JPH11321357A - Driving device for automobile - Google Patents

Abstract

PROBLEM TO BE SOLVED: To enhance a power transmission efficiency under a high running load and in a normal running in the city and to improve fuel consumption by enabling mechanical transmission of power at a plurality of fixed speed change ratios while enabling continous variable transmitting for driving or auxiliary driving by a motor in a driving device for a so-called hybrid automobile in which power is transmitted by means of a planet gear using the two kinds of power sources, of an engine and a plurality of motors. SOLUTION: In this driving device for an automobile, in addition to members connected with an input shaft 30 and an output shaft 32 out of the rotation members of a planet gear, a member A (a first sun gear 12) deceleratingly driving when it is fixed to a case 46, and a member B (a second ring gear 24) acceleratingly driving when it is fixed to the case 46, are provided, and the members A and B are enabled to be separately, or simultaneously connected with a second motor 50 by means of conical clutches 48 and 54 transmitting torque only in one direction.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a drive system for a so-called hybrid vehicle having two types of power sources, an internal combustion engine and an electric motor. The present invention relates to a vehicle drive device having a plurality of motors that can be transmitted to a vehicle.

[0002]

2. Description of the Related Art Conventionally, a driving apparatus for a vehicle which can transmit a driving force input from an engine to an output shaft via a planetary gear and has a plurality of motors has been known as an automobile driving apparatus issued by the Japan Society of Automotive Engineers. The technique described in FIG. 5 on page 17 of "Technology", January 1998 is known.

The conventional example will be described with reference to FIG.
The planetary gear 1 includes a sun gear 2, a carrier 3, and a ring gear 4.
And a pinion 5 pivotally supported by the carrier 3 and meshing with the sun gear 2 and the ring gear 4. The sun gear 2 is connected to a first motor 6, the carrier 3 is connected to a crankshaft 7 of an engine (not shown), the ring gear 4 is connected to a second motor 8, and a chain 9, a reduction gear 10 and a differential device 11 are connected. It is connected to the axle 12 through the shaft. The axle 12 is connected to left and right wheels of an automobile (not shown). The first motor 6 and the second motor 8 can rotate forward and backward, have a function as a motor and a function as a generator, and can be arbitrarily switched.

The operation of the conventional example configured as described above will be described. When power is supplied to the second motor 8 from a battery (not shown), the second motor 8 drives the wheels via the chain 9, the reduction gear 10, the differential device 11, and the axle 12, and can start and accelerate the automobile. . At this time, when the engine is stopped, the carrier 3 is also stopped, so that the sun gear 2 and the first motor 6 rotate in the reverse direction, but the first motor 6 only idles. Here, when a larger driving force is required, the electric power is also supplied to the first motor 6 while supplying the electric power to the second motor 8 so that the torque in the direction in which the sun gear 2 stops is applied. 7 rotates, so that the engine can be started.

[0005] After the engine is started, acceleration is performed as follows. The engine torque entering the carrier 3 from the crankshaft 7 is divided by the planetary gear 1. That is, a part of the engine torque passes through the sun gear 2 to drive the first motor 6 to generate electric power, and the remaining torque passes through the ring gear 4 and the output torque of the second motor 8 to the axle 1.
2 is driven. At this time, the electric power generated by the first motor 6 is supplied to the second motor 8. Therefore, if the power is continuously supplied from the battery to the second motor 8, the second motor 8 uses the electric power from the battery and the electric power generated by the first motor 6 by a part of the engine torque.
2 will be driven.

Further, since the axle 12 is also driven by a part of the engine torque through the ring gear 4, the axle 12 is driven by a part of the engine torque and the second motor 8, and its power source is the engine and the battery. Become. Here, when the power supply from the battery is stopped, the second motor 8 is driven only by the power generated by the first motor 6, and the power source for driving the axle 12 is only the engine.

The ratio (speed change ratio) of the rotation speed of the crankshaft 7 and the rotation speed of the ring gear 4 connected to the axle 12 and rotating together with the second motor 8 to the rotation speed of the carrier 3 integrated therewith is It is automatically determined by the magnitude of the engine torque, the magnitude of the output torque (load) for driving the wheels by the axle 12, and the power supplied from the battery to the second motor 8. When the speed of the vehicle is low and the engine torque is large and the load on the axle 12 is large, the rotation speed of the ring gear 4 is lower than the rotation speed of the sun gear 2, and when the speed of the vehicle gradually increases and the load on the axle 12 decreases, the sun gear 2 The speed changes steplessly so that the rotation speed of the ring gear 4 decreases and the rotation speed of the ring gear 4 increases.

When the vehicle is to be braked, the engine is stopped, the second motor 8 is switched to a generator to generate power, and the vehicle is braked. It is possible to perform so-called energy regeneration in which a part of kinetic energy is converted into electric power to charge a battery. Further, at the time of reverse traveling, the reverse driving force is obtained by reversing only the second motor 8 with the electric power supplied from the battery without turning the engine. Generally, an internal combustion engine used as an engine has a characteristic that thermal efficiency is low in a low load operation state, so that a hybrid vehicle usually avoids driving by the engine when the vehicle runs in a low load range, and generates power by the engine and By driving with a motor using the electric power charged to the battery by energy regeneration, and driving in a high-load region by the power of the engine, fuel efficiency can be improved as compared with a conventional vehicle using only an engine as a power source.

[0009]

However, in the above-described conventional example, when the vehicle is driven by the engine, a part of the power is used to generate electric power by the first motor 6, and the electric power is used to generate the second electric power. Since the axle 12 is auxiliary-driven by the motor 8, a loss is inevitably caused in the process of generating power and outputting the electric power by the motor, although partly. That is, the first motor 6
When the sun gear 2 is electrically fixed, the mechanical power is transmitted by the planetary gear 1, which is a speed increasing ratio called overdrive used for high-speed running or the like. Cannot be used for running. Therefore, in general running other than high-speed running, the first motor 6 generates electric power using a part of the driving force of the engine,
The axle 12 is auxiliary-driven by the second motor 8 by the electric power. Therefore, the product of the power generation efficiency of the first motor 6 and the output efficiency of the second motor 8 is the power transmission efficiency of the route for transmitting power by temporarily converting power to electricity. In this way, the power transmission efficiency of a route that converts power into electricity and transmits power is generally inferior to mechanical transmission of gears, chains, and the like.

[0010] For this reason, when the vehicle runs in a driving state in which a high load is applied to the engine, the power transmission ratio in the electric route is increased, which deteriorates the fuel efficiency, and partially degrades the goodness of the hybrid vehicle. There is.

Accordingly, the present invention reduces the power transmission ratio of the electric route and reduces the power of the engine mechanically during steady running when the car is traveling in an urban area, and in operating conditions such as acceleration or climbing with a large running load. The purpose is to improve the fuel efficiency by transmitting it to the axle well.

[0012]

According to a first aspect of the present invention, there is provided a vehicle driving apparatus for driving a vehicle, the driving force input to an input shaft from an engine through a planetary gear. In a motor vehicle drive device having a plurality of motors, the output shaft can be driven by a first motor among the plurality of motors, and the planetary gears are driven by a speed reduction among the rotating members. And a member B that can be fixed to the case to obtain increased speed drive among the rotating members, and the members A and B are each provided with a different motor from the first motor. It is characterized by being connectable.

According to a second aspect of the present invention, one of the other motors (second motor) can be selectively connected to the members A and B. It is characterized by being.

According to a third aspect of the present invention, the one motor (second motor) is provided.
And means for connecting member A and member B,
The cone clutch is provided with a cone ring that meshes with teeth having a helical surface, and is a conical clutch that can self-lock when torque in one direction is applied.

According to a fourth aspect of the present invention, the one motor (second motor) is provided.
Is connectable simultaneously with both the member A and the member B.

According to a fifth aspect of the present invention, the member A can be connected to the another one motor (second motor), and the member A can be connected to the other motor (second motor). One motor is always connected to another motor (third motor).

According to a sixth aspect of the present invention, the planetary gear includes a first sun gear, a first ring gear, and a first carrier that supports a first pinion meshing with the first sun gear. A first planetary gear, a second planetary gear having a second sun gear, a second ring gear, and a second carrier supporting a second pinion meshing with the second sun gear and the second ring gear;
A sun gear and a second sun gear are connected, a first limb gear and a second carrier are connected, a first carrier is connected to one of an input shaft and an output shaft, and a first ring gear and a second carrier are connected to an input shaft. When the first carrier is connected to the input shaft while the first carrier is connected to the input shaft, the second ring gear is used as the member A, the first sun gear and the second sun gear are used as the member B, and the first carrier is output. When connected to a shaft, the first sun gear and the second sun gear are made members A, and the second ring gear is made members B.

According to a seventh aspect of the present invention, the planetary gear includes a first sun gear, a first ring gear, and a first carrier that supports a first pinion meshing with the first sun gear. A first planetary gear, a second planetary gear having a second sun gear, a second ring gear, and a second carrier supporting a second pinion meshing with the second sun gear and the second ring gear;
The ring gear and the second carrier are connected to an output shaft, the first carrier and the second ring gear are connected to an input shaft, the second sun gear is a member A, and the first sun gear is a member B. .

According to an eighth aspect of the present invention, the planetary gear has a first sun gear meshed with a ring gear via a first pinion, and a second sun gear connected to the first pinion and the second pinion. The pinion meshes with the ring gear via the pinion, both pinions are supported by the carrier, one of the ring gear and the carrier is connected to the input shaft, the other of the ring gear and the carrier is connected to the output shaft, and the ring gear and the input shaft are connected. Are connected, the first sun gear is made member A and the second sun gear is made member B. When the ring gear and the output shaft are connected, the second sun gear is made member A and the first sun gear is made member B. It is characterized by the following.

[0020]

According to the first aspect of the present invention, the driving force input to the input shaft from the engine is:
In a motor vehicle drive device that can be transmitted to an output shaft via a planetary gear and has a plurality of motors, the output shaft can be driven by a first motor among the plurality of motors, and the planetary gear is formed by the rotating member. A member A that can be fixed to the case to obtain a deceleration drive, and a member B that can be fixed to the case to obtain a speed-up drive among the rotating members, wherein the members A and B are each a first motor. Because it is configured to be connectable to another motor, it performs stepless shifting by controlling the motor, and performs deceleration drive of mechanical transmission by fixing member A to the case by the motor, and fixes member B to the case by the motor. In this way, the mechanical transmission is accelerated.

According to a second aspect of the present invention, one of the other motors (second motor) is selectively connected to the member A and the member B. Because it was configured to be connectable, 1
The stepless speed change and mechanical deceleration drive described above are performed by switching the connection relationship between the motors.

According to a third aspect of the present invention, the means for connecting the one motor (second motor) and the members A and B has a helical surface. With a cone ring that meshes with teeth, the cone clutch can be self-locked when one-way torque is applied, so the cone clutch is connected only when driving from the engine, and the connection is automatically released when the driving force is lost You.

Further, in the vehicle driving apparatus according to the present invention, the one motor (second motor) is configured to be simultaneously connectable to both the member A and the member B. By connecting both at the same time, the entire planetary gear is mechanically integrated to perform direct connection drive.

According to a fifth aspect of the present invention, in the vehicle driving apparatus of the present invention, the member A can be connected to the another one motor (second motor) and a plurality of motors can be connected. Since the one motor is always connected to another motor (third motor), the connection of the second motor is changed from the member A to the member A while the member A is fixedly decelerated and driven by the third motor. Switch to B to prepare for drive mode change.

According to a sixth aspect of the present invention, the planetary gear includes a first sun gear, a first ring gear, and a first carrier that supports a first pinion engaged with the first sun gear and the first ring gear. A first planetary gear having a second sun gear, a second ring gear, and a second planetary gear having a second carrier supporting a second pinion meshed with the second sun gear and the second ring gear. Connecting the first ring gear and the second carrier, connecting the first carrier to one of the input shaft and the output shaft, connecting the first ring gear and the second carrier to the other of the input shaft and the output shaft, When the first carrier is connected to the input shaft, the second ring gear is used as the member A and the first ring gear is used as the first member.
When the sun gear and the second sun gear are members B and the first carrier is connected to the output shaft, the first sun gear and the second sun gear are members A and the second ring gears are members B. Therefore, the members A and the third motor And the second motor and the member A and the member B can be selectively connected to each other, so that in addition to the stepless speed change, each drive of deceleration, direct connection, and speed increase at a fixed speed ratio is provided. I do.

According to a seventh aspect of the present invention, the planetary gear includes a first sun gear, a first ring gear, and a first carrier that supports a first pinion engaged with the first sun gear and the first ring gear. A first planetary gear having a second sun gear, a second ring gear, and a second planetary gear having a second carrier that supports a second pinion meshing with the second planetary gear. The first ring gear and the second carrier are connected to an output shaft. Since the first carrier and the second ring gear are connected to the input shaft, and the second sun gear is the member A and the first sun gear is the member B, the member A and the third motor are always connected and the second motor is And members A and B can be selectively connected, so that in addition to the stepless speed change, each drive of deceleration, direct connection, and speed increase is performed at a fixed speed ratio.

Further, in the vehicle driving apparatus according to the present invention, the planetary gear has a first sun gear meshed with a ring gear via a first pinion, and a second sun gear meshes with the first pinion. The second pinion meshes with the ring gear, both pinions are supported by the carrier, one of the ring gear and the carrier is connected to the input shaft, and the other of the ring gear and the carrier is connected to the output shaft. When the input shaft is connected, the first sun gear is member A and the second sun gear is member B. When the ring gear is connected to the output shaft, the second sun gear is member A and the first sun gear is member B. Therefore, the member A and the third motor are always connected, and the second motor is selectively connected to the members A and B. By enabling coupling, in addition to the stepless speed change, performs the driving of the deceleration and direct-acceleration at a fixed gear ratio.

[0028]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a skeleton diagram of a main part in a vehicle drive device of the present invention. First planetary gear 10
Are the first sun gear 12, the first ring gear 14, the first
It is composed of a carrier 16 and a first pinion 18 pivotally supported by the first carrier 16 and meshing with the first sun gear 12 and the first ring gear 14. Second planetary gear 20
Is a second sun gear 22, a second ring gear 24, a second
It comprises a carrier 26 and a second pinion 28 pivotally supported by the second carrier 26 and meshing with the second sun gear 22 and the second ring gear 24.

The first carrier 16 is connected to the input shaft 30. The input shaft 30 is driven by the engine 70.
The output shaft 32 is connected to the first ring gear 14 and the second carrier 26 and also to the first motor 34. The output shaft 32 is integrated with a drive gear 36, and the drive gear 36 is connected to an output gear 40 via an idler gear 38. The output gear 40 includes a differential device 42 and is connected to the wheels of an automobile (not shown) via left and right axles 44a and 44b.

The output shaft 32 is connected to the rotor 34a of the first motor 34, and the stator 3 of the first motor 34
4b is fixed to the case 46. First sun gear 12
And the second sun gear 22 are integrally connected and can be connected to the rotor 50a of the second motor 50 via the first conical clutch 48, and the stator 50b of the second motor 50 is fixed to the case 46. Have been.

The first sun gear 12 is connected to the first cone clutch 4
When fixed to the case 46 via the second motor 8 and the second motor 50, mechanical power transmission can be performed from the input shaft 30 to the output shaft 32 at a fixed speed increase ratio as described later.
A member such as the first sun gear 12 that can be mechanically accelerated by being fixed to the case 46 is referred to as a member B.

The second ring gear 24 includes a third motor 52
And the rotor 50a of the second motor 50 via the second conical clutch 54. The stator 52b of the third motor 52 is fixed to the case 46. When the second ring gear 24 is fixed to the case 46 by the third motor 52, mechanical power can be transmitted from the input shaft 30 to the output shaft 32 at a fixed reduction ratio as described later. A member such as the second ring gear 24, which can be mechanically decelerated by being fixed to the case 46, is referred to as a member A.

The first conical clutch 48 and the second conical clutch 54 are arranged symmetrically to each other as shown in FIG. 1, but both have a structure as shown in FIGS. 6 and 7. FIG. 6 is a cross-sectional view of a main part of the first conical clutch 48, showing a portion above the shaft center. FIG. 7 shows a cross section taken along line CC of FIG. Hereinafter, the first conical clutch 48 will be described with reference to FIGS. 6 and 7 as an example.

First sun gear 12 and second sun gear 22
A first hub 56 and a first cone ring 58
Means that one is a helical surface 56a, 58a and the other is a flat surface 5a.
The first cone ring 58 has a conical friction surface 58d on the outside, and the conical friction surface 58d is in contact with the second motor 5c.
First outer ring 6 integrated with the zero rotor 50a
0 corresponds to the inner surface 60d of the cone.

The first cone ring 58 has a groove 58e,
The first fork 62 is engaged with the groove 58e, and the first cone ring 58 can be moved left and right as necessary by an actuator (not shown). Although not shown, the rotor 50a of the second motor 50 and the first hub 56 are supported by the case 46 via bearings or the like so as not to move in the axial direction.

The teeth 56c, 58c in which the first hub 56 and the first cone ring 58 are engaged with each other are helical surfaces 56a, 58a because one of them is a helical surface 56a, 58a.
When the torque in the direction in which the force acts on the side is transmitted, thrust is generated, and the first hub 56 and the first cone ring 58 are separated from each other.
At the right side, and the conical friction surface 58d and the first
The conical inner surfaces 60d of the outer ring 60 are pressed together.

Here, the function of a one-way clutch can be obtained by appropriately setting the leads of the helical surfaces 56a, 58a and the cone angles of the conical friction surface 58d and the conical inner surface 60d. That is, the first cone ring 58
In a state where a torque acts in one direction between the first fork 62 and the first outer ring 60, the first cone ring 58 is moved to the right by the first fork 62 so that the conical friction surface 58 d
Lightly pressed against the inner surface 60d of the cone, the conical friction surface 58
A friction torque is generated between the helical surfaces 56a and 58a by the friction torque between the helical surfaces 56a and 58a.

With this thrust, the conical friction surface 58d and the conical inner surface 60d are pressed more strongly, and a large torque can be transmitted. Then, as a result, the first cone ring 58 and the first outer ring 60
And are integrally connected. The load pressed by the first fork 62 only triggers the self-locking described above, requiring only a slight force and pressing only at the beginning of connection. It is moved in the opposite direction (left side in FIG. 6) to prevent contact between the conical friction surfaces 58d and 60d.

Even in the case of the above-described self-locking connection bear, if a torque in the opposite direction is applied, the teeth 56
Since the thrust is not generated due to the force acting on the flat surfaces 56b, 58b of c, 58c, the self-lock is released and the connection of the first conical clutch 48 is automatically released. This is the function of the one-way clutch that transmits only one-way torque.

The second conical clutch 54 is provided between the second ring gear 24 and the second motor 50 symmetrically with the first conical clutch 48 as described above. Similarly, the second ring gear 24 and the second motor 50 can be connected by controlling the second fork (not shown), and power can be transmitted in only one direction.

The first conical clutch 48 and the second conical clutch 54 can be operated independently of each other, and can be selectively connected to one another or both at the same time. The first planetary gear 10 and the entire second planetary gear 20 are integrally connected as described later.

The first motor 34, the second motor 50, and the third motor 52 can switch the rotation direction between forward rotation and reverse rotation, respectively, and have a motor function and a generator function. It can be switched arbitrarily by a command from the controller that does not.

An automobile equipped with the driving device shown in FIG.
Engine 70, first motor 34 and second motor 50
And a third motor 52, which constitutes a so-called hybrid vehicle. Next, the operation of the driving device having the above configuration will be described. In the following description, "forward rotation" refers to rotation in the same direction as the rotation direction of the engine 70, and "reverse rotation" refers to rotation in the opposite direction.

First, starting and acceleration by electric power supplied from a battery (not shown) will be described. Usually, when the vehicle starts, the engine 70 is stopped. First, the first motor 34 from the battery via the controller
Current in the direction of positive rotation. Then, the output shaft 32 connected to the rotor 34a of the first motor 34 drives the left and right axles 44a, 44b via the idler gear 38, the output gear 40, and the differential device 42. Wheels (not shown) are driven by axles 44a and 44b, and the vehicle starts and starts accelerating.

At this time, since the engine 70 is stopped, the first carrier 16 connected to the input shaft 30 does not rotate, the first sun gear 12 and the second sun gear 22 rotate in reverse, and the second ring gear 24 and The third motor 52 rotates forward, but does not transmit any torque, but only idles. Such a state in which only the first motor is driven is referred to as a first drive mode.

Next, the operation for starting the engine 70 to further increase the driving force will be described. In this case, in addition to the driving by the first motor 34, the third motor 52 that is rotating forward causes the third motor 52 to generate power, so that the torque in the reverse rotating direction acts on the second ring gear, and the first carrier 16 rotates in the forward rotating direction. And the engine 70 through the input shaft 30
To rotate. Here, when control such as supplying fuel to the engine 70 or connecting an ignition circuit (not shown) is performed, the engine 70 starts.

When the engine 70 starts and starts driving,
Power transmission is performed as follows. The power of the engine 70 enters the first carrier 16 and is torque-divided by the first planetary gear 10, and partly passes through the first ring gear 14 and the output shaft 3.
2 from the first sun gear 12 to the second
The rotation is transmitted to the sun gear 22 and the second ring gear 24 is rotated in the reverse direction via the second pinion 28.

At this time, the third motor 52 is immediately switched to the reverse-rotating generator, and the second conical clutch 48 is pressed and connected with the second fork (not shown). That is, the second conical clutch 48 is configured to self-lock when driven in the reverse rotation direction from the second ring gear 22. With this self-lock, the second motor 50
Are connected to the second ring gear 22 and rotate reversely with the third motor 52. Then, the second motor 50 is also caused to generate electric power together with the third motor 52, and the electric power is supplied to the first motor 34.

When the third motor 52 and the second motor 50 generate electric power while rotating in the reverse direction, a torque in the normal rotation direction acts on the second carrier 26 connected to the output shaft 32. Planetary gear 10, second planetary gear 2
The ratio of the torque mechanically transmitted to the output shaft 32 via 0 is: That is, if the ratio of the number of teeth of the first sun gear 12 to the number of teeth of the first ring gear 14 is α1, and the ratio of the number of teeth of the second sun gear 22 to the number of teeth of the second ring gear 24 is α2, (α1 + α2 + α1 · α2) / (Α
2 + α1 · α2) times increased torque is transmitted mechanically.

The torque for actually driving the output shaft 32 is obtained by adding the output torque of the first motor 34 to the mechanical transmission. Therefore, the first from the battery
If power is continuously supplied to the motor 34, the first motor 3
4 is driven by the electric power from the battery and the electric power generated by the third motor 52 and the second motor 50, and the power source for driving the output shaft 32 is the engine 70 and the battery.

Here, when the power supply from the battery is stopped, the first motor 34 is driven only by the power generated by the third motor 52 and the second motor 50, and the output shaft 32 is connected to the first planetary gear 10 The power source is only the engine 70 including the torque mechanically transmitted via the second planetary gear 20. The state in which the third motor 52 and the second motor 50 are driven while generating power in the reverse rotation is called a second drive mode.

The ratio (speed change ratio) of the rotation speed of the input shaft 30 to the rotation speed of the output shaft 32 in the second drive mode is determined by the magnitude of the torque of the engine 70 entering the input shaft 30 and the output shaft 32 driving the automobile. And the power supplied from the battery to the first motor 34. Further, the electric power generated by the third motor 52 and the second motor 50 also changes according to them.

That is, when the speed of the vehicle is low and the torque of the engine 70 is large and the load on the output shaft 32 is large, the rotation speed of the input shaft 30 is significantly higher than the rotation speed of the output shaft 32.
When the speed of the vehicle gradually increases and the load on the output shaft 32 decreases, the rotation speed of the output shaft 32 increases, and conversely, the input shaft 30 increases.
Changes steplessly so that the number of rotations decreases. At the same time, the rotation speeds of the third motor 52 and the second motor 50 also decrease.

When the vehicle speed further increases or the rotation speed of the engine 70 decreases, the second ring gear 24
At the same time, the rotation speeds of the third motor 52 and the second motor 50 decrease, and eventually stop. Second ring gear 24
In order for the battery to stop, it is necessary to supply electric power from the battery to at least the third motor 52 so as to generate torque in the forward rotation direction, and to electrically fix the torque to the case 46.

Normally, the motor has the characteristic of producing the largest amount of torque when the number of revolutions is zero.
The electric power required to fix the motor 4 to the case 46 is small, and the third motor 52 only needs to be able to start the engine 70 and exert the power to maintain the fixing of the second ring gear 24. The capacity is smaller than that of the motor 50.

As described above, when the second ring carrier 24 is stopped together with the third motor 52, the ratio of the rotation speed of the input shaft 30 to the rotation speed of the output shaft 32 (speed ratio: output shaft rotation speed /
The input shaft rotation speed) is the reciprocal of the aforementioned torque ratio (α2 + α1)
.Alpha.2) / (. Alpha.1 + .alpha.2 + .alpha.1.alpha.2), and mechanical power transmission with a fixed reduction ratio. Here, the second ring gear 24 fixed to the case 46 in order to obtain a fixed reduction ratio is the member A described above. Such a state of mechanical power transmission with a fixed reduction ratio is referred to as a third drive mode.

Also in the third drive mode, it is possible to supply electric power from the battery to the first motor 34 to add to the power of mechanical transmission, and conversely, to perform the first drive while performing mechanical drive. The battery can be charged by causing the motor 34 to generate power. In the third drive mode, the first sun gear 12 and the second sun gear 22 are rotating forward.

In the third drive mode, the third motor 5
When the power is supplied from the battery to the second motor 50 and the second ring gear 24 is rotated forward while the second ring gear 24 is fixed, the self-lock is released and the connection of the second conical clutch 54 is released. 2 The number of rotations of the motor 50 increases and the first sun gear 12 and the second sun gear 22
And almost the same.

At this time, when the first fork 62 is actuated, the second motor 50 is switched to a generator to connect the first conical clutch 48, and the power supply to the third motor is stopped. That is, the first conical clutch 48
The second motor 50 is connected to the first sun gear 12 and the second sun gear 22 because the first sun gear 12 and the second sun gear 22 are configured to self-lock in a direction in which the second motor 50 is driven by a forward rotation from the first sun gear 12 and the second sun gear 22. , And generate power with forward rotation.

The electric power generated by the second motor 50 is the first electric power.
It is supplied to a motor 34. In this case, the battery can also supply power to the first motor 34. Second
When the motor 50 generates electric power, the ratio of the torque mechanically transmitted from the first carrier 16 to the first ring gear 14 becomes 1 / (1 + α1). That is, although the torque mechanically transmitted to the output shaft 32 is smaller than the torque of the engine 70 entering the input shaft 30, the output torque of the first motor 34 is further applied to the output shaft 32.

Also in this case, the ratio (speed change ratio) of the rotation speed of the input shaft 30 to the rotation speed of the output shaft 32 is determined by the magnitude of the torque of the engine 70 entering the input shaft 30 and the torque of the output shaft 32 driving the automobile. It is automatically determined by the magnitude of (load) and the electric power supplied from the battery to the first motor 34, and the gear ratio changes steplessly. Also, the second motor 5
The power generated by 0 also changes accordingly. The second ring gear 24 and the third motor 52 idle in the forward rotation direction. As described above, the first sun gear 12 is driven by the forward rotation, the second motor 50 generates power to supply power to the first motor 34, and the rotation speed of the output shaft 32 is lower than the rotation speed of the input shaft 30. Is called a fourth drive mode.

When the speed of the vehicle increases or the rotation speed of the engine 70 decreases, the rotation speeds of the output shaft 32 and the input shaft 30 eventually become almost the same. Here, when the second fork is operated again, the second conical clutch 54 can be connected. At the same time, the power generation by the second motor 50 is stopped. That is, in the fourth drive mode, the second ring gear 24 idles in the forward rotation direction at a rotation speed slightly lower than the rotation speed of the input shaft 30, but when the rotation speeds of the output shaft 32 and the input shaft 30 become substantially the same, The rotation speed of the second ring gear 24 is also substantially the same.

The second conical clutch 54 moves the second conical clutch 54 in the reverse rotation direction.
When the motor 50 is driven, self-locking is possible. Therefore, a torque in the reverse rotation direction acts on the second cone clutch 54, and a torque in the forward rotation direction acts on the first cone clutch 48, so that the double cone clutch 54, 48 are in a self-lock state. For this reason, the first planetary gear 10, the second planetary gear 20, the second motor 50, the third motor 52, the output shaft 32, and the first motor 34 all rotate integrally with the input shaft 30, and Shaft 30 and output shaft 32
Is directly connected mechanically.

The state in which the input shaft 30 and the output shaft 32 are mechanically directly connected to each other and the speed ratio becomes 1 is called a fifth drive mode. Since this direct connection is maintained purely mechanically, the power consumed for power transmission is zero. Of course,
Also in the fifth drive mode, it is possible to supply electric power from the battery to the first motor 34 to increase the mechanical power transmission, and conversely, to perform the first direct drive while performing the mechanical direct drive.
The battery can be charged by causing the motor 34 to generate power.

In this state, the second motor 50 is again caused to generate power and supplied to the first motor 34 to control the rotation speed of the output shaft 32 to be higher than that of the input shaft 30.
The connection of the conical clutch 54 is released, and the second motor generates electric power via the first sun gear 12 with a part of the power of the engine 70 in the same manner as in the above-described fourth drive mode.
4 will be driven.

Also in this case, the first driving mode is used similarly to the fourth driving mode.
The ratio of the torque mechanically transmitted from the carrier 16 to the first ring gear 14 is 1 / (1 + α1), and the gear ratio is the magnitude of the torque of the engine 70 and the magnitude of the torque (load) of the output shaft 32. And the power supplied from the battery to the first motor 34 in a stepless manner. In addition, the electric power generated by the second motor 50 also changes according to them. In this manner, the second sun gear 12
A state in which the motor 50 generates power in the forward rotation to supply power to the first motor 34 and the rotation speed of the output shaft 32 is higher than the rotation speed of the input shaft 30 is referred to as a sixth drive mode.

In this state, when the speed of the automobile further increases or the number of revolutions of the engine 70 decreases, the rotation of the first sun gear 12 eventually stops. At this time, electric power is supplied from the battery to the second motor 50 so as to generate a torque in the reverse rotation direction, and the first sun gear 12 is electrically fixed to the case 46. The first sun gear 12 is connected to the case 46
, The gear ratio becomes (1 + α1), and the input shaft 3
From 0, the output shaft 32 is driven at an increased speed at a fixed speed ratio. Here, in order to obtain a fixed speed increase ratio, case 46
The first sun gear 12 is fixed to the member B as described above.
Call. In addition, a state in which the motor is mechanically driven at the increased speed at the fixed gear ratio is referred to as a seventh drive mode.

Also in the seventh drive mode, it is possible to supply electric power from the battery to the first motor 34 and further to the third motor 52 to increase mechanical power transmission, and conversely, It is also possible to charge the battery by causing the first motor 34 to generate electric power while increasing the speed.

Next, when gradually reducing the speed of the vehicle,
And the case of braking will be described. In any of the above-described first to seventh drive modes,
When the driver releases the throttle pedal of the vehicle or depresses the brake pedal to stop the braking, the driving is immediately stopped, the engine 70 is stopped, and the first motor 34 is caused to generate power.

The first cone clutch 48 and the second cone clutch 54 are both self-locked and capable of transmitting power only when driven by the engine 70. Therefore, the self-lock is immediately performed when the engine 70 is stopped. It is released. By controlling the amount of power generated by the first motor 34, appropriate braking is performed. In addition, a part of the kinetic energy of a car, which was conventionally discarded by converting it into heat with a friction brake, is converted into electricity and stored in a battery. It can be performed. The electric power stored in the battery during energy regeneration is used at the time of accelerating the vehicle next time, thereby obtaining the effect of reducing the fuel consumption of the vehicle.

Next, a case where the vehicle is driven backward will be described. The reverse of the vehicle can be accelerated from the start by rotating the first motor 34 in the reverse direction by supplying power from the battery. In this case, since the engine 70 remains stopped, the first sun gear 12, the second sun gear 22
Rotates forward, and the second ring gear 24 rotates reversely.

In the reverse drive, when the driving force is insufficient only with the output of the first motor 34, the battery is removed from the battery while maintaining the relationship between the rotational speeds of the first sun gear 12, the second sun gear 22, and the second ring gear 24. The third motor 52 is driven in the reverse rotation direction by the power supply of
The first conical clutch 48 is connected to cause the second motor 50 to generate power via the second sun gear 22. By doing so, the second carrier 26 is driven backward without applying torque to the engine, so that the reverse driving force can be applied while the engine is stopped.

It should be noted that even when the vehicle is moving backward, the engine 70 is rotated to connect the first conical clutch 48, and the second motor 50 can generate electric power via the second sun gear 22. Since the forward rotation torque acts on the one ring gear 14, the reverse driving force is reduced accordingly. Further, the first motor 34 is also used for reverse braking.
By regenerating power, energy regeneration can be performed in the same manner as in forward travel.

As described above, in the embodiment of FIG. 1, the second ring gear 24 of the member A and the member B
The first drive mode is controlled by the connection relationship between the first sun gear 12 and the second motor 50 and the control such as the driving and power generation of the first motor 34, the second motor 50, and the third motor 52, and the fixing to the case 46. To a seventh drive mode to drive the automobile.

In particular, the speed can be changed steplessly from the start of vehicle speed 0 to the seventh drive mode, and the three speeds of deceleration, direct connection, and acceleration can be obtained.
The greatest feature is that mechanical power transmission of fixed speed ratios of various kinds is possible. That is, in the mechanical power transmission, since there is no power transmission of the electric route for driving the first motor 34 by generating power by the power of the engine 70, the power transmission efficiency is higher than that of the conventional example especially in the third drive mode and the fifth drive mode. The third drive mode of deceleration is used during low-speed acceleration or climbing a hill with a large running load, and the third drive mode of deceleration or the fifth drive mode directly connected according to the vehicle speed during steady driving in a city. On the other hand, when driving at high speed, the fuel efficiency of the automobile can be improved by increasing the drive ratio in the seventh drive mode of increasing speed.

FIG. 2 is a skeleton diagram showing another embodiment of the vehicle drive device of the present invention. First, the description will focus on the differences from the embodiment of FIG. Although having two sets of planetary gears 10 and 20 is the same as FIG. 1, the first carrier 16 and the second ring gear 24 are connected and also connected to the input shaft 30. The output shaft 32 is connected to the second carrier 26 and also to the output shaft 32.
Is also linked.

The first sun gear 12 has a first conical clutch 48.
Can be connected to the second motor 50 and constitute a member B, and the second sun gear 22 is connected to the third motor 52
, And can also be connected to the second motor 50 via the second conical clutch 54 to form the member A.

Although the detailed description is omitted,
Each motor 34, 50, 52 and first conical clutch 4
8. By controlling the second conical clutch 54 in the same manner as in the embodiment of FIG. 1, various driving from the first driving mode to the seventh driving mode becomes possible. The same applies to braking and reverse driving. Therefore, also in the embodiment of FIG.
A stepless speed change is possible, and the relationship between the gear ratio α1, α2 of each of the planetary gears 10 and 20 and the speed ratio is different from that of the embodiment of FIG.
Mechanical power transmission can be performed at various speed ratios, and an appropriate drive mode can be selected according to the driving conditions to drive the vehicle with good fuel efficiency.

Next, FIG. 3 is a skeleton diagram showing another embodiment of the vehicle drive device of the present invention. FIG.
1, the connection relationship between the first planetary gear 10 and the second planetary gear 20 is exactly the same as in the embodiment of FIG.
The connection relationship between the input shaft 30 and the output shaft 32 is reversed, and the input shaft 30 and the output shaft 32 extend in opposite directions with the same axis. That is, the input shaft 30 is connected to the first ring gear 14
The output shaft 32 is connected to the first carrier 16 and also to the first motor 34.

The second ring gear 24 can be connected to the second motor 50 by the first conical clutch 48 and constitutes a member B. The first sun gear 12 and the second sun gear 22 are always connected to the third motor 52. And the second motor 50 via the second conical clutch 54.
Can be connected to each other and constitute the member A. The embodiment shown in FIG. 3 is suitable for a rear-wheel drive vehicle.

Although the detailed description is omitted,
Each motor 34, 50, 52 and first conical clutch 4
8. By controlling the second conical clutch 54 in the same manner as in the embodiment of FIG. 1, various driving from the first driving mode to the seventh driving mode becomes possible. The same applies to braking and reverse driving. Therefore, also in the embodiment of FIG.
A stepless speed change is possible, and the relationship between the gear ratio α1, α2 of each of the planetary gears 10 and 20 and the speed ratio is different from that of the embodiment of FIG.
Mechanical power transmission can be performed at various speed ratios, and an appropriate drive mode can be selected according to the driving conditions to drive the vehicle with good fuel efficiency.

FIG. 4 is a skeleton diagram showing another embodiment of the vehicle drive device of the present invention. FIG.
, The planetary gear 10 has a so-called double-row configuration,
A first sun gear 12, a second sun gear 22, a ring gear 14, a carrier 16, a first pinion 18 pivotally supported by the carrier 16 and meshing with the first sun gear 12 and the ring gear 14, and a first pinion 18 similarly pivotally supported by the carrier 16; 1
The second pinion 28 is configured to mesh with the pinion 18 and the second sun gear 22. The carrier 16 is connected to the input shaft 30. The input shaft 30 is driven by the engine 70.

The output shaft 32 is connected to the ring gear 14 and also to the first motor 34. The output shaft 32 is integrated with the drive gear 36 and the drive gear 3
Reference numeral 6 drives the automobile via an idler gear (not shown) as in the embodiment of FIG. The first sun gear 12 can be connected to the second motor 50 by a first conical clutch 48 and constitutes a member B.
Is always connected to the third motor 52 and
The member A can also be connected to the second motor 50 via the conical clutch 54.

Although the detailed description is omitted,
Each motor 34, 50, 52 and first conical clutch 4
8. By controlling the second conical clutch 54 in the same manner as in the embodiment of FIG. 1, various driving from the first driving mode to the seventh driving mode becomes possible. The same applies to braking and reverse driving. Therefore, also in the embodiment of FIG.
While the stepless speed change is possible, the relationship between the gear ratio α1, α2 of the planetary gear 10 and the speed ratio is different from that of the embodiment of FIG. 1, but three types of speed change fixed at deceleration, direct connection, and speed increase. Mechanical power transmission is possible at the ratio, and an appropriate drive mode can be selected according to the traveling conditions, and traveling with good fuel efficiency can be performed.

Next, FIG. 5 is a skeleton diagram showing another embodiment of the vehicle drive device of the present invention. The planetary gear 10 has a double-row configuration as in the embodiment of FIG. 4, and includes a first sun gear 12, a second sun gear 22, a ring gear 14, a carrier 16, and a first sun gear A first pinion 18 meshing with the ring gear 12 and the ring gear 14;
The second pinion 28 is configured to mesh with the pinion 18 and the second sun gear 22.

The ring gear 14 is connected to the input shaft 30. The input shaft 30 is driven by the engine 70. The output shaft 32 is connected to the carrier 16 and also to the first motor 34. The output shaft 32 is integrated with a drive gear 36, and the drive gear 36 drives the vehicle via an idler gear (not shown) as in the embodiment of FIG. The second sun gear 22 is a first conical clutch 4
8, the first sun gear 12 is connectable to the second motor 50 and constitutes a member B.
2 and the second conical clutch 54
Can also be connected to the second motor 50 via the.

Although a detailed description is omitted, in the above configuration,
Each motor 34, 50, 52 and first conical clutch 4
8. By controlling the second conical clutch 54 in the same manner as in the embodiment of FIG. 1, various driving from the first driving mode to the seventh driving mode becomes possible. The same applies to braking and reverse driving. Therefore, also in the embodiment of FIG.
While the stepless speed change is possible, the relationship between the gear ratio α1, α2 of the planetary gear 10 and the speed ratio is different from that of the embodiment of FIG. 1, but three types of speed change fixed at deceleration, direct connection, and speed increase. Mechanical power transmission is possible at the ratio, and an appropriate drive mode can be selected according to the traveling conditions, and traveling with good fuel efficiency can be performed.

As described above, in each of the embodiments of the present invention, in any of the embodiments, the speed can be steplessly changed from the start to the speed-up drive, and the three steps of deceleration, direct connection, and speed-up can be achieved.
A major feature is that mechanical power transmission is possible with a fixed type of gear ratio. Therefore, the vehicle can be driven smoothly without any incongruity by stepless and smooth shifting, and the electric drive and the mechanical drive are optimized in the first drive mode and other drive modes by taking advantage of the hybrid vehicle. To improve fuel efficiency under all driving conditions.

In particular, in mechanical power transmission with a fixed gear ratio, since there is no power transmission in the electric route and the power transmission efficiency is high, the third drive mode of deceleration is used in running with a large load such as acceleration or uphill. In steady driving in the city, various driving is performed by frequently using the third driving mode of deceleration or the fifth driving mode directly connected in accordance with the vehicle speed, and driving in the seventh driving mode of increasing speed in high speed driving. Under the conditions, control can be performed to maximize fuel efficiency.

The vehicle drive system according to the present invention, based on the general knowledge of those skilled in the art, makes active use of the engine and each motor for smooth gear shifting while making heavy use of mechanical transmission of a fixed gear ratio. Control, program the shift control appropriately to use a fixed gear ratio to improve fuel efficiency, and further connect the second motor to the members A and B by other means. The present invention can be implemented in a mode in which a change or improvement such as a clutch having a structure is added.

[0091]

As described above, according to the vehicle drive device of the present invention, the following effects can be obtained. (1) According to the vehicle driving device of the present invention described in claim 1, the driving force input from the engine to the input shaft can be transmitted to the output shaft via the planetary gear, and the plurality of motors are provided. In an automobile drive device, the output shaft can be driven by a first motor among a plurality of motors,
The planetary gear includes a member A of the rotating members that can be fixed to the case to obtain a deceleration drive, and a member B of the rotating members that can be fixed to the case to obtain an increased speed drive. Is the first
Because it is configured to be connectable to a different motor from the motor,
A stepless speed change can be performed by the control of the motor, and the member A is fixed to the case by the motor to reduce the mechanical transmission, and the member B is fixed to the case by the motor to reduce the mechanical transmission. Since the speed-up drive can be performed, there is no power transmission in the electric route in the mechanical transmission, and the power transmission efficiency in the deceleration drive is higher than in the related art, so that the fuel efficiency of the vehicle can be improved.

(2) According to the vehicle drive device of the present invention described in claim 2, one motor (second motor)
However, since it is configured such that it can be selectively connected to the members A and B, stepless speed change and mechanical deceleration drive and speed increase drive can be performed without increasing the motor capacity of the entire drive device. Therefore, the weight and space of the driving device can be saved, and the manufacturing cost can be reduced.

(3) According to the vehicle driving apparatus of the third aspect of the present invention, one motor (second motor)
The means for selectively coupling the member A and the member A is a conical clutch that includes a cone ring that meshes with teeth having a helical surface and is capable of self-locking when a torque in one direction is applied. Only when a torque in the direction is applied, the conical clutch is connected, and when the driving force is lost, the connection is automatically released.
It is possible to smoothly shift from the mechanical drive mode of direct connection and speed increase to the drive mode with no step, and to switch from the drive state to the braking action.

(4) According to the vehicle driving device of the present invention, one motor (second motor) is provided.
And the member A and the member B can be connected at the same time. By connecting both at the same time, in addition to the above-described deceleration drive and speed-up drive, the entire planetary gear is integrally mechanically driven directly. Therefore, the power transmission of the electric route is also eliminated, the power transmission efficiency is high, and the fuel efficiency under running conditions suitable for direct drive such as steady running can be improved.

(5) According to the vehicle driving apparatus of the present invention, the member A can be connected to the second motor and is always connected to the third motor. Switching the connection of the second motor from member A to member B while performing deceleration drive in the third drive mode by fixing the member A to the case by the motor, and smoothly changing to the stepless shift in the fourth drive mode. Can be migrated.

(6) According to the vehicle driving apparatus of the present invention, the planetary gear includes a first sun gear, a first ring gear, and a first carrier that supports a first pinion engaged with the first sun gear and the first ring gear. A first planetary gear having a second sun gear, a second ring gear, and a second planetary gear having a second carrier supporting a second pinion meshed with the second sun gear and the second ring gear. Connecting the first ring gear and the second carrier, connecting the first carrier to one of the input shaft and the output shaft, connecting the first ring gear and the second carrier to the other of the input shaft and the output shaft, When the first carrier is connected to the input shaft, the second ring gear is used as the member A and the first ring gear is used as the first member.
When the sun gear and the second sun gear are members B and the first carrier is connected to the output shaft, the first sun gear and the second sun gear are members A and the second ring gears are members B. Therefore, the members A and the third motor And the second motor and the member A and the member B can be selectively connected to each other.
Each drive of direct connection and speed increase can be performed, and various drive modes can be properly used according to running conditions to improve fuel efficiency.

(5) According to the vehicle driving apparatus of the present invention, the planetary gear includes a first sun gear, a first ring gear, and a first carrier that supports a first pinion engaged with the first sun gear and the first ring gear. A first planetary gear having a second sun gear, a second ring gear and a second planetary gear having a second carrier supporting a second pinion meshing with the second sun gear and the second ring gear. A shaft is connected to the first carrier and the second ring gear to the input shaft, and the second sun gear is the member A and the first sun gear is the member B. The motor is always connected and the second motor can be selectively connected to the member A and the member B. In addition to the simple structure, the speed can be changed steplessly and the fixed. It becomes possible to perform each drive of deceleration, direct connection, and speed increase at the set gear ratio, and it is possible to improve fuel efficiency by properly using various drive modes according to running conditions.

(8) According to the vehicle driving apparatus of the present invention, in the planetary gear, the first sun gear meshes with the ring gear via the first pinion, and the second sun gear meshes with the first pinion. The second pinion meshes with the ring gear, both pinions are supported by the carrier, one of the ring gear and the carrier is connected to the input shaft, and the other of the ring gear and the carrier is connected to the output shaft. When the input shaft is connected, the first sun gear is member A and the second sun gear is member B. When the ring gear is connected to the output shaft, the second sun gear is member A and the first sun gear is member B. Therefore, the member A is always connected to the third motor, and the second motor is selectively connected to the members A and B. By making it possible, in addition to stepless speed change with a simple configuration, it is possible to perform each drive of deceleration, direct connection, and speed increase with a fixed gear ratio, and various drive modes according to driving conditions Can be used to improve fuel efficiency.

[Brief description of the drawings]

FIG. 1 is a skeleton diagram of a vehicle drive device of the present invention.

FIG. 2 is a skeleton diagram of another embodiment of the vehicle drive device of the present invention.

FIG. 3 is a skeleton diagram of another embodiment of the vehicle drive device of the present invention.

FIG. 4 is a main part skeleton diagram of another embodiment of the vehicle drive device of the present invention.

FIG. 5 is a main part skeleton diagram of another embodiment of the vehicle drive device of the present invention.

FIG. 6 is a sectional view of a main part of a first conical clutch in the vehicle drive device of the present invention.

FIG. 7 is a sectional view taken along the line CC of FIG. 6;

FIG. 8 is a skeleton diagram showing a conventional example.

[Explanation of symbols]

 10: 1st planetary gear 12: 1st sun gear 14: 1st ring gear 16: 1st carrier 18: 1st pinion 20: 2nd planetary gear 22: 2nd sun gear 24: 2nd ring gear 26: 2nd carrier 28: 2nd 2 pinion 30: input shaft 32: output shaft 34: first motor 36: drive gear 38: idler gear 40: output gear 42: differential gear 44: axle 46: case 48: first conical clutch 50: second motor 52 : Third motor 54: Second conical clutch 56: First hub 58: First cone ring 60: First outer ring 62: First fork 70: Engine

Claims (8)

[Claims] 1. An automobile drive device having a plurality of motors, wherein a driving force input from an engine to an input shaft can be transmitted to an output shaft via a planetary gear, and the output shaft is connected to the plurality of motors. The planetary gear can be driven by the first motor, and the planetary gear is a member A of the rotating member which can be fixed to the case to obtain a deceleration drive.
And a member B that can be fixed to a case to obtain speed-up driving among the rotating members, wherein the members A and B can be connected to different motors from the first motor, respectively. A driving device for an automobile. 2. The vehicle according to claim 1, wherein one of the other motors (second motor) is selectively connectable to the members A and B. Drive device. 3. The one motor (second motor)
And the means for connecting the member A and the member B is a conical clutch that includes a cone ring that meshes with teeth having a helical surface and is capable of self-locking when a one-way torque is applied. An automobile drive device according to claim 2. 4. The one motor (second motor)
4. The vehicle drive device according to claim 2, wherein the first and second members can be connected simultaneously with both the member A and the member B. 5. The motor according to claim 5, wherein the member A is connectable to the another one motor (second motor), and further different from the one motor among the plurality of motors (third motor). 5. The vehicle drive device according to claim 2, wherein the drive device is always connected to the vehicle. 6. The planetary gear includes a first planetary gear having a first sun gear, a first ring gear, and a first gear supporting a first pinion meshing with the first sun gear, a second sun gear, and a second ring gear. A second planetary gear having a second carrier for supporting a second pinion; connecting the first sun gear and the second sun gear;
A ring gear is connected to the second carrier, the first carrier is connected to one of the input shaft and the output shaft, and the first ring gear and the second carrier are connected to the input shaft and the output shaft. When the first carrier is connected to the input shaft, the second ring gear is the member A, and the first sun gear and the second sun gear are the members B. 6. The device according to claim 1, wherein, when one carrier is connected to the output shaft, the first sun gear and the second sun gear are the members A, and the second ring gear is the member B. 7. Automotive drive system. 7. The planetary gear meshes with a first planetary gear having a first sun gear, a first ring gear, and a first carrier supporting a first pinion meshing with the first sun gear, a second sun gear, and a second ring gear. A second planetary gear having a second carrier for supporting a second pinion, connecting the first ring gear and the second carrier to the output shaft, and connecting the first carrier and the second ring gear to the input shaft; The vehicle drive device according to claim 1, wherein the second sun gear is the member A, and the first sun gear is the member B, while being connected to a shaft. 8. The planetary gear, wherein a first sun gear meshes with a ring gear via a first pinion, a second sun gear meshes with the ring gear via the first pinion and a second pinion, and the pinion is a carrier. When one of the ring gear and the carrier is connected to the input shaft, the other of the ring gear and the carrier is connected to the output shaft, and the ring gear and the input shaft are connected. When the first sun gear is the member A, the second sun gear is the member B, and when the ring gear is connected to the output shaft, the second sun gear is the member A and the first sun gear is 6. The vehicle drive device according to claim 1, wherein the member B is used.