable of switching between all-cylinder operation in which all cylinders are operated and rest-in-cylinder operation in which at least some cylinders are deactivated (for example, An accumulator (for example, an embodiment described later) that is used in a hybrid vehicle having an engine 6) in an embodiment described later and an electric motor (for example, a motor 7 in an embodiment described later) as drive sources and supplies electric power to the motor.
- An accumulator for example, an embodiment described later
- an electric motor for example, a motor 7 in an embodiment described later
- first input shaft for example, a first main shaft 11 in an embodiment described later
- gear positions for example, a third speed gear pair 23 and a fifth speed gear pair 25 in an embodiment described later
- first transmission mechanism The mechanical power from the output shaft of the internal combustion engine is received by a second input shaft (for example, the second intermediate shaft 16 of the embodiment described later), and a plurality of shift speeds (for example, for the second speed of the embodiment described later).
- a second speed change mechanism capable of engaging one of the gear pair 22 and the fourth speed gear pair 24) with the second input shaft and the drive wheel; and an output shaft of the internal combustion engine.
- a first connecting / disconnecting portion (for example, a first clutch 41 in an embodiment described later) capable of engaging with the first input shaft, an output shaft of the internal combustion engine, and the second input shaft.
- a hybrid vehicle drive device including a transmission (for example, a transmission 20 of an embodiment described later) having a second connecting / disconnecting portion (for example, a second clutch 42 of an embodiment described later) that can be combined.
- a cylinder deactivation operation necessity determination unit (for example, a cylinder deactivation operation necessity determination unit) that determines whether or not the cylinder deactivation operation of the internal combustion engine is necessary when the vehicle is capable of traveling and the required driving force of the vehicle is smaller than the driving force in the cylinder deactivation operation of the internal combustion engine
- An ECU 5 according to an embodiment to be described later, and when the idle cylinder operation necessity determination unit determines that the idle cylinder operation is unnecessary, the first connecting / disconnecting portion and the second connecting / disconnecting portion are disconnected to perform EV mode.
- the idle cylinder operation necessity determination unit determines that the idle cylinder operation is necessary, the internal combustion engine is idled, and the first and second connection parts are connected to each other. At least one of them is connected.
- the cylinder deactivation operation necessity determination unit determines that the cylinder deactivation operation is necessary when the paddle shift is selected. It is characterized by.
- the non-cylinder driving necessity determination unit determines that the cylinder-free driving is necessary when the sport mode is selected. It is characterized by.
- the deactivation operation necessity determination unit determines that the regenerative power generation is performed. It is characterized by determining that driving is necessary.
- the non-cylinder driving necessity determination unit determines that the cylinder is idle when the vehicle is cruising. It is characterized by determining that driving is necessary.
- the non-cylinder operation necessity determination unit determines that the cylinder is idle when the vehicle is traveling inertially. It is characterized by determining that driving is necessary.
- the internal combustion engine is idled while the first connecting / disconnecting portion is connected, and in the EV mode.
- pre-shifting to the second input shaft is performed, and switching from the first connecting / disconnecting portion to the second connecting / disconnecting portion is performed.
- the invention according to claim 8 is the hybrid vehicle drive device according to claim 1, further comprising a traveling state prediction unit (for example, an ECU 5 in an embodiment to be described later) linked with the car navigation system, and whether or not the idle cylinder operation is necessary.
- the determination unit determines that the cylinder rest operation is necessary when the travel state prediction unit predicts switching from the EV mode to another travel mode.
- the invention according to claim 9 is the hybrid vehicle drive device according to claim 1, further comprising an electronically controlled throttle (for example, an electronically controlled throttle 66 of an embodiment described later) capable of controlling the intake air amount of the internal combustion engine,
- an electronically controlled throttle for example, an electronically controlled throttle 66 of an embodiment described later
- the required driving force of the vehicle is smaller than the driving force in the idle cylinder operation of the internal combustion engine
- the internal combustion engine is operated in the idle cylinder operation and the electronic control throttle is opened according to the increase in the required driving force.
- the required driving force of the vehicle is larger than the driving force in the cylinder-free operation of the internal combustion engine and can be output by the motor and the driving force in the cylinder-free operation of the internal combustion engine.
- the internal combustion engine is operated in a cylinderless operation, and the motor is controlled to output a difference between the required driving force and the driving force in the cylinder idle operation of the internal combustion engine.
- the required driving force of the vehicle is greater than the sum of the driving force of the internal combustion engine in the idle cylinder operation and the driving force that can be output by the electric motor, the internal combustion engine is switched from the idle cylinder operation to the all cylinder operation.
- the opening degree of the electronic control throttle is controlled to be changed to the opening degree in the all cylinder operation.
- the idle cylinder operation includes a partially idle cylinder operation in which only some cylinders are deactivated and an idle cylinder operation.
- the required driving force of the vehicle is smaller than the driving force in the all cylinder operation of the internal combustion engine, and the BSFC bottom operation can be performed by the partial cylinder operation of the internal combustion engine.
- the required driving force of the vehicle is smaller than the driving force of the internal combustion engine in the full cylinder operation, and the difference is not less than a predetermined value.
- the vehicle is controlled to run in an EV mode or to make the internal combustion engine perform a full cylinder resting operation.
- the internal combustion engine when the required driving force of the vehicle is smaller than the driving force of the internal combustion engine during the idle cylinder operation, the internal combustion engine can be idled as necessary, thereby improving the fuel consumption. In addition, when the driving force of the internal combustion engine becomes necessary, the internal combustion engine can be driven quickly.
- the internal combustion engine can be re-driven promptly when selecting the paddle shift that requires quick response.
- the internal combustion engine can be re-driven promptly when a sports mode is selected that requires quick response.
- the internal combustion engine can be re-driven at the next shift speed.
- the internal combustion engine when the switching from the EV mode to another travel mode can be predicted at an early stage by the navigation system, the internal combustion engine is subjected to the cylinder resting operation, so that the driving force of the internal combustion engine is actually required. Even in this case, the internal combustion engine can be redriven quickly.
- the operating state of the internal combustion engine can be switched according to the required driving force, so that the fuel consumption can be further improved.
- FIG. 1stEV mode is shown, (a) is a speed diagram, (b) is a figure which shows the transmission condition of torque. It is a figure which shows the drive device for hybrid vehicles in 1st EV mode 1st all cylinder rest operation. It is a figure which shows the drive device for hybrid vehicles in 1stEV mode 2nd all cylinder rest operation. It is a flowchart which shows operation
- FIG. 1 is a schematic diagram of a vehicle drive device of Patent Document 1.
- the hybrid vehicle drive device 1 of the present embodiment is for driving drive wheels DW and DW (driven parts) via drive shafts 9 and 9 of a vehicle (not shown).
- the engine 6 is, for example, a SOHC V-type 6-cylinder engine.
- a crankshaft 6 a of the engine 6 is connected to a first clutch (first connecting / disconnecting portion) 41 and a second clutch (second connecting / disconnecting portion) of the transmission 20. Part) 42 is provided.
- the engine 6 may include a VTEC (registered trademark: variable valve mechanism), and the cylinder arrangement may be in-line or horizontal. Further, the number of cylinders of the engine 6 is not limited to 6, and can be appropriately selected according to horsepower and the like.
- the motor 7 is a three-phase brushless DC motor, and includes a stator 71 composed of 3n armatures 71a, and a rotor 72 arranged to face the stator 71.
- Each armature 71a includes an iron core 71b and a coil 71c wound around the iron core 71b.
- the armature 71a is fixed to a casing (not shown) and is arranged at substantially equal intervals in the circumferential direction around the rotation axis. Yes.
- the 3n coils 71c constitute n sets of U-phase, V-phase, and W-phase three-phase coils.
- the rotor 72 has an iron core 72a and n permanent magnets 72b arranged at almost equal intervals around the rotation axis, and the polarities of two adjacent permanent magnets 72b are different from each other.
- the fixing portion 72c for fixing the iron core 72a has a hollow cylindrical shape, is disposed on the outer peripheral side of the ring gear 35 of the planetary gear mechanism 30 described later, and is connected to the sun gear 32 of the planetary gear mechanism 30. Accordingly, the rotor 72 is configured to rotate integrally with the sun gear 32 of the planetary gear mechanism 30.
- the planetary gear mechanism 30 includes a sun gear 32, a ring gear 35 that is arranged coaxially with the sun gear 32 and that surrounds the sun gear 32, and a planetary gear 34 that meshes with the sun gear 32 and the ring gear 35. And a carrier 36 that supports the planetary gear 34 so as to be capable of rotating and revolving. In this way, the sun gear 32, the ring gear 35, and the carrier 36 are configured to be differentially rotatable with respect to each other.
- the ring gear 35 is provided with a brake mechanism 61 configured to be able to stop (lock) the rotation of the ring gear 35.
- a synchro mechanism may be used instead of the brake mechanism 61.
- the transmission 20 is a so-called dual clutch transmission that includes the first clutch 41 and the second clutch 42, the planetary gear mechanism 30, and a plurality of transmission gear groups described later.
- the transmission 20 includes a first main shaft 11 (first input shaft) disposed on the same axis (rotation axis A1) as the crank shaft 6a of the engine 6, a second main shaft 12, and a connecting shaft 13.
- a counter shaft 14 output shaft rotatable around a rotation axis B1 arranged in parallel with the rotation axis A1, and a first intermediate rotatable around a rotation axis C1 arranged in parallel with the rotation axis A1.
- a second intermediate shaft 16 (second input shaft) rotatable around a rotation axis D1 arranged in parallel with the rotation axis A1, and a rotation axis E1 arranged in parallel with the rotation axis A1 Is provided with a rotatable reverse shaft 17.
- the first main shaft 11 is provided with a first clutch 41 on the engine 6 side, and a sun gear 32 of the planetary gear mechanism 30 and a rotor 72 of the motor 7 are attached to the opposite side of the engine 6 side. Accordingly, the first main shaft 11 is selectively connected to the crankshaft 6 a of the engine 6 by the first clutch 41 and directly connected to the motor 7 so that the power of the engine 6 and / or the motor 7 is transmitted to the sun gear 32. It is configured.
- the second main shaft 12 is configured to be shorter and hollow than the first main shaft 11, and is disposed so as to be relatively rotatable so as to cover the periphery of the first main shaft 11 on the engine 6 side.
- the second main shaft 12 is provided with a second clutch 42 on the engine 6 side, and an idle drive gear 27a is integrally attached to the opposite side to the engine 6 side. Accordingly, the second main shaft 12 is selectively connected to the crankshaft 6a of the engine 6 by the second clutch 42, and the power of the engine 6 is transmitted to the idle drive gear 27a.
- the connecting shaft 13 is configured to be shorter and hollow than the first main shaft 11, and is disposed so as to be relatively rotatable so as to cover the periphery of the first main shaft 11 on the side opposite to the engine 6 side. Further, a third speed drive gear 23 a is integrally attached to the connecting shaft 13 on the engine 6 side, and a carrier 36 of the planetary gear mechanism 30 is integrally attached to the opposite side of the engine 6 side. Therefore, the carrier 36 attached to the connecting shaft 13 and the third-speed drive gear 23a are configured to rotate integrally by the revolution of the planetary gear 34.
- first main shaft 11 is rotatable relative to the first main shaft 11 between a third speed drive gear 23 a attached to the connecting shaft 13 and an idle drive gear 27 a attached to the second main shaft 12.
- a fifth driven gear 25a is provided, and a reverse driven gear 28b that rotates integrally with the first main shaft 11 is attached.
- a first main shaft 11 and a third speed drive gear 23a or a fifth speed drive gear 25a are connected or released between the third speed drive gear 23a and the fifth speed drive gear 25a.
- a shift shifter 51 is provided. When the first speed-shifting shifter 51 is in-gear at the third speed connection position, the first main shaft 11 and the third speed drive gear 23a are connected to rotate integrally and in-gear at the fifth speed connection position.
- the first main shaft 11 and the fifth speed drive gear 25a rotate integrally, and when the first speed change shifter 51 is in the neutral position, the first main shaft 11 has the third speed drive gear 23a and the fifth speed drive gear 25a. It rotates relative to the drive gear 25a.
- the sun gear 32 attached to the first main shaft 11 and the carrier 36 connected to the third speed drive gear 23a by the connecting shaft 13 are provided.
- the ring gear 35 While rotating integrally, the ring gear 35 also rotates together, and the planetary gear mechanism 30 is united.
- a first idle driven gear 27b that meshes with an idle drive gear 27a attached to the second main shaft 12 is integrally attached to the first intermediate shaft 15.
- the second intermediate shaft 16 is integrally attached with a second idle driven gear 27c that meshes with the first idle driven gear 27b attached to the first intermediate shaft 15.
- the second idle driven gear 27c constitutes the first idle gear train 27A together with the idle drive gear 27a and the first idle driven gear 27b described above.
- the second intermediate shaft 16 is rotatable relative to the second intermediate shaft 16 at positions corresponding to the third speed drive gear 23a and the fifth speed drive gear 25a provided around the first main shaft 11, respectively.
- a second speed drive gear 22a and a fourth speed drive gear 24a are provided.
- the second intermediate shaft 16 includes a second intermediate shaft 16 and a second speed drive gear 22a or a fourth speed drive gear 24a between the second speed drive gear 22a and the fourth speed drive gear 24a.
- a second shifter 52 for shifting or connecting the two.
- the second shifter 52 shifts in-gear at the second speed connection position
- the second intermediate shaft 16 and the second speed drive gear 22a rotate together
- the second shifter 52 shifts to the fourth speed.
- the second intermediate shaft 16 and the fourth-speed drive gear 24a rotate together.
- the second shifter shifter 52 is in the neutral position
- the second intermediate shaft 16 moves to the second speed.
- the drive gear 22a and the fourth speed drive gear 24a rotate relative to each other.
- a first shared driven gear 23b, a second shared driven gear 24b, a parking gear 21, and a final gear 26a are integrally attached to the counter shaft 14 in order from the side opposite to the engine 6 side.
- the first shared driven gear 23b meshes with the third speed drive gear 23a attached to the connecting shaft 13 to form the third speed gear pair 23 together with the third speed drive gear 23a
- the second speed gear pair 22 is configured together with the second speed drive gear 22a by meshing with the second speed drive gear 22a provided on the intermediate shaft 16.
- the second shared driven gear 24b meshes with the fifth speed drive gear 25a provided on the first main shaft 11 to form the fifth speed gear pair 25 together with the fifth speed drive gear 25a, and the second intermediate shaft.
- a third idle driven gear 27d that meshes with the first idle driven gear 27b attached to the first intermediate shaft 15 is integrally attached to the reverse shaft 17.
- the third idle driven gear 27d constitutes a second idle gear train 27B together with the above-described idle drive gear 27a and first idle driven gear 27b.
- the reverse shaft 17 is provided with a reverse drive gear 28 a that meshes with a reverse driven gear 28 b attached to the first main shaft 11 so as to be rotatable relative to the reverse shaft 17.
- the reverse drive gear 28a constitutes the reverse gear train 28 together with the reverse driven gear 28b.
- a reverse shifter 53 for connecting or releasing the reverse shaft 17 and the reverse drive gear 28a is provided on the opposite side of the reverse drive gear 28a from the engine 6 side.
- the first shifter 51, the second shifter 52, and the reverse shifter 53 use a clutch mechanism having a synchronizing mechanism (synchronizer mechanism) that matches the rotational speed of the shaft to be connected with the gear.
- a synchronizing mechanism synchronizer mechanism
- the transmission 20 configured as described above has an odd-numbered gear group consisting of a third speed drive gear 23a and a fifth speed drive gear 25a on the first main shaft 11, which is one of the two transmission shafts.
- a first gear group) and an even-stage gear group (first gear group) composed of a second-speed drive gear 22a and a fourth-speed drive gear 24a on the second intermediate shaft 16, which is the other of the two transmission shafts. 2 gear groups) are provided.
- the hybrid vehicle driving apparatus 1 is further provided with an air conditioner compressor 112 and an oil pump 122, and the oil pump 122 is arranged on the oil pump auxiliary machine shaft 19 arranged in parallel with the rotation axis A1 to E1. It is attached to the pump auxiliary machine shaft 19 so as to be integrally rotatable.
- An oil pump driven gear 28c meshing with the reverse drive gear 28a and an air conditioner drive gear 29a are attached to the oil pump auxiliary shaft 19 so as to be integrally rotatable, and the engine 6 that rotates the first main shaft 11 and // The power of the motor 7 is transmitted.
- the air conditioner compressor 112 is provided on the air conditioner auxiliary shaft 18 arranged in parallel with the rotation axes A1 to E1 via the air conditioner clutch 121.
- An air conditioner driven gear 29b to which power is transmitted from an air conditioner drive gear 29a via a chain 29c is attached to the air conditioner auxiliary shaft 18 so as to be integrally rotatable with the air conditioner auxiliary shaft 18, and an oil pump auxiliary shaft 19 is provided.
- the power of the engine 6 and / or the motor 7 is transmitted through an air conditioner transmission mechanism 29 including an air conditioner drive gear 29a, a chain 29c, and an air conditioner driven gear 29b.
- the air conditioner compressor 112 is configured such that power transmission can be interrupted by connecting and disconnecting the air conditioner clutch 121 by an air conditioner operating solenoid (not shown).
- the hybrid vehicle drive device 1 of the present embodiment has the following first to fifth transmission paths.
- the crankshaft 6a of the engine 6 includes the first main shaft 11, the planetary gear mechanism 30, the connecting shaft 13, and the third speed gear pair 23 (third speed drive gear 23a, first common use).
- This is a transmission path connected to the drive wheels DW and DW via the driven gear 23b), the counter shaft 14, the final gear 26a, the differential gear mechanism 8, and the drive shafts 9 and 9.
- the reduction gear ratio of the planetary gear mechanism 30 is set so that the engine torque transmitted to the drive wheels DW and DW via the first transmission path corresponds to the first speed. That is, the reduction ratio obtained by multiplying the reduction ratio of the planetary gear mechanism 30 and the reduction ratio of the third speed gear pair 23 is set to be equivalent to the first speed.
- the crankshaft 6a of the engine 6 has the second main shaft 12, the first idle gear train 27A (the idle drive gear 27a, the first idle driven gear 27b, the second idle driven gear 27c), the second 2 intermediate shaft 16, second speed gear pair 22 (second speed drive gear 22a, first shared driven gear 23b) or fourth speed gear pair 24 (fourth speed drive gear 24a, second shared driven gear) 24b), a transmission path connected to the drive wheels DW and DW via the counter shaft 14, the final gear 26a, the differential gear mechanism 8, and the drive shafts 9 and 9.
- the first idle gear train 27A the idle drive gear 27a, the first idle driven gear 27b, the second idle driven gear 27c
- the second 2 intermediate shaft 16 second speed gear pair 22 (second speed drive gear 22a, first shared driven gear 23b) or fourth speed gear pair 24 (fourth speed drive gear 24a, second shared driven gear) 24b
- a transmission path connected to the drive wheels DW and DW via the counter shaft 14, the final gear 26a, the differential gear mechanism 8, and the drive shafts 9 and
- the crankshaft 6a of the engine 6 is used for the first main shaft 11, the third speed gear pair 23 (the third speed drive gear 23a, the first shared driven gear 23b) or the fifth speed.
- the gear pair 25 (the fifth speed drive gear 25a and the second shared driven gear 24b)
- the counter shaft 14 the final gear 26a, the differential gear mechanism 8, and the drive shafts 9 and 9, without the planetary gear mechanism 30.
- the motor 7 is connected to the planetary gear mechanism 30 or the third speed gear pair 23 (third speed drive gear 23a, first shared driven gear 23b) or fifth speed gear pair 25 ( 5th speed drive gear 25a, second shared driven gear 24b), counter shaft 14, final gear 26a, differential gear mechanism 8, and drive shafts 9 and 9 are connected to drive wheels DW and DW. It is.
- crankshaft 6a of the engine 6 is connected to the second main shaft 12, the second idle gear train 27B (idle drive gear 27a, first idle driven gear 27b, third idle driven gear 27d), reverse Shaft 17, reverse gear train 28 (reverse drive gear 28a, reverse driven gear 28b), planetary gear mechanism 30, connecting shaft 13, third speed gear pair 23 (third speed drive gear 23a, first common use)
- This is a transmission path connected to the drive wheels DW and DW via the driven gear 23b), the counter shaft 14, the final gear 26a, the differential gear mechanism 8, and the drive shafts 9 and 9.
- the motor 7 is connected to a power control unit (hereinafter referred to as PDU) 2 that controls the operation thereof.
- PDU 2 is connected to a battery 3 that supplies power to the motor 7 or charges power from the motor 7.
- the motor 7 is driven by electric power supplied from the battery 3 via the PDU 2. Further, the motor 7 can perform regenerative power generation by rotation of the drive wheels DW and DW during deceleration traveling and power of the engine 6 to charge the battery 3 (energy recovery).
- the PDU 2 is connected to an electric control unit (hereinafter referred to as ECU) 5.
- ECU electric control unit
- An electronically controlled throttle (ETCS: Electronic Throttle Control System) 66 that electronically controls a throttle valve (not shown) is connected to the engine 6, and the throttle valve is directly controlled according to the throttle opening calculated by the ECU 5.
- the intake air amount of the engine 6 is controlled electronically.
- the ECU 5 is a control device for performing various controls of the entire vehicle, and is connected to a mode detection unit 55 and an accelerator pedal opening detection unit (AP) 56.
- AP accelerator pedal opening detection unit
- the ECU 5 includes an acceleration request, a braking request, an engine speed, a motor speed, a remaining capacity (SOC: StateSOof Charge) of the battery 3 and a temperature, information from the mode detector 55, an accelerator pedal opening detector The accelerator pedal opening information detected by 56, the rotational speeds of the first and second main shafts 11 and 12, the rotational speed of the counter shaft 14, etc., the vehicle speed, the gear position, the shift position, and the like are input.
- a signal for controlling the engine 6 a signal for controlling the PDU 2, a signal for controlling the motor 7, a signal indicating the power generation state / charge state / discharge state of the battery 3, the first and second shift shifters 51. 52, a signal for controlling the reverse shifter 53, a signal for controlling the engagement (lock) and release (neutral) of the brake mechanism 61, an output signal for controlling the engagement and release of the air conditioner clutch 121, and the like.
- the ECU 5 has a control map (Map) as shown in FIG. 3 in order to determine whether various controls can be performed according to the SOC of the battery 3, and basically based on this control map. , ENG start, idle stop, deceleration regeneration, ENG separation, running in EV mode, and whether or not the MOT rotation speed can be adjusted are determined.
- Map control map
- ENG start, idle stop, deceleration regeneration, ENG separation, running in EV mode, and whether or not the MOT rotation speed can be adjusted are determined.
- ⁇ executable
- ⁇ is prohibited
- ⁇ is conditional.
- the SOC is classified into four zones, C zone, B zone, A zone, and D zone, from the smallest to the largest, and the A zone is further divided into the AL zone, from the smallest SOC to the largest. It is classified into three zones, AM zone and AH zone, and it is divided into 6 zones in total. And in the D zone close to the maximum charge amount, deceleration regeneration and ENG disconnection are allowed under certain conditions, EV travel and idle stop are prohibited in the B zone and C zone, and the AM zone is controlled as the target charge amount. Yes.
- the hybrid vehicle drive device 1 configured as described above controls the connection and disconnection of the first and second clutches 41 and 42, and the first shifter 51, the second shifter 52, the brake mechanism 61, and the reverse drive By controlling the engagement position of the shifter 53, the engine 6 can perform the first to fifth speed traveling and the reverse traveling.
- the first clutch 41 In the first speed running, the first clutch 41 is engaged and the brake mechanism 61 is engaged, so that the driving force is transmitted to the drive wheels DW and DW via the first transmission path. In the second speed traveling, the driving force is transmitted to the drive wheels DW and DW via the second transmission path by engaging the second clutch 42 and in-gearing the second shifter shifter 52 at the second speed connection position. In the third speed running, the first clutch 41 is engaged and the first shifter 51 is in-geared at the third speed connection position, whereby the driving force is transmitted to the drive wheels DW and DW via the third transmission path. Is done.
- the driving force is transmitted to the drive wheels DW and DW through the second transmission path by in-gearing the second shifter shifter 52 at the fourth speed connecting position, and the fifth speed traveling is performed.
- the driving force is transmitted to the drive wheels DW and DW via the second transmission path by in-gearing the first shifter 51 at the fifth speed connection position.
- the second clutch 42 is engaged and the reverse shifter 53 is connected, whereby reverse travel is performed via the fifth transmission path.
- shift speeds are determined based on the required driving force of the vehicle calculated according to the accelerator opening detected by the accelerator pedal opening detector 56, the driving mode detected by the mode detector 55, the shift position, the vehicle speed, and the like. Based on this, it is switched by the ECU 5.
- the operating state of the engine 6 can be switched based on the required driving force of the vehicle.
- the engine 6 in the hybrid vehicle drive device 1 of the present embodiment is a V-type 6-cylinder engine and includes a variable valve timing mechanism (VT) 65 capable of cylinder deactivation operation.
- VT variable valve timing mechanism
- Each of the six cylinders has a structure that can be kept closed by the variable valve timing mechanism 65.
- a cam lift rocker arm (not shown) and a valve drive rocker arm that are driven integrally during operation for cylinders that the variable valve timing mechanism 65 deactivates in response to a command from the ECU 5.
- the intake valve and the exhaust valve (not shown) of the cylinder are maintained in a closed state.
- variable valve timing mechanism 65 controls the rocker arm for each cylinder according to the command from the ECU 5 based on the required driving force of the vehicle derived from the driver's operation of the accelerator pedal and the traveling state of the vehicle. By doing so, it is possible to switch between all-cylinder operation in which all six cylinders are deactivated, partially-cylinder operation in which some cylinders are deactivated, and all-cylinder operation in which all six cylinders are driven. Will be.
- the opening degree of the electronically controlled throttle is set based on the command of the ECU 5.
- the engine travel can be performed in a state in which the engine 6 is partially rested by the variable valve timing mechanism 65 by changing to the opening degree in the partially resting operation.
- the pumping loss can be reduced and the fuel consumption can be reduced, and the fuel consumption can be improved.
- the engine 6 is controlled to be partially rested and the opening degree of the electronically controlled throttle is increased as the required driving force increases. do it.
- the engine 6 is assisted by the output of the motor 7, The part-cylinder operation can be continued. Therefore, when the required driving force of the vehicle is smaller than the sum of the output when the engine 6 is partially cylinder-capped and the output of the motor 7, the ECU 5 causes the engine 6 to partially idle and the engine 6 Control is performed so that the motor 7 outputs the difference between the output when the cylinder 6 is partially rested and the required driving force.
- the engine 6 When the required driving force of the vehicle exceeds the sum of the output when the engine 6 is partially cylinder-capped and the output of the motor 7, the engine 6 is switched to all-cylinder operation and the electronic control throttle is opened. The degree is changed to the opening degree in all cylinder operation.
- the operating state of the engine 6 can be appropriately switched according to the required driving force of the vehicle, and the fuel efficiency can be improved.
- the engine 6 may be temporarily partially or fully deactivated. You can also.
- energy is not consumed by driving the engine 6 and friction can be reduced, so that a regenerative loss of energy can be reduced, so that more energy can be obtained by power generation.
- fuel consumption can be further improved, and quick braking force can be obtained.
- the first shifter 51 for shifting is in-geared with the third-speed drive gear 23a, for example.
- the rotor 72 is rotated to perform regenerative power generation. If the engine 6 is in a cylinder resting operation at this time, energy is not consumed by driving the engine 6, so that fuel efficiency can be improved, and more rapid braking force can be obtained.
- regenerative power generation can be performed while the second clutch 42 is engaged, it is possible to quickly return to the second speed travel when accelerating again.
- the motor 7 assists or regenerates by engaging the brake mechanism 61 while the engine is running or by preshifting the first and second shifter shifters 51 and 52.
- the engine 6 can be started by the motor 7 and the battery 3 can be charged even during idling. Further, the first and second clutches 41 and 42 can be disconnected and the EV 7 can be driven by the motor 7.
- the first speed EV travel mode in which the brake mechanism 61 is engaged to travel through the fourth transmission path and the first shifter 51 for shifting are in-gear at the third speed connection position.
- the third speed EV traveling mode that travels through the fourth transmission path, and the fifth speed EV that travels through the fourth transmission path by in-gearing the first shifter 51 at the fifth speed connection position is a driving mode.
- first speed EV traveling (1st EV mode) will be described with reference to FIG.
- the brake mechanism 61 is locked from the initial state (OWC lock ON).
- the sun gear 32 of the planetary gear mechanism 31 connected to the rotor 72 is rotated in the forward direction as shown in FIG.
- the first and second clutches 41 and 42 are disengaged, the power transmitted to the sun gear 32 is transmitted from the first main shaft 11 to the crankshaft 6a of the engine 6. It will never be done.
- the reverse travel in the 1st EV mode can be performed by driving the motor 7 in the reverse direction and applying the motor torque in the reverse direction.
- the first and second clutches 41 and 42 are normally disconnected, and the engine 6 is simply idling or stopped.
- the engine 6 is simply idling or stopped.
- the first clutch 41 or the second clutch 42 is engaged, and the first main shaft 11 or the second main shaft 12 and the crank shaft 6a It is necessary to adjust the rotation speed.
- the engine 6 is stopped, it is necessary to start the engine 6 in addition to fastening the first clutch 41 or the second clutch 42.
- the hybrid vehicle drive device 1 of the present embodiment when the driver requires quick responsiveness, it is possible to quickly switch from the EV mode to another travel mode that uses the driving force of the engine 6.
- the engine 6 is allowed to travel in the EV mode by performing all-cylinder operation while the first clutch 41 or the second clutch 42 is engaged.
- the traveling mode can be quickly switched only by switching the operation state of the engine 6 to the all-cylinder operation or the partially-cylinder operation. .
- FIG. 5 shows the case where the engine 6 is running in the 1st EV mode and the engine 6 is made to perform all cylinder resting operation with the first clutch 41 engaged.
- torque is transmitted from the sun gear 32 to the carrier 36 as the sun gear 32 of the planetary gear mechanism 31 rotates in the forward rotation direction by driving the motor 7, and the third speed It is transmitted to the drive wheels DW and DW via the fourth transmission path passing through the gear pair 23 for use.
- the sun gear 32 is directly connected to the crankshaft 6 a of the engine 6 via the first main shaft 11, and the crankshaft 6 a rotates together with the first main shaft 11.
- variable valve timing mechanism 65 causes the cam lift rocker arm (not shown) and the valve drive rocker arm. (Not shown) may be controlled to move together. According to the said structure, since the control of the rotation speed adjustment of the 1st main shaft 11 and the crankshaft 6a required when the 1st clutch 41 is fastened is unnecessary, the engine 6 can be driven rapidly.
- the hybrid vehicle drive device 1 of the present embodiment it is possible to quickly shift from the EV mode to the travel mode in which the engine 6 is driven, and to satisfy the driver's demand for responsiveness. . Further, in addition to the case where the quick response described above is required, stable traveling can be performed by quickly shifting from the EV mode to the traveling mode for driving the engine 6 in the following cases.
- FIG. 6 shows a case where the vehicle travels in the first EV mode, the second clutch 42 is engaged, and the engine 6 is fully cylinder-removed at the second speed.
- torque is transmitted from the sun gear 32 to the carrier 36 as the sun gear 32 of the planetary gear mechanism 31 rotates in the forward rotation direction by driving the motor 7, and the third speed It is transmitted to the drive wheels DW and DW via the fourth transmission path passing through the gear pair 23 for use.
- the second shifter shifter 52 is in-geared at the second-speed connection position (pre-shifted to the second speed), so that the second-speed drive gear 22a is accompanied by the rotation of the sun gear 32.
- the second intermediate shaft 16 rotate together.
- the second main shaft 12 rotates from the second idle driven gear 27c attached to the second intermediate shaft 16 via the first idle driven gear 27b and the idle drive gear 27a.
- the crankshaft 6 a rotates with the second main shaft 12.
- variable valve timing mechanism 65 causes the cam lift rocker arm (not shown) and the valve drive rocker arm. (Not shown) may be controlled to move together. According to this configuration, since it is not necessary to control the rotation speed adjustment of the second main shaft 12 and the crankshaft 6a that is required when the second clutch 42 is engaged, the engine 6 can be driven promptly at the next shift stage. Can do.
- FIG. 7 is a flowchart for explaining the operation of the hybrid vehicle drive device 1 of the present embodiment.
- the ECU 5 determines whether or not the required output D of the vehicle is smaller than the output Pr of the engine 6 when the engine 6 is partially cylinder-capped (step S11). If it is determined in step S11 that the required output D is less than the engine output Pr at the time of partial cylinder resting operation, then the ECU 5 is currently traveling in the EV mode or is capable of traveling in the EV mode. Is determined (step S12). Whether the vehicle can travel in the EV mode is determined by the ECU 5 based on the required output D of the vehicle, the SOC of the battery 3, the temperature, and the like. If it is determined in step S12 that the vehicle is currently traveling in the EV mode or is capable of traveling in the EV mode, the ECU 5 performs an EV mode cylinder deactivation determination (step S13).
- FIG. 8 is a flowchart for explaining EV mode cylinder deactivation determination processing.
- the ECU 5 determines whether or not the sport mode is currently selected (step S21). When it is determined in step S21 that the sport mode is not selected, the ECU 5 next determines whether or not the paddle shift is currently selected (step S22). If it is determined in step S22 that the paddle shift is not selected, the ECU 5 determines whether or not the vehicle is currently in regenerative travel (step S23). When it is determined in step S23 that the vehicle is not regeneratively traveling, the ECU 5 determines whether the vehicle is currently traveling (cruising traveling) with the accelerator pedal being depressed (step S24). If it is determined in step S24 that the vehicle is not cruising, the ECU 5 determines whether the vehicle is currently traveling (inertia traveling) only by the inertia of the vehicle without stepping on the accelerator pedal (step S25). .
- step S25 If it is determined in step S25 that the vehicle is not traveling inertia, the ECU 5 determines that the cylinder deactivation is not necessary, disconnects the first and second clutches 41 and 42, and uses the driving force of the motor 7 to drive the EV mode. (Step S26), and the process ends.
- step S27 If it is determined that any one of the determinations in steps S21 to S26 is applicable, it is considered that the responsiveness of the engine 6 is required. Therefore, the ECU 5 determines that the cylinder deactivation is necessary, and The engine 6 is fully cylinder-cleaved while the first clutch 41 or the second clutch 42 is engaged, and is controlled to run in the EV mode by the driving force of the motor 7 (step S27), and the process ends.
- step S12 when it is determined in step S12 that the vehicle is not traveling in the EV mode and is not capable of traveling in the EV mode, the ECU 5 controls the engine 6 to perform a part-cylinder operation. (Step S14), the process ends.
- step S11 If it is determined in step S11 that the required output D is equal to or greater than the engine output Pr during partial cylinder resting operation, that is, if it is determined that D ⁇ Pr, the ECU 5 next requests It is determined whether or not the output D is smaller than the sum of the engine output Pr at the time of partial cylinder rest operation and the Pm of the motor 7, that is, whether D ⁇ Pr + Pm is satisfied (step S15). If it is determined in step S15 that D ⁇ Pr + Pm, the ECU 5 controls the engine 6 so as to perform a partial cylinder rest operation, and calculates a difference between the requested output and the output of the engine 6 in the partial cylinder rest operation. Control is performed so that the motor 7 outputs the signal (step S16), and the process ends. Therefore, in this case, the engine 6 that is partially rested is assisted by the motor 7 and travels.
- step S15 If it is determined in step S15 that the required output D is greater than or equal to the sum of the engine output Pr and the motor 7 during partial cylinder resting operation, that is, if it is determined that D ⁇ Pr + Pm, The ECU 5 controls the engine 6 to operate all cylinders (step S17), and the process ends.
- the hybrid vehicle drive device 1 of the present embodiment when the required drive force of the vehicle is smaller than the drive force of the engine 6 in the cylinderless operation, the engine 6 is turned on as necessary. Since the cylinder can be rested, the fuel consumption can be improved and the engine 6 can be driven quickly when the driving force of the engine 6 is required. In particular, when selecting a paddle shift or a sport mode that requires fast responsiveness, the engine 6 can be re-driven quickly. Further, even when kickdown gear shifting or tip-in gear shifting is performed, stable running can be performed with good responsiveness without causing a shock. Further, since the energy regeneration loss can be reduced, the fuel consumption can be further improved, and the engine 6 can be re-driven quickly. Furthermore, since the operating state of the engine 6 can be switched according to the required driving force, the fuel consumption can be further improved.
- determining whether or not cylinder deactivation is necessary in addition to considering the above-described conditions, information such as road conditions obtained from a navigation system (not shown) may be considered. If it is predicted that the engine 6 needs to be started early based on these pieces of information, it can be determined that cylinder deactivation is necessary. According to such a configuration, even if it becomes necessary to actually drive the engine 6 and travel after that, the engine 6 can be re-driven promptly.
- the gear position can be changed as follows. For example, if the engine 6 is fully cylinder-removed and the vehicle speed is increased while traveling in the EV mode, a pre-shift is performed to an even number above the current gear and the second clutch 42 is engaged. Next, when the engine 6 is driven, control is performed so that the engine 6 can be operated at the upper gear. As a result, the engine 6 can be re-driven at the next shift speed.
- the rotational speed of the motor 7 may increase.
- the gear is shifted to the upper even gear.
- all cylinder resting operation is being performed and the required driving force is large, after switching to an even number and then shifting to an odd number, or once releasing torque with an AMT shift, for example from 3rd to 5th And shift.
- the motor 7 is switched to an even number in order to reduce the rotation speed, and after waiting for an odd number of rotations to be allowed, the speed is changed to an odd number again. This can prevent the motor 7 from over-rotating.
- the BSFC (Net Fuel Consumption) bottom operation output during all cylinder operation or partial cylinder operation is considered.
- the BSFC bottom operation output during all-cylinder operation or partial rest-cylinder operation means output at an operating point at which the fuel consumption is minimized during all-cylinder operation or part-cylinder operation. .
- FIG. 9 is a flowchart for explaining the operation of the hybrid vehicle drive device 1 according to this modification.
- the ECU 5 compares the BSFC bottom operation output Pb during all-cylinder operation with the required output D of the vehicle (step S51). If it is determined in step S51 that D> Pb, the ECU 5 determines the current SOC of the battery 3 (step S52). If it is determined in step S52 that the SOC of the battery 3 indicates a value equal to or greater than the A zone (see FIG. 3), the ECU 5 controls the engine 6 to operate all cylinders, The difference from the BSFC bottom operation output Pb during the cylinder operation is controlled to be output by the motor 7 (step S53), and the process ends.
- the all-cylinder engine 6 is assisted by the motor 7 and travels.
- the engine 6 is operated at an operating point at which the fuel consumption is minimized, so that the fuel consumption is minimized and the fuel consumption is reduced. Can be improved. If it is determined in step S52 that the SOC of the battery 3 indicates a value less than the A zone (see FIG. 3), the ECU 5 controls the engine 6 to operate all cylinders (step S54). finish.
- step S51 If it is determined in step S51 that D ⁇ Pb, the ECU 5 compares the BSFC bottom operation output Pb during all-cylinder operation with the required output D of the vehicle again (step S55). If it is determined in step S55 that the difference between the BSFC bottom operation output Pb during all-cylinder operation and the required output D of the vehicle is less than the first predetermined value, that is, the required output D and the BSFC bottom during all-cylinder operation.
- the engine 6 is controlled to operate in all cylinders (step S56), and the process ends. In this case, since the engine 6 is operated at an operating point where the fuel consumption is minimized, the fuel consumption can be minimized and the fuel consumption can be improved.
- step S55 If it is determined in step S55 that the difference between the BSFC bottom operation output Pb during all-cylinder operation and the required output D of the vehicle is equal to or greater than the first predetermined value and D ⁇ Pb, the ECU 5 The BSFC bottom operation output Pb is further compared with the required output D of the vehicle (step S57). Specifically, in step S57, whether or not the difference between the BSFC bottom operation output Pb during the all-cylinder operation and the required output D of the vehicle is greater than or equal to a second predetermined value that is greater than the first predetermined value, that is, D ⁇ Whether or not Pb is determined.
- D ⁇ Pb is when the required output of the vehicle is extremely low and nearly zero, or when a braking force is required by stepping on a brake (not shown).
- step S57 it is determined that the difference between the BSFC bottom operation output Pb during all-cylinder operation and the required output D of the vehicle is equal to or greater than a second predetermined value that is greater than the first predetermined value, and D ⁇ Pb. If so, the ECU 5 determines the current SOC of the battery 3 (step S58).
- step S58 If it is determined in step S58 that the SOC of the battery 3 indicates a value equal to or higher than the A zone, it is possible to travel in the EV mode (see FIG. 3), so the ECU 5 performs the EV mode cylinder deactivation determination. (Step S59), the process ends. Since each process in the EV mode cylinder deactivation determination is the same as each process (FIG. 8) in the first embodiment, the description is omitted here.
- step S58 If it is determined in step S58 that the SOC of the battery 3 is less than the A zone, the vehicle cannot travel in the EV mode (see FIG. 3). In this case, the ECU 5 determines whether the responsiveness of the engine 6 is requested (step S60).
- the case where the responsiveness of the engine 6 is required is, for example, the case where the paddle shift is selected or the case where the sport mode is selected.
- step S60 If it is determined in step S60 that the responsiveness of the engine 6 is required, the ECU 5 controls the engine 6 to perform a cruising travel (cruise traveling) or an inertial traveling with all cylinders rested (step S61). The process ends. Thereby, braking force can be obtained.
- step S60 the ECU 5 disconnects the engine 6 by disconnecting the first and second clutches 41 and 42 and performs regenerative power generation with the motor 7. (Step S61), and the process ends. As a result, the battery 3 can be charged and a braking force can be obtained.
- step S57 If it is determined in step S57 that the difference between the BSFC bottom operation output Pb during all-cylinder operation and the required output D of the vehicle is greater than or equal to the first predetermined value and less than the second predetermined value, that is, D ⁇ Pb.
- the ECU 5 determines the current SOC of the battery 3 (step S63). If it is determined in step S63 that the SOC of the battery 3 shows a value equal to or higher than the A zone, it is possible to travel in the EV mode (see FIG. 3), so the ECU 5 performs the EV mode cylinder deactivation determination. (Step S59), the process ends. Since each process in the EV mode cylinder deactivation determination is the same as each process (FIG. 8) in the first embodiment, the description is omitted here.
- step S63 When it is determined in step S63 that the SOC of the battery 3 is less than the A zone, the vehicle cannot travel in the EV mode (see FIG. 3).
- the ECU 5 compares the BSFC bottom operation output Prb during the partial cylinder rest operation with the requested output D of the vehicle (step S64). If it is determined in step S64 that the difference between the BSFC bottom operation output Prb and the vehicle required output D during the partially rested operation is less than the first predetermined value, that is, the requested output D and the partially rested operation If it is determined that the BSFC bottom operation output Prb at the time is substantially equal (D ⁇ Prb), the engine 6 is controlled so as to be partially cylinder-removed (step S65), and the process ends. In this case, the engine 6 is partially rested at the operating point at which the fuel consumption is minimized, so that the fuel consumption can be improved by minimizing the fuel consumption.
- step S64 If it is determined in step S64 that the difference between the BSFC bottom operation output Prb during the partially rested operation and the required output D of the vehicle is equal to or greater than the first predetermined value and D ⁇ Prb is not satisfied, the ECU 5 Control is performed so as to travel by all-cylinder operation (step S66), and the process ends.
- an odd-numbered stage gear is arranged on the first main shaft 11 that is the input shaft to which the motor 7 of the dual clutch transmission is connected, and the input shaft to which the motor 7 is not connected is used.
- the even-numbered gear is arranged on a certain second intermediate shaft 16
- the present invention is not limited to this, and the even-numbered gear is arranged on the first main shaft 11, which is the input shaft to which the motor 7 is connected, and the motor 7 is not connected.
- An odd-numbered gear may be arranged on the second intermediate shaft 16 that is the input shaft.
- gears may be provided as sixth, eighth,...
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Abstract
Description
本実施形態のハイブリッド車両用駆動装置1は、図1に示すように、車両(図示せず)の駆動軸9,9を介して駆動輪DW,DW(被駆動部)を駆動するためのものであり、駆動源である内燃機関(以下「エンジン」という)6と、電動機(以下「モータ」という)7と、動力を駆動輪DW,DWに伝達するための変速機20と、を備えている。
ここで、第1共用従動ギヤ23bは、連結軸13に取り付けられた第3速用駆動ギヤ23aと噛合して第3速用駆動ギヤ23aと共に第3速用ギヤ対23を構成し、第2中間軸16に設けられた第2速用駆動ギヤ22aと噛合して第2速用駆動ギヤ22aと共に第2速用ギヤ対22を構成する。
第2共用従動ギヤ24bは、第1主軸11に設けられた第5速用駆動ギヤ25aと噛合して第5速用駆動ギヤ25aと共に第5速用ギヤ対25を構成し、第2中間軸16に設けられた第4速用駆動ギヤ24aと噛合して第4速用駆動ギヤ24aと共に第4速用ギヤ対24を構成する。
ファイナルギヤ26aは差動ギヤ機構8と噛合して、差動ギヤ機構8は、駆動軸9,9を介して駆動輪DW,DWに連結されている。従って、カウンタ軸14に伝達された動力はファイナルギヤ26aから差動ギヤ機構8、駆動軸9,9、駆動輪DW,DWへと出力される。
(1)第1伝達経路は、エンジン6のクランク軸6aが、第1主軸11、遊星歯車機構30、連結軸13、第3速用ギヤ対23(第3速用駆動ギヤ23a、第1共用従動ギヤ23b)、カウンタ軸14、ファイナルギヤ26a、差動ギヤ機構8、駆動軸9,9を介して、駆動輪DW,DWに連結される伝達経路である。ここで、遊星歯車機構30の減速比は、第1伝達経路を介して駆動輪DW,DWに伝達されるエンジントルクが第1速相当となるように設定されている。即ち、遊星歯車機構30の減速比と第3速用ギヤ対23の減速比をかけ合わせた減速比が第1速相当となるように設定されている。
1st EVモードでは、初期状態からブレーキ機構61をロック状態(OWC ロックON)にすることによりなされる。この状態で、モータ7を駆動(正転方向にトルクを印加)すると、図4(a)に示すように、ロータ72に接続された遊星歯車機構31のサンギヤ32が正転方向に回転する。このとき、図4(b)に示すように、第1及び第2クラッチ41、42が切断されているため、サンギヤ32に伝達された動力は第1主軸11からエンジン6のクランク軸6aに伝達されることはない。そして、ブレーキ機構61のロックがなされているため、モータトルクがサンギヤ32からキャリア36に減速して伝達され、第3速用ギヤ対23を通る第4伝達経路を介して駆動輪DW,DWに伝達される。
また、この1st EVモードでの後進走行は、モータ7を逆転方向に駆動し、逆転方向にモータトルクを印加することで行うことができる。
例えば、エンジン6を全休筒運転すると共にEVモードで走行中、車速が高くなった場合には、現在の変速段よりも上の偶数段へとプレシフトを行うと共に第2クラッチ42を締結することにより、次にエンジン6を駆動する際に上の変速段で運転できるように制御する。これにより、次の変速段でのエンジン6の再駆動を速やかに行うことができる。
本発明の変形例について、図9を参照して以下説明する。本変形例の構成に関し、上述した実施形態と同様の部分についてはその説明を省略する。
ステップS52で、バッテリ3のSOCがAゾーン(図3参照)未満の値を示すと判断される場合には、ECU5は、エンジン6を全筒運転するように制御し(ステップS54)、処理が終了する。
ステップS60で、エンジン6の応答性が要求されていないと判断された場合、ECU5は、第1,第2クラッチ41,42を切断することによりエンジン6を切り離すとともに、モータ7で回生発電を行うよう制御し(ステップS61)、処理が終了する。これにより、バッテリ3の充電を行うことが可能となるとともに、制動力を得ることができる。
例えば、前述した実施形態および変形例においては、デュアルクラッチ式変速機のモータ7が接続された入力軸である第1主軸11に奇数段ギヤを配置し、モータ7が接続されていない入力軸である第2中間軸16に偶数段ギヤを配置したが、これに限定されず、モータ7が接続された入力軸である第1主軸11に偶数段ギヤを配置し、モータ7が接続されていない入力軸である第2中間軸16に奇数段ギヤを配置してもよい。
3 バッテリ(蓄電器)
5 ECU
6 エンジン(内燃機関)
7 モータ(電動機)
11 第1主軸(第1入力軸)
14 カウンタ軸(出力軸)
16 第2中間軸(第2入力軸)
41 第1クラッチ(第1断接部)
42 第2クラッチ(第2断接部)
51 第1変速用シフター
52 第2変速用シフター
20 変速機
Claims (10)
- 全ての気筒を運転する全筒運転と少なくとも一部の気筒を休止して運転する休筒運転とを切替可能な内燃機関と、電動機と、を駆動源とするハイブリッド車両に用いられ、
前記電動機に電力を供給する蓄電器と、
前記内燃機関の出力軸及び前記電動機からの機械的動力を、前記電動機と係合する第1入力軸で受け、複数の変速段のいずれかを係合状態にして前記第1入力軸と駆動輪とを係合させることが可能な第1変速機構と、
前記内燃機関の出力軸からの機械的動力を第2入力軸で受け、複数の変速段のいずれかを係合状態にして前記第2入力軸と駆動輪とを係合させることが可能な第2変速機構と、
前記内燃機関の出力軸と前記第1入力軸とを係合させることが可能な第1断接部と、
前記内燃機関の出力軸と前記第2入力軸とを係合させることが可能な第2断接部と、を有する変速機を備えるハイブリッド車両用駆動装置であって、
前記電動機の駆動力のみにより前記第1入力軸を介してEVモードで走行可能であり、
車両の要求駆動力が前記内燃機関の休筒運転での駆動力よりも小さい場合に前記内燃機関の休筒運転の要否を判断する休筒運転要否判断部をさらに備え、
前記休筒運転要否判断部により休筒運転が不要と判断された場合、前記第1断接部および前記第2断接部を切断してEVモードで走行可能であり、
前記休筒運転要否判断部により休筒運転が必要と判断された場合、前記内燃機関を休筒運転すると共に、前記第1断接部および前記第2断接部の少なくとも一方を接続することを特徴とするハイブリッド車両用駆動装置。 - 前記休筒運転要否判断部は、パドルシフトが選択されている場合に、休筒運転が必要と判断することを特徴とする請求項1に記載のハイブリット車両用駆動装置。
- 前記休筒運転要否判断部は、スポーツモードが選択されている場合に、休筒運転が必要と判断することを特徴とする請求項1に記載のハイブリット車両用駆動装置。
- 前記休筒運転要否判断部は、前記電動機により回生発電を行う場合に、休筒運転が必要と判断することを特徴とする請求項1から3のいずれか1項に記載のハイブリット車両用駆動装置。
- 前記休筒運転要否判断部は、車両が巡航走行している場合に、休筒運転が必要と判断することを特徴とする請求項1から3のいずれか1項に記載のハイブリット車両用駆動装置。
- 前記休筒運転要否判断部は、車両が慣性走行している場合に、休筒運転が必要と判断することを特徴とする請求項1から5のいずれか1項に記載のハイブリッド車両用駆動装置。
- 前記第1断接部を接続したまま前記内燃機関を休筒運転すると共にEVモードで走行している時に、前記第2入力軸へのプレシフトを行うと共に前記第1断接部から前記第2断接部への切替を行うことを特徴とする請求項1から6のいずれか1項に記載のハイブリッド車両用駆動装置。
- カーナビゲーションシステムと連動する走行状態予測部を備え、
前記休筒運転要否判断部は、前記走行状態予測部によりEVモードから他の走行モードへの切替が予測される場合に、休筒運転が必要と判断することを特徴とする請求項1に記載のハイブリッド車両用駆動装置。 - 前記内燃機関の吸気量を制御可能な電子制御スロットルを備え、
車両の要求駆動力が前記内燃機関の休筒運転での駆動力よりも小さい場合には、前記内燃機関を休筒運転で運転すると共に、要求駆動力の増大に応じて前記電子制御スロットルの開度を増加させる制御を行い、
車両の要求駆動力が、前記内燃機関の休筒運転での駆動力よりも大きく、且つ、前記内燃機関の休筒運転での駆動力と前記電動機により出力可能な駆動力との和より小さい場合には、前記内燃機関を休筒運転で運転すると共に、前記電動機に前記要求駆動力と前記内燃機関の休筒運転での駆動力との差分を出力させる制御を行い、
車両の要求駆動力が、前記内燃機関の休筒運転での駆動力と前記電動機により出力可能な駆動力との和より大きい場合には、前記内燃機関を休筒運転から全筒運転に切り替えると共に、前記電子制御スロットルの開度を全筒運転における開度に変更するよう制御を行うことを特徴とする請求項1に記載のハイブリッド車両用駆動装置。 - 前記休筒運転は、一部の気筒のみを休止して運転する一部休筒運転と、全ての気筒を休止して運転する全休筒運転と、を含み、
車両の要求駆動力が前記内燃機関の全筒運転での駆動力よりも小さく、前記内燃機関の一部休筒運転によりBSFCボトム運転が可能である場合には、前記内燃機関を一部休筒運転するよう制御し、
車両の要求駆動力が前記内燃機関の全筒運転での駆動力よりも小さく、その差が所定値以上である場合には、前記蓄電器の残容量および前記要求駆動力に応じて、EVモードで走行するか、前記内燃機関を全休筒運転するよう制御することを特徴とする請求項1に記載のハイブリッド車両用駆動装置。
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JP2014201308A (ja) * | 2013-04-03 | 2014-10-27 | ドクター エンジニール ハー ツェー エフ ポルシェ アクチエンゲゼルシャフトDr. Ing. h.c.F. Porsche Aktiengesellschaft | 内燃機関と電気機械とを有するハイブリッド車 |
US9809106B2 (en) | 2013-04-03 | 2017-11-07 | Dr. Ing. H.C.F. Porsche Aktiengesellschaft | Hybrid vehicle with internal combustion engine and electric machine |
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DE112011102037T5 (de) | 2013-05-02 |
BR112012031741A2 (pt) | 2016-11-01 |
US20130096761A1 (en) | 2013-04-18 |
US20150336561A1 (en) | 2015-11-26 |
JPWO2011158882A1 (ja) | 2013-08-19 |
US9919701B2 (en) | 2018-03-20 |
CN102939214A (zh) | 2013-02-20 |
CN102939214B (zh) | 2015-08-19 |
JP5696143B2 (ja) | 2015-04-08 |
JP2015155296A (ja) | 2015-08-27 |
RU2013101599A (ru) | 2014-07-20 |
US9073546B2 (en) | 2015-07-07 |
RU2534465C2 (ru) | 2014-11-27 |
JP6101718B2 (ja) | 2017-03-22 |
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