JPH05305822A - Hybrid powered vehicle - Google Patents

Abstract

PURPOSE:To dispense with the setup of any one-way clutch for separating a gap between a motor and an engine of a car at a time when the vehicle is driven by the motor alone. CONSTITUTION:This vehicle is provided with an engine 11 and a motor being selectively drivable, and this engine 11 is connected to a transmission 13 which shifts the generated engine speed and transmits it to each of driving wheels 19. This transmission 13 is provided with a gear unit, a frictional engaging element and a one-way clutch, and at least one of the one-way clutches is installed in such a direction as allowing that rotation of the motor 15 becomes speedier than that of the engine 11 at a time when the motor 15 is driven and the engine 11 is stopped instead. Therefore, when the car is driven by the motor 15 alone, an output shaft 12 of the engine 11 is able to maintain its stoppage intact.

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, a vehicle generally shifts the rotation generated by operating an engine, which is a gasoline engine, through a transmission such as an automatic transmission or a manual transmission and transmits the rotation to driving wheels. There is. Since the gasoline engine burns a mixture of gasoline and air in a compressed state and converts the energy generated at this time into torque, not only noise accompanying combustion is generated, but also the environment is polluted by exhaust gas. Will end up.

On the other hand, there has been provided an electric vehicle in which the engine is replaced with an electric motor, that is, a motor, to eliminate the generation of noise and exhaust gas. In this case, a vehicle is equipped with a motor and a battery, and the drive wheels are rotated by the motor to drive the vehicle. Therefore, almost no noise is generated when the vehicle runs, and no exhaust gas is generated.

However, in the case of an electric vehicle, the amount of electricity with which the battery can be charged is limited, and the cruising range becomes short. Therefore, it is necessary to mount a large battery to obtain a sufficient cruising range. In addition, when using a motor that is large enough to be installed in a normal vehicle, the value of the torque generated is smaller than when using an engine, and sudden start, high load running, high speed running, etc. I can't.

Therefore, a hybrid type vehicle using both an engine and a motor is provided. Various kinds of hybrid vehicles of this type are provided, and a series (series) type vehicle in which a generator drives an engine to generate electric energy, a motor is rotated by the electric energy, and the rotation is transmitted to driving wheels is provided. (See Japanese Patent Laid-Open No. 62-104403) and parallel type in which driving wheels are directly rotated by an engine and a motor. The parallel type is a one-system type in which an engine drive system and a motor drive system are further connected (JP-A-56-132).
No. 102, U.S. Pat. No. 4,533,011) and a two-system type in which front wheels and rear wheels are independently driven by an engine and a motor, respectively.

In the case of the series type, since the drive wheels are driven only by the motor, it cannot travel at a high speed over a long distance. Therefore, the parallel type is used when traveling a long distance at high speed. In the hybrid vehicle having the above configuration, it is possible to select traveling only by the motor, traveling only by the engine, or traveling together by using the engine and the motor. For example, it is possible to travel only by the motor in the low speed range.
In the high-speed range, it is possible to drive only by the engine or by using both the engine and the motor together.

In this case, if the engine is connected while traveling only by the motor, the engine itself becomes a resistance and consumes energy correspondingly. Therefore, a clutch or a one-way clutch is provided between the engine and the motor. However, while traveling only by the motor, the clutch can be released or the one-way clutch can be released to disconnect the two.

The rotation transmitted from the engine or the motor is further transmitted to the transmission, the transmission is changed in speed, and then transmitted to the drive wheels.

[0009]

However, in the above-mentioned conventional hybrid type vehicle, in which the clutch is disengaged when traveling only by the motor, the hydraulic circuit for the clutch is required, and the hybrid type vehicle is operated by the motor. When switching from running to running with the engine, unless the engine speed is synchronized with the motor speed, a shock will be generated due to the engagement of the clutch, so not only will control be complicated due to synchronization. The size of the power transmission system is lengthened by the amount of the clutch, and the cost is increased.

On the other hand, in the case of freeing the one-way clutch while traveling only by the motor,
It is not necessary to synchronize the number of revolutions of the engine with the number of revolutions of the motor when switching from traveling by the motor to traveling by the engine, but the engine brake cannot be applied while traveling only by the engine. Also, the engine cannot be started by the motor. Also in this case, the size of the power transmission system is lengthened by the provision of the one-way clutch, and the cost is increased.

The present invention solves the above-mentioned problems of the conventional hybrid type vehicle and eliminates the need to provide an independent clutch or a one-way clutch for disconnecting the motor from the engine when traveling only by the motor. It is an object of the present invention to provide a hybrid vehicle that does not cause a shock when switching from driving with the engine to driving with the engine, and does not have a long dimension or a high cost.

[0012]

Therefore, in a hybrid vehicle of the present invention, an engine that can be selectively driven, a motor that can be selectively driven, a gear unit,
The transmission has a frictional engagement element and a one-way clutch, and has a transmission that receives the rotation of the engine to change gears.

By disengaging at least one one-way clutch of the transmission, the one-way clutch is arranged in a direction that allows the rotation of the motor to be faster than the rotation of the engine when the motor is driven and the engine is stopped.

[0014]

According to the present invention, as described above, the engine that can be selectively driven and the motor that can be selectively driven are provided. It is possible to select the traveling that uses both. The engine is connected to a transmission so that the rotation generated by the engine can be speed-changed and transmitted to the drive wheels. Therefore, the transmission has a gear unit, a friction engagement element, and a one-way clutch, and the elements of the gear unit are selectively engaged and disengaged by the friction engagement element.

At least one of the one-way clutches of the transmission becomes free,
When the motor is driven and the engine is stopped, the motor is allowed to rotate faster than the engine. Therefore, when the hybrid vehicle is traveling only by the motor, the one-way clutch can be disengaged to idle the predetermined element of the planetary gear unit so that the rotation of the output shaft of the engine is not transmitted.

Therefore, it is not necessary to provide an independent clutch or a one-way clutch for disconnecting the motor from the engine when traveling only by the motor, and a shock may occur when switching from traveling by the motor to traveling by the engine. In addition, the size can be shortened and the cost can be reduced.

[0017]

Embodiments of the present invention will now be described in detail with reference to the drawings. FIG. 1 is a schematic view of a hybrid type vehicle showing a first embodiment of the present invention, and FIG. 2 is a second view of the present invention.
FIG. 3 is a schematic view of a hybrid type vehicle showing the embodiment of FIG. 3, and FIG. 3 is an operation diagram of the hybrid type vehicle showing the first and second embodiments of the present invention.

In FIG. 1, 11 is an engine, 12 is an output shaft of the engine 11, 13 is a transmission that is connected to the output shaft 12, receives the rotation of the engine 11 and outputs the rotated rotation, and 14 is the transmission. 13 output shaft, 15 consists of stator and rotor,
A motor that receives a drive current to drive and rotate, 16 is an output shaft of the motor 15, and 17 is a differential device.

The rotor of the motor 15 corresponds to the output shaft 1
It is fixed to 4, 16 and rotates integrally. Therefore,
Both the rotation output from the transmission 13 and the rotation output from the motor 15 are transmitted to the differential device 17 via the output shaft 16. Further, reference numeral 18 is a drive shaft for transmitting the rotation of the differential device 17 due to the differential to the drive wheel 19. in this case,
Both the engine 11 and the motor 15 drive the drive wheels 19. The drive wheels 19 may be either front wheels or rear wheels.

The transmission 13 is composed of a planetary gear unit 22 of a single planetary type, a clutch C, a brake B and a one-way clutch F,
The planetary gear unit 22 comprises a ring gear R, a pinion P, a carrier CR and a sun gear S.
The output shaft 12 of the engine 11 and the carrier CR are connected so that the rotation of the engine 11 is input to the carrier CR. The ring gear R and the output shaft 14 are connected to rotate the transmission 13 from the ring gear R. It is supposed to be output. A one-way clutch F and a clutch C are provided between the sun gear S and the carrier CR.
Are connected in parallel, and a brake B is connected between the sun gear S and the case 23 of the hybrid vehicle.

In the transmission 13, as shown in FIG. 3, when the brake B is released and the clutch C is engaged at the first speed (1st), the planetary gear unit 22 is brought into a direct connection state, and the engine 11 rotates. The same number of rotations as the number of rotations is output to the output shaft 14. Also,
When the brake B is engaged and the clutch C is released at the second speed (2nd), the sun gear S is fixed, the one-way clutch F is released, the carrier CR is rotated, and the planetary gear unit 22 is in the overdrive state. .. As a result, the rotation increased in speed from the ring gear R is output to the output shaft 14.

The one-way clutch F and the clutch C can be arranged between any two elements of the ring gear R, the carrier CR and the sun gear S, and the clutch C can be provided unless the engine braking at the first speed is required. Can be omitted. When the hybrid type vehicle having the above-described configuration travels only with the engine 11, the supply of the drive current to the motor 15 is stopped and the engine 11 is driven.

When traveling only with the motor 15,
The clutch C is released to supply the drive current to the motor 15 and stop the engine 11. At this time, the ring gear R rotates together with the rotor of the motor 15, but the one-way clutch F becomes free and the sun gear S idles in the opposite direction, so that the stopped state of the engine 11 can be maintained.

When traveling using both the engine 11 and the motor 15, the clutch C is engaged to output the sum of the outputs of the engine 11 and the motor 15 to the output shaft 16. The engine 11 can be started by a stator (not shown), or can be started by engaging the clutch C or the brake B while the motor 15 is running.

From the running by the motor 15 to the engine 1
When switching to traveling by 1, when the rotation of the engine 11 is increased, the one-way clutch F locks and synchronizes, so that control for synchronization is not particularly required. Next, a second embodiment will be described. In FIG. 2, 1
1 is an engine, 12 is an output shaft of the engine 11, 13 is a transmission connected to the output shaft 12, 14 is an output shaft of the transmission 13, 15 is a motor, 1
6 is an output shaft of the motor 15, 17 is a differential device, 18 is a drive shaft, 19 is a drive wheel composed of front wheels or rear wheels, and C1 is a first clutch arranged between the motor 15 and the differential device 17. The first clutch C1
Selectively blocks the rotation of the engine 11 or the motor 15 from being transmitted to the differential device 17.

The rotor of the motor 15 corresponds to the output shaft 1
It is fixed to 4, 16 and rotates integrally. Therefore,
Both the rotation output from the transmission 13 and the rotation output from the motor 15 are transmitted to the differential device 17 via the output shaft 16. The transmission 13 is formed of a planetary gear unit 25 of a double planetary type, a brake B and a one-way clutch F, and the planetary gear unit 25 is composed of a ring gear R, pinions P ₁ and P ₂ , a carrier CR and a sun gear S.

The output shaft 12 of the engine 11 and the ring gear R are connected so that the rotation of the engine 11 is input to the ring gear R, the carrier CR and the output shaft 14 are connected, and the carrier CR to the transmission 13 are connected. The rotation of is output. A one-way clutch F is connected between the sun gear S and the carrier CR, and a brake B is connected between the sun gear S and the case 23.

The transmission 13 operates as shown in the operation table constructed by removing the clutch C in FIG. In the second embodiment, the engine 11 can be started without using the starter when the hybrid vehicle is stopped. That is, when the first clutch C1 is released and the brake B is engaged to drive the motor 15, the engine 11 can be started. Further, the motor 11 can be used as a generator by driving the engine 11 while stopped in the same state.

FIG. 4 is a vehicle speed / torque relationship diagram in the first and second embodiments of the present invention. In the figure, a ₁ is the torque line of the torque generated by the motor 15 (FIGS. 1 and 2),
₂ is the torque line of the torque (engine torque) output by the transmission 13 when the transmission 13 shifts to the first speed, and a ₃ is the torque line of the transmission 13.
The torque line of the torque (engine torque) that the transmission 13 outputs when shifting to high speed is shown.

In the low speed region, the vehicle can be driven only by the motor 15, and the engine 11 and the motor 15 can be used together. Further, in the medium / high speed range, the vehicle can be driven only by the engine 11. FIG. 5 is a schematic view of a hybrid vehicle showing a third embodiment of the present invention,
FIG. 6 is an operation diagram of a hybrid type vehicle showing a third embodiment of the present invention.

In the figure, 11 is an engine, 12 is an output shaft of the engine 11, 13 is a transmission connected to the output shaft 12, and 14 is the transmission 13.
Output shaft, 15 is a motor, 16 is an output shaft of the motor 15, 17 and 26 are differential devices, 19 and 27
Is a drive wheel composed of front wheels or rear wheels. In this case, the torque transmission systems of the engine 11 and the motor 15 are independently provided to transmit the respective rotations to the front wheels or the rear wheels.

The transmission 13 comprises a planetary gear unit 28, a clutch C and a one-way clutch F, and the planetary gear unit 28 comprises a ring gear R, a pinion P, a carrier CR and a sun gear S. The output shaft 12 is connected to the ring gear R and the carrier CR is connected to the output shaft 14. In the hybrid vehicle having the above structure, when the clutch C is disengaged in the first speed,
The one-way clutch F is locked to enter the underdrive state, and the decelerated rotation is output to the output shaft 14.
Further, when the clutch C is engaged in the second speed, the planetary gear unit 28 is directly connected and the rotation of the engine 11 is directly transmitted to the output shaft 14.

In the hybrid vehicle having the above structure,
When traveling only by the motor 15, the drive current is supplied to the motor 15 to drive the drive wheels 19. On the other hand, engine 1
1 is stopped, but the drive wheels 27 are
Will follow. At this time, the carrier CR rotates by being driven by the drive wheels 27, but the one-way clutch F becomes free and the sun gear S idles in the opposite direction.
The stopped state of 1 can be maintained.

FIG. 7 is a schematic view of a hybrid type vehicle showing a fourth embodiment of the present invention, and FIG. 8 is an operation diagram of a hybrid type vehicle showing the fourth embodiment of the present invention. In the figure,
11 is an engine, 12 is an output shaft of the engine 11, 13
Is a transmission connected to the output shaft 12, 14
Is an output shaft of the transmission 13, 15 is a motor,
Reference numeral 16 is an output shaft of the motor 15, 17 is a differential device, and 19 is a drive wheel composed of front wheels or rear wheels.

The transmission 13 includes a first counter drive gear 31, a first counter driven gear 32,
It comprises a second counter drive gear 33, a second counter driven gear 34, a clutch C and a one-way clutch F. The first counter drive gear 31 and the second counter drive gear 33 are on the output shaft 12, the first counter driven gear 32 and the second counter. Driven gear 34 is output shaft 1
It is fixed at 4. In addition, the first counter drive gear 31
The gear ratio between the first counter driven gear 32 and the second counter driven gear 32 is the second counter drive gear 33 and the second counter driven gear 34.
It is set to be larger than the gear ratio between.

In the hybrid vehicle having the above structure,
When the clutch C is disengaged in the first speed, the rotation of the engine 11 is transmitted to the second counter drive gear 33 via the output shaft 12 and is decelerated between the second counter drive gear 33 and the second counter driven gear 34 to output the output shaft. 14, 16
Is transmitted to the drive wheel 19 via. At this time, the one-way clutch F is locked. Here, when engine braking is required at the first speed, a clutch for engaging the second counter driven gear 34 and the output shaft 14 may be provided in parallel with the one-way clutch F.

When the clutch C is engaged in the second speed,
The rotation of the engine 11 is transmitted to the first counter drive gear 31 via the output shaft 12, is decelerated between the first counter drive gear 31 and the first counter driven gear 32, and is driven via the output shafts 14 and 16 to drive wheels 19. Be transmitted to. At this time, the one-way clutch F becomes free. In the hybrid vehicle having the above structure, when the vehicle is driven only by the motor 15, the drive current is supplied to the motor 15 to drive the drive wheels 19. On the other hand, although the engine 11 is stopped, the clutch C is released and the one-way clutch F is released, so that the stopped state of the engine 11 can be maintained.

FIG. 9 is a schematic view of a hybrid type vehicle showing the fifth embodiment of the present invention, and FIG. 10 is an operation diagram of the hybrid type vehicle showing the fifth embodiment of the present invention. In the figure, 11 is an engine, 12 is an output shaft of the engine 11,
13 is a transmission connected to the output shaft 12,
Reference numeral 14 is an output shaft of the transmission 13, 15 is a motor, 16 is an output shaft of the motor 15, 17 is a differential device, and 19 is a drive wheel composed of front wheels or rear wheels.

The transmission 13 includes a first planetary gear unit 36 and a second planetary gear unit 3.
7, a clutch C, a brake B, a first one-way clutch F1 and a second one-way clutch F2, and the first planetary gear unit 36 includes a ring gear R ₁ , a pinion P ₁ , a carrier CR ₁ and a sun gear S ₁ , and the second planetary gear unit The unit 37 is formed of a ring gear R ₂ , a pinion P ₂ , a carrier CR ₂ and a sun gear S ₂ .

The output shaft 12 is the ring gear R ₁ of the first planetary gear unit 36, the carrier CR ₁ of the first planetary gear unit 36 is the output shaft 14, and the sun gear S ₁ of the first planetary gear unit 36 is the second planetary gear unit 37. The ring gear R ₂ of the second planetary gear unit 37 is connected to the output shaft 14 of the sun gear S ₂ . Further, the ring gear R ₁ of the first planetary gear unit 36 and the sun gear S ₁ are connected by the clutch C, the sun gear S ₁ is connected to the case 23 via the one-way clutch F1 and the brake B, and the carrier CR of the second planetary gear unit 37 is connected. ₂ is connected to the case 23 via the second one-way clutch F2.

In the hybrid vehicle having the above structure,
When the clutch C and the brake B are released in the first speed, the engine 11 rotates through the ring gear R ₁ and the carrier CR.
₁ , the sun gears S ₁ and S ₂ are idled in the opposite direction to lock the second one-way clutch F2, and the carrier C
Prevent rotation of R ₂ . The rotation of the carrier CR ₁ is also transmitted to the ring gear R ₂ . As a result, the decelerated rotation is transmitted to the output shaft 14.

When the clutch C is disengaged and the brake B is engaged in the second speed, the rotation of the sun gears S ₁ and S ₂ idling in the opposite direction in the first speed is prevented. As a result, the decelerated rotation is transmitted to the output shaft 14. When the clutch C is engaged in the third speed, the first planetary gear unit 36
The second planetary gear unit 37 and the second planetary gear unit 37 are directly connected, and the rotation of the engine 11 is directly transmitted to the output shaft 14.

In the hybrid vehicle having the above structure,
When traveling only by the motor 15, the drive current is supplied to the motor 15 to drive the drive wheels 19 and the engine 11 is stopped. At this time, the carrier CR ₁ rotates as the motor 15 rotates, but since the brake B is released when the engine 11 is stopped, the sun gear S ₁ idles. Therefore, the stopped state of the engine 11 can be maintained.

[Brief description of drawings]

FIG. 1 is a schematic diagram of a hybrid vehicle showing a first embodiment of the present invention.

FIG. 2 is a schematic view of a hybrid vehicle showing a second embodiment of the present invention.

FIG. 3 is an operation diagram of a hybrid vehicle showing first and second embodiments of the present invention.

FIG. 4 is a vehicle speed / torque relationship diagram in the first and second embodiments of the present invention.

FIG. 5 is a schematic diagram of a hybrid vehicle showing a third embodiment of the present invention.

FIG. 6 is an operation diagram of a hybrid vehicle showing a third embodiment of the present invention.

FIG. 7 is a schematic diagram of a hybrid vehicle showing a fourth embodiment of the present invention.

FIG. 8 is an operation diagram of a hybrid vehicle showing a fourth embodiment of the present invention.

FIG. 9 is a schematic view of a hybrid vehicle showing a fifth embodiment of the present invention.

FIG. 10 is an operational diagram of a hybrid vehicle showing a fifth embodiment of the present invention.

[Explanation of symbols]

11 engine 13 transmission 15 motor 22, 25, 28, 41-44 planetary gear unit 36 first planetary gear unit 37 second planetary gear unit C clutch C1 first clutch B brake F one-way clutch F1 first one-way clutch F2 second one-way clutch

Claims (1)

[Claims] 1. An engine capable of selectively driving (a),
(B) A selectively driven motor, (c) a gear unit, a friction engagement element, and a one-way clutch, and a transmission that receives the rotation of the engine to change gears. (D) One-way of the transmission A hybrid vehicle in which at least one of the clutches is disengaged so that the rotation of the motor is faster than the rotation of the engine when the engine is stopped by driving the motor. ..