JP2011037329A - Power train of vehicle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce an increase amount of cost of the driving source of an oil pump for generating hydraulic pressure while an engine is stopped. <P>SOLUTION: A hybrid system 300 includes a first MG 311 connected to a sun gear 322 of a planetary gear 320, a second MG 312 connected to a ring gear 328, the engine 100 connected to a carrier 326, a CO clutch 330 for connecting the first MG 311 and the sun gear 322 in an engaged state and shutting off the first MG 311 and the sun gear 322 in a release state, a first oil pump 910 connected to the first MG 311 via a one-way clutch, and a second oil pump 920 connected to the second MG 312 and the ring gear 328. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a power train of a vehicle, and more particularly to a power train provided with an oil pump that generates hydraulic pressure necessary for operation of the power train when the engine is stopped.

  Conventionally, a hybrid vehicle in which a motor is mounted as a drive source in addition to an engine is known. In a hybrid vehicle, the engine is stopped when the vehicle is stopped, for example, in order to reduce fuel consumption. Further, even during EV travel that travels using only the driving force output from the motor, the engine is stopped unless there is a special request such as warming up the catalyst.

  By the way, the hydraulic pressure required for the operation of the clutch and brake of the transmission is generated by, for example, an oil pump driven by an engine. Therefore, when the engine is stopped, oil pressure cannot be generated using the oil pump. Therefore, as described in JP-A-11-287316 (Patent Document 1), in addition to an oil pump driven by an engine, an oil pump driven by a motor is mounted on the vehicle.

JP-A-11-287316

  However, when a dedicated motor for driving an oil pump used when the engine is stopped is newly installed, the cost of the vehicle can be increased by the motor and the control device that controls the motor.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a vehicle power train that can reduce the amount of cost increase required for a device that generates hydraulic pressure. That is.

  A power train for a vehicle according to a first aspect is a power train for a vehicle on which a differential device including a first rotating element, a second rotating element coupled to a wheel, and a third rotating element is mounted. The power train connects the first rotating electrical machine and the first rotating electrical machine and the first rotating element in the engaged state, and shuts off the first rotating electrical machine and the first rotating element in the released state. An engagement element, a second rotating electric machine connected to the second rotating element, an engine connected to the third rotating element, a one-way clutch connected to the first rotating electric machine, and a one-way clutch A first oil pump coupled to the first rotating electrical machine, and a second oil pump coupled to the second rotating electrical machine and the second rotating element.

  According to this configuration, the engine is assisted by the driving force output from the second rotating electrical machine connected to the second rotating element, or only the driving force output from the second rotating electrical machine is used. And can drive. While the vehicle is traveling, hydraulic pressure can be generated using the second rotating electric machine and the second oil pump connected to the second rotating element. If the engaging element is in the engaged state, the engine can be cranked for starting the engine by operating the first rotating electrical machine as a motor. Further, if the engagement element is in the engaged state during the operation of the engine, the first rotating electrical machine can be operated as a generator using the driving force output from the engine. If the engagement element is in the released state while the engine is stopped, the first oil pump can generate hydraulic pressure by operating the first rotating electrical machine as a motor. However, when the first rotating electrical machine rotates in the reverse direction, the oil can flow backward by the first oil pump. Therefore, the first oil pump is connected to the first rotating electric machine via the one-way clutch. This prevents the first oil pump from being driven when the first rotating electrical machine rotates in the reverse direction. Therefore, backflow of oil can be prevented. Therefore, adverse effects when the first rotating electrical machine is used as a drive source for the first oil pump can be reduced. Therefore, the first rotary electric machine used for power generation and engine start is used as the drive source for the first oil pump without newly providing a drive source for the first oil pump that generates hydraulic pressure while the engine is stopped. be able to. Therefore, it is possible to provide a vehicle power train that can reduce an increase in cost required for a device that generates hydraulic pressure.

  A vehicle power train according to a second aspect of the present invention is a vehicle power train on which a differential device including a first rotating element, a second rotating element coupled to a wheel, and a third rotating element is mounted. The power train connects the first rotating electrical machine and the first rotating electrical machine and the first rotating element in the engaged state, and shuts off the first rotating electrical machine and the first rotating element in the released state. An engagement element, a second rotating electric machine connected to the second rotating element, an engine connected to the third rotating element, an output shaft of the first rotating electric machine connected to the first rotating electric machine Oil that has been sucked from the suction port is discharged from the discharge port when rotating in the first direction, and discharged when the output shaft of the first rotating electrical machine rotates in the second direction opposite to the first direction. A first oil pump that discharges oil sucked from the outlet from the suction port, a switching mechanism that switches between an oil passage connected to the suction port and an oil passage connected to the discharge port, a second rotating electrical machine, and a second And a second oil pump coupled to the rotating element.

  According to this configuration, the engine is assisted by the driving force output from the second rotating electrical machine connected to the second rotating element, or only the driving force output from the second rotating electrical machine is used. And can drive. While the vehicle is traveling, hydraulic pressure can be generated using the second rotating electric machine and the second oil pump connected to the second rotating element. If the engaging element is in the engaged state, the engine can be cranked for starting the engine by operating the first rotating electrical machine as a motor. Further, if the engagement element is in the engaged state during the operation of the engine, the first rotating electrical machine can be operated as a generator using the driving force output from the engine. If the engagement element is in the released state while the engine is stopped, the first oil pump can generate hydraulic pressure by operating the first rotating electrical machine as a motor. However, when the first rotating electrical machine is reversed, the oil can flow backward by the first oil pump. Therefore, when the output shaft of the first rotating electrical machine rotates in the first direction and when the output shaft of the first rotating electrical machine rotates in the second direction opposite to the first direction, The oil passage connected to the suction port and the oil passage connected to the discharge port are switched by the switching mechanism. Thereby, when the 1st rotary electric machine reversely rotates, the backflow of the oil by a 1st oil pump can be prevented. Therefore, adverse effects when the first rotating electrical machine is used as a drive source for the first oil pump can be reduced. Therefore, the first rotary electric machine used for power generation and engine start is used as the drive source for the first oil pump without newly providing a drive source for the first oil pump that generates hydraulic pressure while the engine is stopped. be able to. Therefore, it is possible to provide a vehicle power train that can reduce an increase in cost required for a device that generates hydraulic pressure.

  In addition to the configuration of the second invention, the power train of the vehicle according to the third invention is a first oil passage connected to a storage section for storing oil, and a second connected to a device to which oil is supplied. The oil passage is further provided. When the output shaft of the first rotating electrical machine rotates in the first direction, the switching mechanism connects the first oil path to the suction port and connects the second oil path to the discharge port. When the output shaft of the rotating electrical machine rotates in the second direction, the second oil passage is connected to the suction port and the first oil passage is connected to the discharge port.

  According to this configuration, even when the output shaft of the first rotating electrical machine rotates in the reverse direction, hydraulic pressure can be supplied from the first oil pump to the device.

  In the vehicle power train according to the fourth invention, in addition to the configuration of any one of the first to third inventions, the first rotating electrical machine drives the first oil pump in a state where the engagement element is released. Operates to

  According to this configuration, for example, if the engagement element is released while the engine is stopped, the first oil pump can generate hydraulic pressure by operating the first rotating electrical machine as a motor.

  In the power train of the vehicle according to the fifth aspect of the invention, in addition to the configuration of the fourth aspect of the invention, the engaging element operates so as to be in the released state when the engine is stopped.

  According to this configuration, the engaging element is released while the engine is stopped. Therefore, hydraulic pressure can be generated by the first oil pump by operating the first rotating electric machine as a motor while the engine is stopped.

  In the power train of the vehicle according to the sixth aspect of the invention, in addition to the configuration of the fifth aspect of the invention, the engaging element operates so as to be in the released state when the engine is stopped and the vehicle is stopped.

  According to this configuration, even when the hydraulic pressure cannot be generated by the second oil pump, the hydraulic pressure is generated by the first oil pump by operating the first rotating electrical machine as a motor while the engine is stopped. Can do.

  In the power train of the vehicle according to the seventh invention, in addition to the configuration of the fifth invention, the engagement element is such that the engine stops and the vehicle travels using the driving force output from the second rotating electrical machine. Operates to be released in the middle state.

  According to this configuration, hydraulic pressure can be generated by the first oil pump in addition to the second oil pump.

  In the power train of the vehicle according to the eighth invention, in addition to the configuration of any one of the first to seventh inventions, the differential device is a planetary gear. The first rotating element is a sun gear. The second rotating element is a ring gear. The third rotating element is a carrier.

  According to this configuration, in a vehicle in which the planetary gear is mounted as a differential device, it is used for power generation and engine start without newly providing a first oil pump drive source that generates hydraulic pressure while the engine is stopped. The first rotating electrical machine can be used as a drive source for the first oil pump.

It is a schematic block diagram which shows the power train of a hybrid vehicle. It is a figure which shows the hybrid system of 1st Embodiment. It is a figure which shows the alignment chart of a power split device. It is a figure which shows a transmission. It is a figure which shows an operation | movement table. It is a figure which shows a shift map. It is a figure which shows the hydraulic circuit of 1st Embodiment. It is a figure (the 1) which shows an alignment chart in the state in which an engine is drive | operating. It is a figure (the 2) which shows an alignment chart in the state in which an engine is drive | operating. It is a figure which shows the collinear diagram of the state which the output shaft of 1st MG of the hybrid system of 1st Embodiment reversely rotated. It is a figure which shows the alignment chart of the state which the engine and the vehicle stopped. It is a figure which shows the alignment chart at the time of starting an engine in the state which the vehicle stopped. It is a figure which shows the alignment chart in EV driving | running | working which the engine stopped. It is a figure which shows the alignment chart at the time of starting an engine during EV driving | running | working. It is a figure which shows the hybrid system in 2nd Embodiment. It is FIG. (1) which shows the hydraulic circuit of 2nd Embodiment. FIG. 6 is a (second) diagram illustrating a hydraulic circuit according to a second embodiment. It is a figure which shows the alignment chart of the state which the output shaft of 1st MG of the hybrid system of 2nd Embodiment rotated reversely.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following description, the same parts are denoted by the same reference numerals. Their names and functions are also the same. Therefore, detailed description thereof will not be repeated.

<First Embodiment>
A hybrid vehicle will be described with reference to FIG. This hybrid vehicle is an FR (Front engine Rear drive) vehicle. A vehicle other than FR may be used.

  The power train of the hybrid vehicle includes an engine 100, a hybrid system 300, a transmission 400, a propeller shaft 500, a differential gear 600, and a rear wheel 700. The power train is controlled by an ECU (Electronic Control Unit) 800. ECU 800 may be divided into a plurality of ECUs. Further, the transmission 400 may not be provided.

  Engine 100 is an internal combustion engine that burns a mixture of fuel and air injected from injector 102 in a combustion chamber of a cylinder. The piston in the cylinder is pushed down by the combustion, and the crankshaft is rotated.

  Hybrid system 300 is coupled to engine 100. Transmission 400 is coupled to hybrid system 300. The driving force output from the transmission 400 is transmitted to the left and right rear wheels 700 via the propeller shaft 500 and the differential gear 600.

  The ECU 800 includes a position switch 806 for the shift lever 804, an accelerator opening sensor 810 for the accelerator pedal 808, a depression force sensor 814 for the brake pedal 812, a throttle opening sensor 818 for the electronic throttle valve 816, and an engine speed sensor 820. The input shaft speed sensor 822, the output shaft speed sensor 824, the oil temperature sensor 826, and the water temperature sensor 828 are connected via a harness or the like.

  The position (position) of shift lever 804 is detected by position switch 806, and a signal representing the detection result is transmitted to ECU 800. Corresponding to the position of the shift lever 804, a shift in the transmission 400 is automatically performed.

  Accelerator opening sensor 810 detects the opening of accelerator pedal 808 and transmits a signal representing the detection result to ECU 800. The pedaling force sensor 814 detects the pedaling force of the brake pedal 812 (the force with which the driver steps on the brake pedal 812), and transmits a signal representing the detection result to the ECU 800.

  The throttle opening sensor 818 detects the opening of the electronic throttle valve 816 whose opening is adjusted by the actuator, and transmits a signal indicating the detection result to the ECU 800. Electronic throttle valve 816 adjusts the amount of air taken into engine 100 (engine 100 output).

  Instead of or in addition to the electronic throttle valve 816, the amount of air taken into the engine 100 can be reduced by changing the lift amount of the intake valve (not shown) or the exhaust valve (not shown) and the opening / closing phase. You may make it adjust.

  Engine rotation speed sensor 820 detects the rotation speed of the output shaft (crankshaft) of engine 100 and transmits a signal representing the detection result to ECU 800. Input shaft rotational speed sensor 822 detects input shaft rotational speed NI of transmission 400 and transmits a signal representing the detection result to ECU 800. Output shaft rotational speed sensor 824 detects output shaft rotational speed NO of transmission 400 and transmits a signal representing the detection result to ECU 800.

  Oil temperature sensor 826 detects the temperature (oil temperature) of oil (ATF: Automatic Transmission Fluid) used for operation and lubrication of hybrid system 300 and transmission 400, and transmits a signal representing the detection result to ECU 800.

  Water temperature sensor 828 detects the temperature (water temperature) of cooling water for engine 100 and transmits a signal representing the detection result to ECU 800.

  The ECU 800 includes a position switch 806, an accelerator opening sensor 810, a pedaling force sensor 814, a throttle opening sensor 818, an engine speed sensor 820, an input shaft speed sensor 822, an output shaft speed sensor 824, an oil temperature sensor 826, and a water temperature sensor. Based on the signal sent from 828 or the like, the map stored in the ROM 802 and the program, the devices are controlled so that the vehicle is in a desired running state.

  The hybrid system 300 will be further described with reference to FIG. The hybrid system 300 is disposed on a common shaft center in a case 202 as a non-rotating member attached to a vehicle body, and is connected to an engine 100 via a torsional damper 204 and an input shaft 206. It includes a power split mechanism 310 that is connected, and a transmission member 208 that connects power split mechanism 310 and transmission 400. The driving force output from the hybrid system 300 is transmitted to the rear wheel 700 via the output shaft 210 of the transmission 400.

  Note that the hybrid system 300 and the transmission 400 are configured symmetrically with respect to the axis thereof, and therefore, the lower side is omitted in the portion representing the hybrid system 300 and the transmission 400 in FIG. The same applies to the following description.

  Power split device 310 includes planetary gear 320. Planetary gear 320 includes a sun gear 322, a pinion gear 324, a carrier 326 that supports the pinion gear 324 so as to rotate and revolve, and a ring gear 328 that meshes with the sun gear 322 via the pinion gear 324.

The carrier 326 is connected to the input shaft 206, that is, the engine 100. The sun gear 322 is connected to a rotor of a first MG (Motor Generator) 311. Ring gear 328 is second
It is connected to the rotor of MG 312 and the transmission member 208. The second MG 312 may be provided in any part constituting the power transmission path from the transmission member 208 to the rear wheel 700 that is the drive wheel.

  Power split device 310 functions as a differential device by relatively rotating sun gear 322, carrier 326, and ring gear 328. As shown in FIG. 3, the rotational speed of the sun gear 322, the rotational speed of the carrier 326, and the rotational speed of the ring gear 328 are in a relationship connected by a straight line in the nomographic chart. Due to the differential function of power split device 310, the driving force output from engine 100 is distributed to sun gear 322 and ring gear 328.

  Returning to FIG. 2, the first MG 311 is driven as a generator by the driving force distributed to the sun gear 322. The electric power generated by the first MG 311 is supplied to the second MG 312 or charged in a battery (not shown).

  The power split mechanism 310 functions as a continuously variable transmission by causing the first MG 311 to generate electric power using the distributed driving force, or causing the second MG 312 to rotationally drive using electric power generated by the first MG 311.

  First MG 311 and second MG 312 are three-phase AC rotating electric machines. First MG 311 and second MG 312 are controlled so as to satisfy the target output torque of transmission 400 calculated from, for example, the accelerator opening and the vehicle speed, and to realize optimal fuel consumption in engine 100.

  A C0 clutch 330 is provided between first MG 311 and sun gear 322. C0 clutch 330 connects first MG 311 and sun gear 322 in the engaged state, and disconnects first MG 311 and sun gear 322 in the released state.

  Between the first MG 311 and the C0 clutch 330, a one-way clutch 900 and a first oil pump 910 are provided. One-way clutch 900 is connected to first MG 311. First oil pump 910 is connected to first MG 311 via one-way clutch 900.

  First oil pump 910 is driven by first MG 311. When the first MG 311 rotor rotates, the first oil pump 910 generates hydraulic pressure. Even if the sun gear 322 rotates when the C0 clutch 330 is in the engaged state, the first oil pump 910 can generate hydraulic pressure.

  However, the one-way clutch 900 transmits torque to the first oil pump 910 in the direction in which the output shaft of the first oil pump 910 rotates in the forward direction, while the torque is transmitted in the direction in which the output shaft of the first oil pump 910 rotates in the reverse direction. 1 Not transmitted to oil pump 910.

  A second oil pump 920 is provided between second MG 312 and transmission 400. Second oil pump 920 is connected to second MG 312, ring gear 328 and transmission member 208. When the rotor of second MG 312 rotates, that is, when ring gear 328 rotates, second oil pump 920 generates hydraulic pressure.

  The transmission 400 will be described with reference to FIG. The transmission 400 is not limited to the one described below, and various other types of transmission 400 may be used. A continuously variable transmission or the like may be used instead of the transmission 400.

  Transmission 400 includes three planetary gears 411 to 413 of a single pinion type, and five friction engagement elements of C1 clutch 421, C2 clutch 422, B1 brake 431, B2 brake 432, and B3 brake 433.

  By engaging the friction engagement elements of the transmission 400 in the combinations shown in the operation table shown in FIG. 5, the five forward gears from the first gear to the fifth gear are formed in the transmission 400.

  The frictional engagement element that is engaged when forming the fourth gear is the same as the frictional engagement element that is engaged when forming the fifth gear. That is, the transmission gear ratio in transmission 400 is the same between the fourth gear and the fifth gear. However, the gear ratio of power split mechanism 310 is different.

  When the 4-speed gear stage is formed, the power split mechanism 310 allows the first MG 311 to rotate, the engine speed and the transmission member 208 become the same, and the gear ratio becomes “1”. On the other hand, when forming the fifth gear, the rotational speed of the first MG 311 is set to “0”, so that the rotational speed of the transmission member 208 is made higher than the engine rotational speed, and the transmission ratio is set to “1”. Is also made smaller.

  Shifting in transmission 400 is controlled based on, for example, a shift diagram shown in FIG. The shift map in the present embodiment is determined by using the target output torque calculated from the accelerator opening and the vehicle speed, and the vehicle speed as parameters. Note that the parameters of the shift map are not limited to these.

The solid line in FIG. 6 is an upshift line, and the broken line is a downshift line. In FIG. 6, a region surrounded by a one-dot chain line indicates a region where EV traveling is performed using only the driving force of second MG 312 without using the driving force of engine 100. During EV traveling, the engine 100 is stopped unless there is a request for warming up a catalyst (not shown).

  In the region surrounded by the one-dot chain line in FIG. 6, only the driving force output from the engine 100 when the engine 100 is operated, or the driving force output from the second MG 312 in addition to the driving force output from the engine 100 is obtained. The used HV traveling is performed.

  The C1 clutch 421, the C2 clutch 422, the B1 brake 431, the B2 brake 432, and the B3 brake 433 of the transmission 400 are operated by hydraulic pressure. The C0 clutch 330 of the hybrid system 300 is also operated by hydraulic pressure.

  As shown in FIG. 7, in the hybrid vehicle, the hydraulic pressure generated by the first oil pump 910 and the second oil pump 920 is adjusted to the line pressure, and the hydraulic pressure adjusted using the line pressure as the original pressure is the C0 clutch 330. , A hydraulic circuit 930 that supplies and discharges oil for lubrication to appropriate portions is provided to the C1 clutch 421, the C2 clutch 422, the B1 brake 431, the B2 brake 432, and the B3 brake 433.

  The operating states of the C0 clutch 330, the C1 clutch 421, the C2 clutch 422, the B1 brake 431, the B2 brake 432, and the B3 brake 433 are controlled by the ECU 800 using a hydraulic circuit 930.

  As shown in FIG. 7, the first oil pump 910 is provided with a suction port 912 and a discharge port 914. When the first oil pump 910 rotates forward, the oil sucked from the suction port 912 is discharged from the discharge port 914. When the first oil pump 910 rotates in the reverse direction, the oil sucked from the discharge port 914 can be discharged from the suction port 912.

  The second oil pump 920 is provided with a suction port 922 and a discharge port 924. When the second oil pump 920 rotates forward, the oil sucked from the suction port 922 is discharged from the discharge port 924. When the second oil pump 920 rotates in the reverse direction, the oil sucked from the discharge port 924 can be discharged from the suction port 922.

  The discharge ports 914 and 924 of the oil pumps 910 and 920 are provided with check valves 912 and 922 that open at the discharge pressure of the oil pumps 910 and 920 and close in the opposite direction, and a hydraulic circuit 930. On the other hand, these oil pumps 910 and 920 are connected in parallel to each other.

  Each oil pump 910, 920 sucks the oil stored in the oil pan 940 and outputs the hydraulic pressure.

  Hereinafter, operating states of the C0 clutch 330, the first oil pump 910, and the second oil pump 920 will be described.

  When the engine 100 is in operation while the vehicle is running, the C0 clutch 330 is controlled to be engaged. In this state, HV traveling is performed using only the driving force output from engine 100 by driving engine 100 or the driving force output from second MG 312 in addition to the driving force output from engine 100. It is.

  Since the C0 clutch 330 is engaged, the driving force output from the engine 100 is transmitted to the first MG 311. Therefore, it is possible to generate power using the first MG 311 by operating the first MG 311 as a generator. Further, the first oil pump 910 is driven by the rotation of the rotor of the first MG 311. Therefore, hydraulic pressure is generated by the first oil pump 910. Further, the second oil pump 920 is driven by the rotation of the rotor of the second MG 312. Therefore, hydraulic pressure is generated by the second oil pump 920.

  As shown in FIG. 8, when the output rotation speed of the second MG 312 is low, the output rotation speed of the first MG 311 is relatively high. Therefore, when the output rotational speed of the second MG 312 is low, hydraulic pressure is generated mainly by the first oil pump 910.

  As shown in FIG. 9, when the output rotation speed of the second MG 312 is high, the output rotation speed of the first MG 311 is relatively low. Therefore, when the output rotational speed of the second MG 312 is high, hydraulic pressure is generated mainly by the second oil pump 920.

  However, as shown in FIG. 10, in a state where the vehicle speed is extremely high, that is, in a state where the output rotational speed of the second MG 312 is extremely high, the output shaft of the first MG 311 can rotate in the reverse direction. However, when the output shaft of the first MG 311 rotates in the reverse direction, the one-way clutch 900 prevents the first oil pump 910 from rotating in the reverse direction. This prevents the first oil pump 910 from being driven when the first MG 311 rotates in the reverse direction. Therefore, backflow of oil can be prevented. Therefore, adverse effects when the first MG 311 is used as a drive source for the first oil pump 910 can be reduced.

  As shown in FIG. 11, when the engine 100 and the vehicle are stopped, the C0 clutch 330 is controlled to be in a released state. In this state, the first MG 311 is controlled to drive the first oil pump 910. The first oil pump 910 generates hydraulic pressure by driving the first oil pump 910 using the first MG 311. Therefore, even when the engine 100 is stopped, the hydraulic pressure necessary for the operation of the C0 clutch 330, the C1 clutch 421, the C2 clutch 422, the B1 brake 431, the B2 brake 432, and the B3 brake 433 can be secured.

  As shown in FIG. 12, when starting the engine 100 with the vehicle stopped, the C0 clutch 330 is engaged. In this state, the first MG 311 operates as a motor, so that the engine 100 can be cranked using the first MG 311.

  As shown in FIG. 13, during EV travel using only the driving force output from second MG 312 with engine 100 stopped, C0 clutch 330 is controlled to be in a released state. In this state, the first MG 311 is controlled to drive the first oil pump 910. The first oil pump 910 generates hydraulic pressure by driving the first oil pump 910 using the first MG 311. Further, the second oil pump 920 is driven by the rotation of the rotor of the second MG 312. Therefore, hydraulic pressure is generated by the second oil pump 920. Therefore, even when the engine 100 is stopped, it is possible to ensure the hydraulic pressure necessary for the operation of the C0 clutch 330, the C1 clutch 421, the C2 clutch 422, the B1 brake 431, the B2 brake 432, and the B3 brake 433.

  As shown in FIG. 14, when starting engine 100 during EV traveling, C0 clutch 330 is engaged. In this state, the first MG 311 operates as a motor, so that the engine 100 can be cranked using the first MG 311.

  As described above, according to the power train of the present embodiment, when the C0 clutch is in the released state, the first oil pump is driven using the first MG that performs cranking and power generation of the engine. The hydraulic pressure can be generated by the first oil pump even during stoppage. When the output shaft of the first MG rotates in the reverse direction, the first oil pump is prevented from being driven by the one-way clutch. Therefore, backflow of oil can be prevented. Therefore, adverse effects when the first MG is used as a drive source for the first oil pump can be reduced. Therefore, the first MG used for power generation and engine start can be used as the drive source for the first oil pump without newly providing a drive source for the first oil pump that generates hydraulic pressure while the engine is stopped. As a result, it is possible to reduce an increase in cost required for a device that generates hydraulic pressure.

<Second Embodiment>
Hereinafter, a second embodiment will be described. In the present embodiment, the first oil pump 910 is directly connected to the first MG 311. Further, a switching valve 950 is provided as a switching mechanism for switching the oil passage connected to the suction port 912 of the first oil pump 910 and the oil passage connected to the discharge port 914. Other structures are the same as those in the first embodiment. Therefore, detailed description thereof will not be repeated here.

  Referring to FIG. 15, a first oil pump 910 is provided between first MG 311 and C0 clutch 330. First oil pump 910 is directly connected to first MG 311 without a one-way clutch.

  Referring to FIG. 16, the hybrid vehicle is provided with a switching valve 950 as a switching mechanism for switching an oil passage connected to suction port 912 of first oil pump 910 and an oil passage connected to discharge port 914. . Switching valve 950 is a solenoid valve controlled by ECU 800, for example. A valve other than the solenoid valve may be used. For example, the switching valve 950 may be operated by a hydraulic pressure regulated using another valve.

  The hybrid vehicle is further provided with a first oil passage 951 connected to the oil pan 940 and a second oil passage 952 connected to the hydraulic circuit 930.

  When the output shaft of the first MG 311 rotates forward (rotates in the first direction), the oil sucked from the suction port 912 of the first oil pump 910 is discharged from the discharge port 914 as shown in FIG. In this case, the switching valve 950 is controlled so that the first oil passage 951 is connected to the suction port 912 and the second oil passage 952 is connected to the discharge port 914.

  On the other hand, when the output shaft of the first MG 311 rotates in the reverse direction (rotates in the second direction opposite to the first direction), it is sucked from the discharge port 914 of the first oil pump 910 as shown in FIG. Oil is discharged from the inlet 912. Therefore, oil can flow backward. In this case, the switching valve 950 is controlled to connect the second oil passage 952 to the suction port 912 and connect the first oil passage 951 to the discharge port 914.

  In this way, even when the output shaft of the first MG 311 rotates reversely with the CO clutch 330 engaged as shown in FIG. 18, the oil drawn from the oil pan 940 is supplied to the hydraulic circuit 930. be able to. Therefore, backflow of oil can be prevented. Therefore, adverse effects when the first MG 311 is used as a drive source for the first oil pump 910 can be reduced.

  The embodiment disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

  100 engine, 202 case, 204 torsional damper, 206 input shaft, 208 transmission member, 210 output shaft, 300 hybrid system, 310 power split mechanism, 311 1st MG, 312 2nd MG, 320 planetary gear, 322 sun gear, 324 pinion gear, 326 Carrier, 328 ring gear, 330 C0 clutch, 400 transmission, 411, 412, 413 planetary gear, 421 C1 clutch, 422 C2 clutch, 431 B1 brake, 432 B2 brake, 433 B3 brake, 500 propeller shaft, 600 differential gear, 700 rear wheel , 800 ECU, 900 one-way clutch, 910 first oil pump, 912 suction port, 914 discharge port, 920 second Oil pump, 922 suction port, 924 discharge port, 930 hydraulic circuit, 940 oil pan, 950 switching valve, 951 first oil passage, 952 second oil passage.

Claims (8)

A power train of a vehicle on which a differential including a first rotating element, a second rotating element coupled to a wheel, and a third rotating element is mounted,
A first rotating electrical machine;
An engagement element that connects the first rotating electrical machine and the first rotating element in an engaged state, and that interrupts the first rotating electrical machine and the first rotating element in a released state;
A second rotating electrical machine coupled to the second rotating element;
An engine coupled to the third rotating element;
A one-way clutch coupled to the first rotating electrical machine;
A first oil pump coupled to the first rotating electrical machine via the one-way clutch;
A vehicle power train comprising: the second rotating electric machine; and a second oil pump coupled to the second rotating element. A power train of a vehicle on which a differential including a first rotating element, a second rotating element coupled to a wheel, and a third rotating element is mounted,
A first rotating electrical machine;
An engagement element that connects the first rotating electrical machine and the first rotating element in an engaged state, and that interrupts the first rotating electrical machine and the first rotating element in a released state;
A second rotating electrical machine coupled to the second rotating element;
An engine coupled to the third rotating element;
When the output shaft of the first rotating electrical machine is coupled to the first rotating electrical machine and rotates in the first direction, the oil sucked from the suction port is discharged from the discharging port, and the output of the first rotating electrical machine A first oil pump for discharging oil sucked from the discharge port when the shaft rotates in a second direction opposite to the first direction;
A switching mechanism for switching the oil passage connected to the suction port and the oil passage connected to the discharge port;
A vehicle power train comprising: the second rotating electric machine; and a second oil pump coupled to the second rotating element. A first oil passage connected to a reservoir for storing oil;
A second oil passage connected to a device to which oil is supplied,
The switching mechanism connects the first oil passage to the suction port and the second oil passage to the discharge port when the output shaft of the first rotating electrical machine rotates in the first direction. And when the output shaft of the first rotating electrical machine rotates in the second direction, the second oil passage is connected to the suction port and the first oil passage is connected to the discharge port. The power train of the vehicle according to claim 2, which is connected.   4. The vehicle power train according to claim 1, wherein the first rotating electrical machine operates to drive the first oil pump in a state in which the engagement element is released. 5.   The vehicle power train according to claim 4, wherein the engagement element operates to be in a released state when the engine is stopped.   The vehicle power train according to claim 5, wherein the engagement element operates to be in a released state when the engine is stopped and the vehicle is stopped.   6. The engagement element according to claim 5, wherein the engagement element operates to be in a released state in a state where the engine is stopped and the vehicle is running using the driving force output from the second rotating electrical machine. The vehicle power train described. The differential is a planetary gear;
The first rotating element is a sun gear;
The second rotating element is a ring gear;
The vehicle power train according to claim 1, wherein the third rotating element is a carrier.

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