JPH08324262A - Hybrid type vehicle - Google Patents

Abstract

PURPOSE: To secure cooling and lubricating performance in a motor driving mode by transmitting rotation from a first gear element to an oil pump through a second one-way clutch at vehicle stopping time, and also transmitting rotation from an output means to an oil pump through a first one-way clutch at vehicle traveling time. CONSTITUTION: When a vehicle stops, a sun gear S is rotated in the normal direction at generator rotating speed by idling rotation of an engine 11, and its rotation is transmitted to an oil pump 51 through a transmission shaft 17, an oil pump driving gear 55, a driven gear 56 and a one-way clutch F2, and this is driven. On the other hand, the vehicle travels, and when the engine 11 is rotated at high speed, a ring gear R and the sun gear S are respectively rotated in the normal direction in response to the gear ratio of a planetary gear unit 13. Rotation outputted to an oputput shaft 14 from the ring gear R is transmitted to an oil pump 51 through an oil pump driving gear 53, a driven gear 54 and a one-way clutch F1.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hybrid vehicle.

[0002]

2. Description of the Related Art Conventionally, there has been provided a hybrid type vehicle having a drive device using both an internal combustion engine and an electric motor. Various hybrid vehicles of this type are provided, and a series (series) in which a generator is driven by an internal combustion engine to generate electric energy, the electric motor is rotated by the electric energy, and the rotation is transmitted to driving wheels. Type hybrid type vehicles, parallel type hybrid type vehicles in which drive wheels are directly rotated by an internal combustion engine and an electric motor, and the like.

In the series type hybrid vehicle, the internal combustion engine is separated from the drive system, so that the internal combustion engine can be driven at the highest efficiency point. Further, in the parallel hybrid vehicle, the internal combustion engine generates torque and the electric motor generates auxiliary torque, so the ratio of converting mechanical energy into electric energy is small, and High transmission efficiency.

In the hybrid vehicle, an oil pump is arranged on the same axis as the output shaft of the internal combustion engine, as in a vehicle equipped with a general automatic transmission, and the oil pump is an oil pump drive device. It is designed to be activated by. Then, the oil pump is operated by receiving rotation from the internal combustion engine,
The friction engagement element is cooled, and the bearings, gears, electric motors, etc. are lubricated.

[0005]

However, in the above-mentioned conventional hybrid type vehicle, when the internal combustion engine is rotated at a low speed during idling or the like, the friction engagement elements are cooled and the bearings, gears, electric motors, etc. are cooled. Since it is necessary to lubricate, an oil pump having a large capacity is provided so that a sufficient amount of oil can be discharged.

However, if the capacity of the oil pump is increased, an excessive amount of oil is discharged by the oil pump when the internal combustion engine is rotated at a high speed during high-speed running or the like, and the fuel economy of the hybrid vehicle is deteriorated. In addition, if the internal combustion engine is stopped and the electric motor is used to drive the vehicle, the oil pump will stop operating.
It becomes impossible to perform cooling and lubrication.

The present invention solves the above-mentioned problems of the conventional hybrid type vehicle and can discharge a sufficient amount of oil when the internal combustion engine is rotated at a low speed, and the oil is discharged when the internal combustion engine is rotated at a high speed. It is an object of the present invention to provide a hybrid vehicle that is not excessively discharged, and that is capable of cooling and lubricating even when the internal combustion engine is stopped and the vehicle is run by an electric motor.

[0008]

Therefore, in a hybrid vehicle of the present invention, an internal combustion engine, a generator, an electric motor, an output means connected to driving wheels, and the generator are connected. A differential gear device comprising a first gear element, a second gear element connected to the internal combustion engine, and a third gear element connected to the output means, an oil pump, the output means and the oil pump. A first rotation transmitting means for connecting the first gear element and the oil pump to each other via a first one-way clutch;
Second rotation transmitting means connected through the one-way clutch of. In another hybrid vehicle of the present invention, the generator is also used as a drive motor.

[0009]

According to the present invention, in the hybrid type vehicle as described above, the internal combustion engine, the generator, the electric motor, the output means connected to the drive wheels, and the first unit connected to the generator. A differential gear device comprising: a gear element, a second gear element connected to the internal combustion engine, and a third gear element connected to the output means, an oil pump, the output means and the oil pump. It has a first rotation transmitting means for connecting via a first one-way clutch and a second rotation transmitting means for connecting the first gear element and the oil pump via a second one-way clutch. In this case, when the hybrid vehicle is stopped, the third gear element of the differential gear device is stopped as the drive wheels are stopped. Then, the rotation of the idling speed is transmitted to the second gear element, and the second gear element is rotated in the positive direction. As a result, the first gear element is also rotated in the positive direction.

Therefore, the second rotation transmission means is
The rotation of the first gear element is transmitted to the oil pump via the second one-way clutch. Further, when the hybrid type vehicle is driven in the motor drive mode in which only the electric motor is driven, the second gear element is stopped with the stop of the internal combustion engine, but the output means is rotated with the running of the hybrid type vehicle. To be made.

Therefore, the first rotation transmission means transmits the rotation from the output means to the oil pump via the first one-way clutch. In another hybrid vehicle of the present invention, the generator is also used as a drive motor. In this case, the generator can be driven with the internal combustion engine stopped and the hybrid vehicle not running.

[0012]

Embodiments of the present invention will now be described in detail with reference to the drawings. FIG. 1 is a conceptual diagram of a hybrid type vehicle in a first embodiment of the present invention. In the figure, 11 is an internal combustion engine (E / G), 12 is an output shaft that outputs the rotation generated by driving the internal combustion engine 11, and 13 is the rotation input through the output shaft 12. 14 is a planetary gear unit as a differential gear device that performs gear shifting by
3, an output shaft for outputting rotation after shifting, a first gear 15 fixed to the output shaft 14, a 16 arranged on the same axis as the internal combustion engine 11, and a planetary gear via a transmission shaft 17. It is a generator (G) connected to the unit 13.

The planetary gear unit 13 has a first
A sun gear S as a gear element, a pinion P meshing with the sun gear S, a carrier CR as a second gear element that rotatably supports the pinion P, and a third gear meshing with the pinion P. It comprises a ring gear R as a gear element. Further, the sun gear S is the transmission shaft 1
7, the generator 16 is connected to the ring gear R, the first gear 15 is connected to the ring gear R via the output shaft 14, and the internal combustion engine 11 is connected to the carrier CR via the output shaft 12.

Further, the generator 16 has the transmission shaft 1
7, a rotor 21 rotatably arranged, a stator 22 arranged around the rotor 21 and fixed to a casing (not shown), and a coil 23 wound around the stator 22. The generator 16 has a transmission shaft 17
Electric power is generated by the rotation transmitted through. The coil 23 is connected to a battery (not shown) and supplies current to the battery to store electricity.

Further, 25 is an electric motor (M) which receives current from the battery to generate rotation, 26 is an output shaft for outputting the rotation of the electric motor 25, and 27 is fixed to the output shaft 26. It is the second gear. The electric motor 25
Is a rotor 37 fixed to the output shaft 26 and rotatably arranged, a stator 38 arranged around the rotor 37 and fixed to the casing, and a stator 38.
The coil 39 is wound around. The electric motor 25
Generates torque by the current supplied to the coil 39. For that purpose, the coil 39 is connected to the battery, and the current is supplied from the battery.

In order to rotate a drive wheel (not shown) in the same direction as the rotation of the internal combustion engine 11, a counter shaft 31 as an output shaft is provided, and a third gear 32 is fixed to the counter shaft 31. . In addition, the third gear 32 and the first gear 15 and the third gear 32
And the second gear 27 are meshed with each other, and the rotation of the first gear 15 and the rotation of the second gear 27 are reversed and the third gear 32 is rotated.
To be transmitted to.

Further, a fourth gear 33 having a smaller number of teeth than the third gear 32 is fixed to the counter shaft 31. The fifth gear 35 that meshes with the fourth gear 33
The differential device 36 is fixed to the fifth gear 3
The rotation transmitted to the differential gear 36 is transmitted to the differential device 36.
Is transmitted to the drive wheels. In this embodiment, the output shaft 14, the first gear 15, the output shaft 2
6, the second gear 27, the counter shaft 31, and the third gear 32 constitute an output means.

The output shaft 14 has a sleeve shape and is arranged so as to surround the transmission shaft 17. The first gear 15 is arranged closer to the generator 16 than the planetary gear unit 13. Further, in this embodiment, the planetary gear unit 13 is used as the differential gear device, but a bevel gear unit composed of three or more bevel gears can be used.

As described above, not only the rotation generated by the internal combustion engine 11 can be transmitted to the third gear 32, but also the rotation generated by the electric motor 25 can be transmitted to the third gear 32. Therefore, the hybrid vehicle can be driven in the engine drive mode in which only the internal combustion engine 11 is driven, the motor drive mode in which only the electric motor 25 is driven, and the engine / motor drive mode in which the internal combustion engine 11 and the electric motor 25 are driven. . Further, by controlling the electric power generated in the generator 16, the rotation speed of the transmission shaft 17 can be controlled and the internal combustion engine 11 can be driven at the highest efficiency point. Furthermore, when the generator 16 is an electric motor, the generator 16 causes the internal combustion engine 1 to operate.
It is also possible to start 1.

The rotation of the internal combustion engine 11 is output to the output shaft 12 and transmitted to the first gear 15, while the rotation of the electric motor 25 is output to the output shaft 26 to output the second gear 2.
7, the gear ratio in the first gear 15 and the third gear 32 and the gear ratio in the second gear 27 and the third gear 32 can be made different. Therefore, the flexibility of the capacities of the internal combustion engine 11 and the electric motor 25 is increased, and the design of the hybrid vehicle is facilitated. That is, the internal combustion engine 11 is driven in a region where the engine efficiency is high, and the rotation of the internal combustion engine 11 is controlled by the first gear 15 and the third gear.
The gear ratio in the gear 32 can be reduced and transmitted to the counter shaft 31. Further, the electric motor 25 can be driven in a region where the motor efficiency is high, and the rotation of the electric motor 25 can be decelerated by the gear ratio of the second gear 27 and the third gear 32 and transmitted to the counter shaft 31.

By the way, the planetary gear unit 1
3, first gear 15, second gear 27, third gear 32, fourth
Gear 33, fifth gear 35, differential device 3
6. An oil pump (OP) 51 is provided to lubricate various bearings (not shown) and cool the generator 16, the electric motor 25, and the like.
The oil discharged by can be supplied to each lubrication part.

Therefore, the rotation transmitted from the ring gear R and the rotation transmitted from the sun gear S can be selected and transmitted to the oil pump 51. The output shaft 14 is fixed to the first oil pump driving gear 53 at the end portion on the generator 16 side. On the other hand, a driven gear 54 is disposed on the drive shaft 58 of the oil pump 51 via a one-way clutch F1, and the driven gear 54 and the first oil pump drive gear 53 are meshed with each other. Therefore, the rotation of the ring gear R is controlled by the first oil pump drive gear 53,
The oil pump 51 can be operated by transmitting it to the drive shaft 58 of the oil pump 51 via the driven gear 54 and the one-way clutch F1. Output shaft 1
4, the first oil pump drive gear 53 and the driven gear 54 constitute a first rotation transmission means.

A second oil pump drive gear 55 is fixed to the transmission shaft 17 on the generator 16 side of the first oil pump drive gear 53. On the other hand, the one-way clutch F2 is attached to the drive shaft 58 of the oil pump 51.
A driven gear 56 is disposed via the above, and the driven gear 56 and the second oil pump driving gear 55 are meshed with each other. Therefore, the rotation of the sun gear S is
The oil pump 51 can be operated by transmitting it to the drive shaft 58 of the oil pump 51 through the oil pump driving gear 55, the driven gear 56, and the one-way clutch F2. The transmission shaft 17, the second oil pump drive gear 55, and the driven gear 56 constitute second rotation transmission means.

By the way, the one-way clutch F1
Locks when the rotational speed of the driven gear 54 is higher than the rotational speed of the drive shaft 58 of the oil pump 51, and becomes free when the rotational speed of the driven gear 54 is equal to or lower than the rotational speed of the drive shaft 58 of the oil pump 51. The one-way clutch F2 is locked when the rotation speed of the driven gear 56 is higher than the rotation speed of the drive shaft 58 of the oil pump 51, and the rotation speed of the driven gear 56 is equal to or lower than the rotation speed of the drive shaft 58 of the oil pump 51. If you get free.

Therefore, the higher rotation speed of the driven gear 54 and the higher rotation speed of the driven gear 56 is the rotation of the drive shaft 5.
8 and the oil pump 51 is operated. In this embodiment, the first oil pump drive gear 53
Also, the gear ratio of the driven gear 54 and the gear ratio of the second oil pump drive gear 55 and the driven gear 56 are made equal. Therefore, the oil pump 5 is rotated by the higher rotation speed of the carrier CR and the sun gear S.
1 is activated.

Further, the gear ratio of the planetary gear unit 13 is such that when the ring gear R is fixed and the rotation of the internal combustion engine 11 is transmitted to the carrier CR, the sun gear S.
Is set to be higher than that of the carrier CR. Therefore, when the hybrid vehicle is stopped in the engine drive mode, the generator 16 is accelerated and the minimum rotation speed of the oil pump 51 can be increased, so that the basic discharge amount of the oil pump 51 can be reduced. Therefore, the oil pump 51 can be downsized.

Next, the operation of the hybrid type vehicle having the above structure will be described. 2 is a velocity diagram of the hybrid vehicle according to the first embodiment of the present invention when the hybrid vehicle is stopped, and FIG. 3 is a velocity diagram of the hybrid vehicle according to the first embodiment of the present invention when the hybrid vehicle is running. In this case, the number of revolutions of the generator 16 (Fig. 1) (hereinafter referred to as "generator revolution number") is NG.
When the rotational speed of the internal combustion engine 11 (hereinafter referred to as "engine rotational speed") is NEG and the rotational speed of the output shaft 14 (hereinafter referred to as "output rotational speed") is NOUT, NG = 3NEG-2NOUT Become.

When the hybrid vehicle is stopped, the drive wheels (not shown) are stopped, so that the ring gear R of the planetary gear unit 13 is fixed. When the internal combustion engine 11 is rotated at the idling speed, the rotation of the internal combustion engine 11 is transmitted to the carrier CR via the output shaft 12, and the carrier CR is rotated in the forward direction at the engine speed NEG. As a result, the sun gear S is also rotated in the positive direction at the generator speed NG.

Then, the planetary gear unit 13
The gear ratio of, for example, the number of teeth of the ring gear R is the sun gear S
When it is set to be α times (twice in this embodiment) the number of teeth of the generator, the generator speed NG is (α + 1) times the engine speed NEG (this embodiment), as shown in FIG. In 3 times). Therefore, the rotation of the sun gear S is transmitted to the transmission shaft 17, the second oil pump drive gear 55,
When the oil pump 51 is operated by transmitting it to the drive shaft 58 via the driven gear 56 and the one-way clutch F2, a sufficient amount of oil can be discharged by the oil pump 51, so that the capacity of the oil pump 51 is reduced. be able to. That is, the basic discharge amount of the oil pump 51 can be reduced to one third as compared with the case where the oil pump 51 is operated by the internal combustion engine 11. Further, if the capacity of the oil pump 51 is reduced, an excessive amount of oil will not be discharged by the oil pump 51 even when the internal combustion engine 11 is rotated at high speed during high speed traveling or the like.

On the other hand, when the hybrid vehicle is running, the internal combustion engine 11 is rotated at high speed. Therefore, as shown in FIG. 3, the engine speed NEG becomes high, so that the ring gear R and the sun gear S are respectively rotated in the positive direction in accordance with the gear ratio of the planetary gear unit 13. The rotation of the output rotation speed NOUT output from the ring gear R to the output shaft 14 is transmitted to the drive shaft 58 via the first oil pump drive gear 53, the driven gear 54 and the one-way clutch F1 to drive the oil pump 51. Activate. Therefore, the oil pump 51 is output at the output speed NOUT corresponding to the engine speed NE.
Can be operated, so that a sufficient amount of oil can be discharged, and since the generator speed NG does not increase excessively as the vehicle speed increases, excessive oil is discharged. Never.

When the hybrid vehicle is run in the motor drive mode, the carrier CR is stopped with the stop of the internal combustion engine 11, but the output shaft 14 is rotated with the travel of the hybrid vehicle. Therefore, the rotation of the output rotation speed NOUT is transmitted to the drive shaft 58 via the first oil pump drive gear 53, the driven gear 54, and the one-way clutch F1 to operate the oil pump 51. As a result, the oil pump 51 can be operated in accordance with the output rotation speed NOUT, so that a sufficient amount of oil can be discharged and the oil is not discharged excessively.

Since the ring gear R is rotated in the positive direction with the rotation of the output shaft 14, the sun gear S is rotated in the reverse direction. The rotation in the opposite direction is caused by the transmission shaft 17
Although it is transmitted to the second oil pump drive gear 55 and the driven gear 56 via, the one-way clutch F2 becomes free, so that the operation of the oil pump 51 is not hindered.

As described above, a sufficient amount of oil can be discharged by the oil pump 51 when the internal combustion engine 11 is rotated at a low speed, and excessive oil is not discharged when the internal combustion engine 11 is rotated at a high speed. Moreover, even when the hybrid vehicle is driven in the motor drive mode, the oil pump 5
1 can be activated. Next, details of the oil pump drive device will be described.

FIG. 4 is a sectional view of the essential parts of the oil pump drive system according to the first embodiment of the present invention. In the figure, 5
1 is a trochoidal type oil pump, 54 is a driven gear which meshes with a first oil pump driving gear 53 (FIG. 1), 56 is a driven gear which meshes with a second oil pump driving gear 55, 58 is a drive shaft, F1 , F2 is a one-way clutch.

Reference numeral 60 is a casing of a hybrid type vehicle, and the oil pump 51 is fixed to the casing 60. 61 is an oil pump case,
A drive rotor 62 and a driven rotor 63 that meshes with the drive rotor 62 on the outer periphery of the drive rotor 62 are arranged in the oil pump case 61. Both ends of the drive shaft 58 are rotatably supported by bearings 67 and 68.

Next, a second embodiment of the present invention will be described. FIG. 5 is a conceptual diagram of a hybrid vehicle according to the second embodiment of the present invention. The parts having the same structures as those in the first embodiment are designated by the same reference numerals and the description thereof will be omitted. In this embodiment, the first gear 1
Reference numeral 5 denotes an internal combustion engine 11 from the planetary gear unit 13.
It is arranged on the side. The one-way clutch F1 is provided between the output shaft 14 and the first oil pump drive gear 53,
The one-way clutch F2 is arranged between the transmission shaft 17 and the second oil pump drive gear 55.

The output shaft 14 constitutes the first rotation transmitting means, and the transmission shaft 17 constitutes the second rotation transmitting means. Further, in this embodiment, the output shaft 14, the first gear 15, the output shaft 26, the second gear 27, the counter shaft 31, and the third gear 32 constitute an output means.
When the hybrid vehicle is stopped, the drive wheels (not shown) are stopped, so the planetary gear unit 1
The ring gear R of 3 is fixed. When the internal combustion engine 11 is rotated at the idling speed, the rotation of the internal combustion engine 11 is transmitted to the carrier CR via the output shaft 12, and the carrier CR is rotated at the engine speed NEG (FIG. 2).
Can be rotated in the positive direction. As a result, the sun gear S is also rotated in the positive direction at the generator speed NG.

Therefore, the rotation of the sun gear S is transmitted to the transmission shaft 1
7, the one-way clutch F2, the second oil pump drive gear 55, and the driven gear 56 are transmitted to the drive shaft 58 to operate the oil pump 51, and the oil pump 51 discharges a sufficient amount of oil. Therefore, the capacity of the oil pump 51 can be reduced. As a result, the internal combustion engine 11 can be used when traveling at high speed.
Even if the motor is rotated at high speed, the oil pump 51 does not discharge an excessive amount of oil.

On the other hand, when the hybrid vehicle is running, the internal combustion engine 11 is rotated at high speed. Therefore, the engine speed NEG becomes high, so that the ring gear R and the sun gear S are respectively rotated in the positive direction in accordance with the gear ratio of the planetary gear unit 13. The rotation of the output rotation speed NOUT output from the ring gear R to the output shaft 14 is transmitted to the drive shaft 58 via the one-way clutch F1, the first oil pump driving gear 53 and the driven gear 54, and the oil pump 51 is driven. Activate. Therefore, since the oil pump 51 can be operated at the output speed NOUT corresponding to the engine speed NE, a sufficient amount of oil can be discharged, and the oil is not discharged excessively.

When the hybrid vehicle is run in the motor drive mode, the carrier CR is stopped with the stop of the internal combustion engine 11, but the output shaft 14 is rotated with the travel of the hybrid vehicle. Therefore, the rotation of the output rotation speed NOUT is transmitted to the drive shaft 58 via the one-way clutch F1, the first oil pump driving gear 53 and the driven gear 54, and operates the oil pump 51. As a result, even when the hybrid vehicle is driven in the motor drive mode, the oil pump 5
1 can be activated.

Next, a third embodiment of the present invention will be described. FIG. 6 is a conceptual diagram of a hybrid vehicle according to the third embodiment of the present invention. The parts having the same structures as those in the first embodiment are designated by the same reference numerals and the description thereof will be omitted. In this embodiment, the first gear 15
Is arranged closer to the internal combustion engine 11 than the planetary gear unit 13. In addition, the second oil pump drive gear 5
5 and the transmission shaft 17 are arranged on the same axis, and the first oil pump drive gear 53 and the output shaft 26 are arranged on the same axis. A common driven gear 71 that meshes with the first oil pump drive gear 53 and the second oil pump drive gear 55 is rotatably disposed, and the driven gear 71 and the drive shaft 58 of the oil pump 51 are connected to each other. Be connected.

The one-way clutch F1 has the output shaft 2
The one-way clutch F2 is arranged between the transmission shaft 17 and the second oil pump driving gear 55 between the gear 6 and the first oil pump driving gear 53. The output shaft 26 and the second gear 27 serve as a first rotation transmission means,
The transmission shaft 17 forms a second rotation transmission means.

In this embodiment, the output shaft 14,
First gear 15, counter shaft 31, and third gear 32
The output means is constituted by. When the hybrid vehicle is stopped, the drive wheels (not shown) are stopped, so that the ring gear R of the planetary gear unit 13 is fixed. Then, when the internal combustion engine 11 is rotated at the idling speed, the rotation of the internal combustion engine 11 is transmitted to the carrier CR via the output shaft 12, and the carrier CR.
Is rotated in the forward direction at the engine speed NEG (FIG. 2). As a result, the sun gear S is also rotated in the positive direction at the generator speed NG.

Therefore, the rotation of the sun gear S is transmitted to the transmission shaft 1
7, the one-way clutch F2, the second oil pump drive gear 55, and the driven gear 71 are transmitted to the drive shaft 58 to operate the oil pump 51, and the oil pump 51 discharges a sufficient amount of oil. Therefore, the capacity of the oil pump 51 can be reduced. Further, if the capacity of the oil pump 51 is reduced, an excessive amount of oil will not be discharged by the oil pump 51 even when the internal combustion engine 11 is rotated at high speed during high speed traveling or the like.

On the other hand, when the hybrid type vehicle is running, the second gear 27 is rotated by the third gear 32. Then, the rotation of the second gear 27 causes the output shaft 26,
It is transmitted to the drive shaft 58 via the one-way clutch F1, the first oil pump drive gear 53 and the driven gear 71, and operates the oil pump 51. Further, when the hybrid vehicle is driven in the motor drive mode, the output shaft 26 is rotated with the traveling of the hybrid vehicle even if the internal combustion engine 11 is stopped. Therefore, the rotation of the output shaft 26 is transmitted to the drive shaft 58 via the one-way clutch F1, the first oil pump drive gear 53, and the driven gear 71 to operate the oil pump 51. As a result, the oil pump 51 can be operated even when the hybrid vehicle is traveling in the motor drive mode.

Next, a fourth embodiment of the present invention will be described. FIG. 7 is a conceptual diagram of a hybrid vehicle according to the fourth embodiment of the present invention. The parts having the same structures as those in the first embodiment are designated by the same reference numerals and the description thereof will be omitted. In this embodiment, the first gear 1
5 is arranged closer to the generator 16 than the planetary gear unit 13. Further, the sun gear S is connected to the generator 16 via the transmission shaft 17, the ring gear R is connected to the internal combustion engine 11 via the output shaft 12, and the carrier CR is connected to the first gear 15 via the output shaft 14. Further, in the present embodiment, the sun gear S constitutes the first gear element, the ring gear R constitutes the second gear element, and the carrier CR constitutes the third gear element.

The output shaft 12 extends rearward through the generator 16 and is connected to the drive shaft 58 of the oil pump 51 via the one-way clutch F1. Also, the transmission shaft 1
7 is a one-way clutch F as a second rotation transmission means.
2 is connected to the drive shaft 58 of the oil pump 51. The one-way clutches F1 and F2 are locked when the output shaft 12 and the transmission shaft 17 are rotated in the forward direction, and are released when the output shaft 12 and the transmission shaft 17 are rotated in the reverse direction.

Further, in this embodiment, the output means is constituted by the output shaft 14, the first gear 15, the output shaft 26, the second gear 27, the counter shaft 31, and the third gear 32. Then, the output shaft 12 is configured as a first rotation transmission means, and the transmission shaft 17 is configured as a first rotation transmission means. Next, the operation of the hybrid vehicle having the above structure will be described.

FIG. 8 is a speed diagram of the hybrid vehicle according to the fourth embodiment of the present invention when the hybrid vehicle is stopped, and FIG. 9 is a speed diagram of the hybrid vehicle according to the fourth embodiment of the present invention when the hybrid vehicle is running. . If the hybrid vehicle is stopped,
When the internal combustion engine 11 (FIG. 7) is rotated at the idling speed, the rotation of the output shaft 12 is changed to the one-way clutch F1.
Is transmitted to the drive shaft 58 via the drive shaft 58 to operate the oil pump 51. Therefore, since a sufficient amount of oil can be discharged by the oil pump 51, the capacity of the oil pump 51 can be reduced. As a result, the oil pump 51 does not discharge an excessive amount of oil even when the internal combustion engine 11 is rotated at high speed during high-speed traveling or the like.

When the hybrid vehicle is running, the internal combustion engine 11 is rotated at high speed. Therefore, the rotation of the engine speed NEG is transmitted to the drive shaft 58 via the output shaft 12 and the one-way clutch F1 to operate the oil pump 51. As a result, the oil pump 51 can be rotated corresponding to the engine speed NEG, so that a sufficient amount of oil can be discharged.

In this case, as shown in FIG. 8, since the engine speed NEG becomes high, the planetary gear unit 1
Corresponding to the gear ratio of 3, the carrier CR is rotated in the positive direction and the sun gear S is rotated in the reverse direction. And the sun gear S
The rotation of the generator rotational speed NG output from the transmission shaft 17 is transmitted to the one-way clutch F2, but since the one-way clutch F2 becomes free, the oil pump 5
1 does not work.

When the hybrid type vehicle is driven in the motor drive mode, the ring gear R is stopped as the internal combustion engine 11 is stopped, but the output shaft 14 is rotated as the hybrid type vehicle runs. The rotation of the output rotation speed NOUT is transmitted to the carrier CR. Therefore, the sun gear S is rotated in the positive direction at the generator speed NG. The rotation of the generator rotation speed NG output from the sun gear S is transmitted to the drive shaft 58 via the transmission shaft 17 and the one-way clutch F2, and the oil pump 51
Operate. As a result, the oil pump 51 can be operated at the generator rotational speed NG corresponding to the engine rotational speed NEG, so that a sufficient amount of oil can be discharged.

Next, a fifth embodiment of the present invention will be described. In this case, the generator 16 of the first embodiment (FIG. 1) is also used as a drive motor. Then, with the internal combustion engine 11 stopped, and also with the hybrid vehicle not running, the generator 16 is driven to cool the friction engagement elements and lubricate the bearings, gears, the electric motor 25, and the like. can do.

That is, when the hybrid type vehicle is left for a long period of time and is allowed to travel in the motor drive mode, if the electric motor is driven before sufficient oil has spread to the bearings, gears, electric motor 25, etc., The durability of the hybrid vehicle will be reduced. Then, when it is detected that the driver turns on the ignition switch, the generator 16 is driven and the oil pump 51 is operated.

The internal combustion engine 11 is forcibly rotated by driving the generator 16, but the generator 16 is only driven for a short period of time, so that the electric energy consumption is small. Further, the generator 16 in another embodiment can be used as a drive motor.

Further, by driving the electric motor 25 with the internal combustion engine 11 stopped, the output shaft 26
When the hybrid-type vehicle is moved backward by rotating the motor, the oil pump 51 can be operated by driving the generator 16. Then, even when a severe traveling condition is detected at the time of sudden start, the generator 1
The oil pump 51 can be operated by driving 6.

[0057]

As described in detail above, according to the present invention, in a hybrid vehicle, an internal combustion engine, a generator, an electric motor, an output means connected to driving wheels, and the generator. A differential gear unit comprising a first gear element connected to the internal combustion engine, a second gear element connected to the internal combustion engine, and a third gear element connected to the output means, an oil pump, and the output means. And a first rotation transmission means for connecting the oil pump and the oil pump via a first one-way clutch, and a second connection for connecting the first gear element and the oil pump via a second one-way clutch.
Rotation transmission means.

When the hybrid type vehicle is stopped,
The second rotation transmission means transmits the rotation from the first gear element to the oil pump via the second one-way clutch. Therefore, since a sufficient amount of oil can be discharged by the oil pump, the oil pump can be downsized. That is, the basic discharge amount of the oil pump can be reduced as compared with the case where the oil pump is operated by the internal combustion engine.

Therefore, a sufficient amount of oil can be discharged when the internal combustion engine is rotated at a low speed, and excessive oil is not discharged when the internal combustion engine is rotated at a high speed. Also,
When the hybrid vehicle is driven in the motor drive mode, the first rotation transmission means transmits the rotation from the output means to the oil pump via the first one-way clutch. Therefore, cooling and lubrication can be performed even when the hybrid vehicle is driven in the motor drive mode.

In another hybrid vehicle of the present invention, the generator can be used as a drive motor. In this case, the generator can be driven with the internal combustion engine stopped and without the hybrid vehicle running. Therefore, when the hybrid type vehicle is left for a long period of time and then allowed to travel in the motor drive mode, the electric motor is not driven before sufficient oil has spread to the bearings, gears, electric motors, etc. The durability of the vehicle can be increased.

[Brief description of drawings]

FIG. 1 is a conceptual diagram of a hybrid vehicle according to a first embodiment of the present invention.

FIG. 2 is a velocity diagram when the hybrid vehicle according to the first embodiment of the present invention is stopped.

FIG. 3 is a velocity diagram during traveling of the hybrid vehicle according to the first embodiment of the present invention.

FIG. 4 is a cross-sectional view of the essential parts of the oil pump drive device according to the first embodiment of the present invention.

FIG. 5 is a conceptual diagram of a hybrid vehicle according to a second embodiment of the present invention.

FIG. 6 is a conceptual diagram of a hybrid vehicle according to a third embodiment of the present invention.

FIG. 7 is a conceptual diagram of a hybrid vehicle according to a fourth embodiment of the present invention.

FIG. 8 is a velocity diagram when the hybrid vehicle according to the fourth embodiment of the present invention is stopped.

FIG. 9 is a velocity diagram when the hybrid vehicle according to the fourth embodiment of the present invention is running.

[Explanation of symbols]

 11 Internal Combustion Engine 13 Planetary Gear Unit 14, 26 Output Shaft 15 First Gear 16 Generator 25 Electric Motor 27 Second Gear 31 Counter Shaft 32 Third Gear 51 Oil Pump S Sun Gear CR Carrier R Ring Gear F1, F2 One Way Clutch

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Satoru Shimizu Satoru Takane, Fujii-cho, Anjo City, Aichi Prefecture Aisin AW Co., Ltd. (72) Masayuki Takenaka, Takane, Fujii-cho, Anjo City, Aichi Prefecture Aisin・ AW Co., Ltd.

Claims (2)

[Claims] 1. An internal combustion engine, a generator, an electric motor, output means connected to drive wheels, a first gear element connected to the generator, and a second gear element connected to the internal combustion engine. A differential gear device comprising a gear element and a third gear element connected to the output means, an oil pump, and a first rotation connecting the output means and the oil pump via a first one-way clutch. Transmission means and said first
And a second rotation transmitting means for connecting the gear element of (1) and the oil pump via a second one-way clutch. 2. The hybrid vehicle according to claim 1, wherein the generator is also used as a drive motor.