JPH0781443A - Driving device for hybrid type vehicle - Google Patents

Abstract

PURPOSE:To improve power transmitting efficiency when the power generated by a motor is transmitted. CONSTITUTION:A driving device for a hybrid type vehicle is provided with the first shaft, a transmission 3 carrying out a speed change by the rotation from an engine, the second shaft, which is parallel to the first shaft, a transmitting means, which connects the first shaft and the second shaft together and transmits the rotation from the transmission 3 to the second shaft, a motor 4 arranged on the second shaft, and a clutch selectively transmitting the rotation from the engine to the second shaft. As the motor 4 is arranged on the second shaft, the power generate by the motor 4 is transmitted to an output gear 30 without passing through the transmitting means. Therefore, no power transmission loss is generated, so that power transmitting efficiency can be improved.

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 hybrid type vehicle.

[0002]

2. Description of the Related Art Conventionally, a hybrid type vehicle equipped with an internal combustion or external combustion engine and an electric motor (hereinafter referred to as "motor") generally drives the engine to operate a generator. And a series-type hybrid vehicle in which a motor is driven by the electric power of the engine, and power generated by the engine and the motor can be transmitted to drive wheels, and at least one of the engine and the motor is driven. It can be divided into parallel type hybrid vehicles.

In the case of the series type hybrid type vehicle, the engine and the motor are separately mounted on the front side and the rear side of the hybrid type vehicle respectively, and in the case of the parallel type hybrid type vehicle, the engine and the motor are arranged in the front side and the rear side of the hybrid type vehicle. It will be installed on either rear side.
The parallel hybrid vehicle has a structure in which a torque converter, a clutch, and a motor are arranged on the same shaft and they are housed in a drive device case (see Japanese Patent Laid-Open No. 50863/1993).

[0004]

However, in the above-mentioned conventional drive device for a hybrid vehicle, the engine and the motor are arranged on the first shaft, and the power generated by the engine and the motor is transmitted via the gear. Since the power is transmitted to the second shaft and the power of the second shaft is further transmitted to the differential device arranged on the third shaft,
When power is transmitted between the shafts, power transmission loss occurs between gears, resulting in reduced power transmission efficiency.

In the motor drive mode in which only the motor is used, the battery is consumed by the amount of power transmission loss, and the cruising range is shortened. Therefore, it is conceivable to make the power transmission system of the engine and the motor independent, but since the structure becomes large if the power transmission system is made independent, it is necessary to house the drive device of the hybrid vehicle in the conventional automatic transmission case. Will not be possible and the cost will be high.

The present invention solves the problems of the conventional drive device for a hybrid type vehicle, improves the power transmission efficiency when transmitting the power generated by the motor, and An object of the present invention is to provide a drive device for a hybrid vehicle that can be housed in an automatic transmission case.

[0007]

To this end, in a hybrid vehicle drive system according to the present invention, a first shaft and a gear shift which is arranged on the first shaft and receives a rotation from an engine to shift gears. A machine, a second shaft parallel to the first shaft, a transmission means for connecting the first shaft and the second shaft, and transmitting the rotation from the transmission to the second shaft, and on the second shaft. It has a motor arranged and a clutch for selectively transmitting the rotation from the engine to the second shaft.

In another hybrid vehicle drive device of the present invention, a fluid transmission device is disposed on the input side of the transmission.

[0009]

According to the present invention, as described above, in the hybrid vehicle drive device, the first shaft,
A transmission that is disposed on the first shaft and that receives a rotation from the engine to change gears; a second shaft that is parallel to the first shaft; and a transmission that connects the first shaft and the second shaft. Rotation from the second
It has a transmission means for transmitting to the shaft, a motor arranged on the second shaft, and a clutch for selectively transmitting the rotation from the engine to the second shaft.

In this case, since power can be generated by the engine and the motor, the motor is stopped and only the engine is driven when the battery is fully charged during high speed steady running on a highway. The hybrid type vehicle can be driven in the engine drive mode. When the battery is not fully charged during high-speed steady running on a highway, the clutch is engaged, the motor is used as a generator, the rotor is rotated by the power generated by the engine, and the stator is rotated. The electric current can be taken out from the coil to charge the battery.

The hybrid type vehicle can be driven in the engine / motor drive mode at the time of sudden acceleration, sudden start, running at a high load on a highway or the like. In this case, the clutch is engaged, and a combination of the power generated by the engine and the power generated by the motor is transmitted to the output gear. Furthermore, during low speed, low load running, the clutch can be released and only the motor can be driven to drive the hybrid vehicle in the motor drive mode.

Further, since the motor is arranged on the second shaft, the power generated by the motor is transmitted to the output gear without passing through the transmission means. Therefore, power transmission loss does not occur, and power transmission efficiency can be improved. Further, since the transmission is arranged on the first shaft, the transmission on the first shaft of the conventional automatic transmission can be used as it is, and the conventional automatic transmission case can be used for the hybrid vehicle. A drive device can be housed. Therefore, the parts can be shared with the conventional automatic transmission, and it is not necessary to significantly change the manufacturing process. As a result, the cost can be reduced.

In another hybrid vehicle drive device of the present invention, a fluid transmission device is disposed on the input side of the transmission. In this case, the conventional hydraulic transmission on the first shaft of the automatic transmission and the transmission can be used as they are.

[0014]

Embodiments of the present invention will now be described in detail with reference to the drawings. FIG. 1 is a schematic diagram of a drive system for a hybrid vehicle showing a first embodiment of the present invention, and FIG. 2 is a first sectional view of a drive system for a hybrid vehicle showing the first embodiment of the present invention. 3 is a second sectional view of a hybrid vehicle drive device showing a first embodiment of the present invention, and FIG. 4 is a third sectional view of a hybrid vehicle drive device showing the first embodiment of the present invention. Is.

In the figure, 1 is a torque converter as a fluid transmission device arranged on a first shaft, and 3 is a structure arranged on the first shaft. A transmission for performing a single speed change, 4 is a motor that is arranged on a second shaft that is parallel to the first shaft to generate power, and 13 is a third shaft that is parallel to the first and second shafts. It is a differential device which is arranged in the above and differentially rotates. In this case, the engine, the torque converter 1, the transmission 3, the motor 4 and the differential device 1
A drive unit for a hybrid vehicle is constituted by 3.

Further, 6 is an output shaft of the engine which is arranged along the first shaft, and transmits the power generated by the engine to the torque converter 1. The torque converter 1 includes a pump impeller 7 connected to the output shaft 6, a turbine runner 8 connected to the output shaft 2 of the torque converter 1, a one-way clutch F _T , and a drive unit case 9 via the one-way clutch F _T. It has a stator 10 connected to the lockup clutch 11 and a lockup clutch 11 that is engaged or disengaged by switching the flow direction of oil in the torque converter 1.

Further, the transmission 3 has the output shaft 2 as an input shaft and an output shaft 15 disposed behind the output shaft 2 (to the left in the drawing) on the same shaft. The transmission 3 has a first planetary gear unit 16 and a second planetary gear unit 17, and the first and second planetary gear units 16 and 17 are selectively engaged with each other in order to mesh them with each other.
2nd clutch C1, C2, 1st, 2nd, 3rd brake B
1, B2, B3, and first and second one-way clutch F
1 and F2.

The first planetary gear unit 16
Is a ring gear R ₁ connected to a cylinder 19 fixed to the output shaft 2 via a first clutch C1, and an output shaft 1
5, the sun gear S ₁ formed on the front (right side in the figure) end of the sun gear shaft 20 which is rotatably supported, and the front end of the output shaft 15. The connected carrier CR ₁ and the ring gear R
Together brought into meshing between ₁ and the sun gear S _1, consisting of a pinion P ₁ that is rotatably supported by the carrier CR _1.

The sun gear shaft 20 accommodates the first planetary gear unit 16 and the drum 22.
The front end of the drum 22 is connected to the cylinder 19 via the second clutch C2, and the outer periphery is connected to the drive unit case 9 via the first brake B1. An intermediate portion of the sun gear shaft 20 is connected to the drive unit case 9 via a first one-way clutch F1 and a second brake B2 directly connected to the first one-way clutch F1.

On the other hand, the second planetary gear unit
17 is connected to the rear end of the output shaft 15 of the transmission 3.
Ring gear R₂, The rear end of the sun gear shaft 20
Sun gear S formed on the₂, Second one-way clutch
F2 and a third clutch in parallel with the second one-way clutch F2
The casing connected to the drive unit case 9 via the rake B3.
Rear CR₂And the ring gear R₂And Sun Gear S₂
Between the carrier C and the carrier C
R₂Pinion P rotatably supported by ₂Consisting of
It

A counter drive gear 24 is provided behind the transmission 3 and fixed to the output shaft 15. The counter drive gear 24 is meshed with a counter driven gear 26 fixed to the rear end of the counter shaft which is integral with the output shaft 5 of the motor 4 and constitutes a transmission means. The motor 4 includes a stator 28 and a rotor 29, the stator 28 is fixed to the drive unit case 9, and the rotor 29 is fixed to the output shaft 5. And
An output gear 30 is fixed to the output shaft 5, and the output gear 30
And the ring gear 31 of the differential device 13 mesh with each other.

The differential device 13 has a pinion 33 and left and right side gears 35 and 36, and the side gears 35 and 36 are connected to drive shafts 38 and 39. Therefore, the rotation transmitted to the ring gear 31 is differentiated in the differential device 13 and transmitted to the drive shafts 38 and 39 via the left and right side gears 35 and 36.

Next, the operation of the drive system for the hybrid type vehicle having the above structure will be described. In this case, since the drive device of the hybrid vehicle can generate power by the engine and the motor 4, when the battery (not shown) is in a fully charged state during high speed steady running on a highway or the like, the motor 4 can be driven. The hybrid type vehicle can be driven in the engine drive mode by stopping the engine and driving only the engine. When the battery is not fully charged during high-speed steady running on a highway or the like, the first clutch C1 is engaged, the motor 4 is used as a generator, and the rotor 29 is driven by the power generated by the engine. Can be rotated to extract current from the coil of the stator 28 and charge the battery.

The hybrid type vehicle can be driven in the engine / motor drive mode at the time of sudden acceleration, sudden start, running at high load on a highway, etc. In this case, the first clutch C1 is engaged, and a combination of the power generated by the engine and the power generated by the motor 4 is transmitted to the output shaft 5.

Furthermore, during low speed, low load running,
The first clutch C1 is released and only the motor 4 is driven.
Drive a hybrid vehicle in motor drive mode
be able to. Engine drive mode and engine mode
1st clutch in drive mode
C1 is engaged. Then, the first clutch C1 is engaged.
Is transmitted to the output shaft 2 of the torque converter 1.
The forward rotation of the engine is the first planetary gear unit.
Ring gear R of G16₁To the carrier CR
₁And the carrier CR₁Is transmitted to the output shaft 15 which is integrated with
And Sun Gear S ₁And the second planetary gear unit
Sun Gear S of Knit 17₂Via carrier CR ₂Reverse
Try to rotate in the direction. However, the second one way
The clutch F2 is locked and the carrier CR₂
The rotation of the pinion P₂Is rotating and output shaft
Ring gear R integrated with 15₂Transmits the decelerated rotation to
It

The engine drive mode and the engine
At the second speed in the motor drive mode, the first clutch C1 and the second brake B2 are engaged. And
Since the first clutch C1 is engaged, the forward rotation of the engine transmitted to the output shaft 2 is transmitted to the ring gear R ₁ of the first planetary gear unit 16 to rotate the sun gear S ₁ in the reverse direction. And

However, when the second brake B2 is engaged,
The first one-way clutch F1 is locked and
Sun Gear S₁Prevent the rotation of. Therefore, Pinio
P ₁Carrier CR while spinning₁Rotates, the first
The speed was reduced only via the planetary gear unit 16.
The rotation is transmitted to the output shaft 15. Next, the engine drive
Mode and engine / motor drive mode at 3rd speed
At this time, the first clutch C1 and the second clutch C2 are engaged.
Are combined. Then, the first clutch C1 and the second clutch
Since C2 is engaged, the first planetary gear unit
16 is directly connected. Therefore, the rotation of the output shaft 2
It is transmitted to the output shaft 15 as it is.

In this way, the rotation transmitted to the output shaft 15 is transmitted to the output shaft 5 via the counter drive gear 24 and the counter driven gear 26, and the output gear 3
It is transmitted from 0 to the differential device 13. In the hybrid vehicle drive device having the above-described configuration, since the motor 4 is arranged on the second shaft, the power generated by the motor 4 does not pass through the counter drive gear 24 and the counter driven gear 26 and is output to the output gear. Thirty
Can be transmitted to. Therefore, power transmission loss does not occur, and power transmission efficiency can be improved.

Further, since it is not necessary to dispose the motor 4 on the first shaft, it is possible to mount the transmission 3 having three forward gears and one reverse gear or four forward gears and one reverse gear. Therefore, the hybrid vehicle can be driven mainly in the engine drive mode. Further, if the size of the motor 4 is increased so that the hybrid vehicle can be driven in the motor drive mode at medium and low speeds, the battery capacity can be reduced and the maintenance and management of the battery can be facilitated. it can.
Therefore, it is possible to reduce the weight of the drive device of the hybrid vehicle, improve fuel efficiency, and improve acceleration.

By the way, in the drive system for the hybrid type vehicle having the above-mentioned structure, the automatic transmission case of the conventional automatic transmission can be used as it is, and
The on-axis torque converter and transmission can be used as they are. FIG. 5 is a schematic diagram of an automatic transmission corresponding to the first embodiment of the present invention. In the figure, 1 is a torque converter, 3 is a transmission, and 13 is a differential device. The torque converter 1 and the transmission 3 are arranged on the first shaft. Further, reference numeral 40 is an under-drive auxiliary transmission arranged on a second shaft parallel to the first shaft. In this case, the transmission 3 and the auxiliary transmission 40 form an automatic transmission having four forward gears and one reverse gear. The torque converter 1 and the transmission 3 are housed in the automatic transmission case 9a.

In this case, the rotation of the output shaft 15 is transmitted to the counter shaft 25 via the counter drive gear 24 and the counter driven gear 26, and the counter shaft 25 serves as the input shaft of the auxiliary transmission 40. The sub transmission 4
Reference numeral 0 has a third planetary gear unit 43, and also has a third clutch C3, a fourth brake B4, and a third one-way clutch F3 for selectively meshing each element of the planetary gear unit 43.

The third planetary gear unit 43
Is a ring gear R ₃ connected to the front end of the counter shaft 25, a sun gear S ₃ formed at the front (right side in the figure) end of the sun gear shaft 45 rotatably fitted on the counter shaft 25, The carrier CR ₃ connected to the drum 46 fixed to the sun gear shaft 45 so as to accommodate the third planetary gear unit 43, is meshed between the ring gear R ₃ and the sun gear S ₃ , and is caused by the carrier CR ₃ . It consists of a rotatably supported pinion P ₃ .

Therefore, instead of the auxiliary transmission 40 of the conventional automatic transmission, the motor 4 (FIG. 1) is replaced by the counter shaft 25.
1 to fix the automatic transmission shown in FIG.
It is possible to change to the drive device of the hybrid vehicle shown in FIG. In this case, the torque converter 1, the transmission 3, the motor 4, the output gear 30, and the differential device 13
Is integrally housed in the drive unit case 9, the automatic transmission case 9a of the conventional automatic transmission can be used as it is, and the torque converter 1 on the first shaft can be used.
Also, the transmission 3 can be used as it is.

Therefore, the parts can be made common to the conventional automatic transmission, and it is not necessary to greatly change the manufacturing process. Therefore, the cost can be reduced. Next, a second embodiment of the present invention will be described. FIG. 6 is a schematic diagram of a drive device for a hybrid vehicle showing a second embodiment of the present invention.

In the figure, 1 is a torque converter arranged on a first shaft, 103 is a structure arranged on the first shaft, and receives a rotation from an engine (not shown) to perform four forward gears and one reverse gear shift. The transmission to be performed is a second parallel 104 to the first axis.
A motor arranged on the shaft to generate power, 145 is a speed reducer arranged on the second shaft, and 13 is arranged on the third shaft parallel to the first and second shafts and rotated. It is a differential device that makes the differential.

The transmission 103 has the output shaft 2 of the torque converter 1 as an input shaft. Further, the transmission 103 has a first planetary gear unit 116 and a second planetary gear unit 117, and in order to selectively mesh each element of both planetary gear units 116 and 117, 3rd and 4th
Clutch C1, C2, C3, C0, first and second brakes B1, B2, and first and second one-way clutch F1,
Have F0.

The first planetary gear unit 116
Is a first clutch C1 and a fourth clutch C1 arranged in series with each other.
A ring gear R ₁ connected to the output shaft 2 via a clutch C 0 and connected to the drive device case 9 via a second brake B 2 and a first one-way clutch F 1 arranged in parallel with each other, and an external ring gear R _{1 to} the output shaft 2. The sun gear S ₁ formed on the sun gear shaft 120 which is fitted and rotatably supported, the carrier CR ₁ connected to the counter drive gear 124, and the ring gear R ₁ and the sun gear S ₁ are meshed with each other. , The carrier CR
_The pinions P _1A and P _1B are rotatably supported by ₁ .

A drum 122 is fixed to the sun gear shaft 120, the drum 122 is connected to the output shaft 2 via the second clutch C2, and the outer periphery is connected to the drive unit case 9 via the first brake B1. Connected with. On the other hand, the second planetary gear unit 117 has a first clutch C1 via a third clutch C3 and a second one-way clutch F0 arranged in parallel with each other, and an output shaft 2 via the first clutch C1. A ring gear R ₂ connected to the sun gear S ₂ , a sun gear S ₂ formed on the sun gear shaft 120, and a carrier C connected to the carrier CR _1.
R _2, and together brought into meshing between the ring gear R ₂ and the sun gear S _2, consisting of a pinion P ₂ which is rotatably supported by the carrier CR _2.

Then, the counter drive gear 124
Is engaged with a counter driven gear 126 fixed to a counter shaft which is integral with the output shaft 105 of the motor 104, and constitutes a transmission means. The motor 104 includes a stator 128 and a rotor 129.
28 is fixed to the drive unit case 9, and the rotor 129 is fixed to the output shaft 105. Then, the output shaft 105
The output gear 30 is fixed to the output gear 30, and the output gear 30 meshes with the ring gear 31 of the differential device 13.

Next, the operation of the drive device for the hybrid type vehicle having the above-mentioned structure will be described. At the first speed in the engine drive mode and the engine / motor drive mode, the first clutch C1 is engaged and the first and second one-way clutches F1 and F0 are locked. Then, the rotation of the input shaft 2 is transmitted to the ring gear R ₂ via the first clutch C1 and the second one-way clutch F0, and in this state, the ring gear R ₂ is transmitted by the first one-way clutch F1.
_Since the rotation of ₁ is blocked, the rotation of the carrier CR ₂ is significantly reduced while idling the sun gear S ₂ , and this rotation is transmitted to the counter drive gear 124.

The engine drive mode and the engine
At the second speed in the motor drive mode, the first clutch C1 and the first brake B1 are engaged, and the second one-way clutch F0 is locked. Then, the rotation of the input shaft 2 is transmitted to the ring gear R ₂ via the first clutch C1 and the second one-way clutch F0, and
The rotation of the sun gear S ₂ is caused to stop by a brake B1, rotation of the ring gear R ₂ is transmitted is then decelerated to the carrier CR _2, the counter drive gear while rotation of the carrier CR ₂ is idle ring gear R ₁ It is transmitted to 124.

Next, the engine drive mode and the engine
At the third speed in the motor drive mode, the first clutch C1, the third clutch C3, and the fourth clutch C0 are engaged, the second one-way clutch F0 is locked, and the first brake B1 is released. And the input shaft 2
Is transmitted to the ring gear R ₂ via the second one-way clutch F0 and the third clutch C3, and
It is transmitted to the ring gear R ₁ via the fourth clutch C0,
The first and second planetary gear units 116 and 117 are directly connected. Therefore, the rotation of the output shaft 2 is directly transmitted to the counter drive gear 124.

Further, at the 4th speed in the engine drive mode and the engine / motor drive mode, the first clutch C1, the fourth clutch C0 and the first brake B1 are engaged and the third clutch C3 is released. Then, the rotation of the input shaft 2 is rotated by the ring gear R via the fourth clutch C0.
₁ and the rotation of the sun gear S ₁ is stopped by the first brake B1.
The rotation of ₁ causes the carrier C to rotate while rotating the ring gear R _2.
R ₁ is rotated at high speed, and this rotation is transmitted to the counter drive gear 124.

By the way, in this embodiment, the conventional automatic transmission case of the automatic transmission can be used as it is, and the torque converter and the transmission on the first shaft can be used as they are. FIG. 7 is a schematic diagram of an automatic transmission corresponding to the second embodiment of the present invention. In the figure, 1 is a torque converter, 103 is a transmission, and 13
Is a differential device. The torque converter 1 and the transmission 103 are arranged on the first shaft. The torque converter 1 and the transmission 103 are housed in an automatic transmission case 9a.

In this case, the rotations of the carriers CR ₁ and CR ₂ are transmitted to the counter shaft 125 via the counter drive gear 124 and the counter driven gear 126. Therefore, by fixing the motor 104 (FIG. 6) to the counter shaft 125 of the conventional automatic transmission, the automatic transmission shown in FIG. 7 can be changed to the drive device for the hybrid vehicle shown in FIG. In this case, since the torque converter 1, the transmission 103, the motor 104, the output gear 30, and the differential device 13 are integrally housed in the drive device case 9, the automatic transmission case 9a of the conventional automatic transmission is used as it is. The torque converter 1 and the transmission 1 on the first shaft
03 can be used as it is.

Next, a third embodiment of the present invention will be described. FIG. 8 is a schematic diagram of a drive device for a hybrid vehicle showing a third embodiment of the present invention. In the figure, reference numeral 1 denotes a torque converter arranged on a first shaft, 203 denotes a torque converter arranged on the first shaft, and receives a rotation from an engine (not shown) and performs a shift of three forward gears and one reverse gear. , 204 is a motor for generating power by being arranged on a second shaft parallel to the first shaft, 245 is a speed reducer arranged on the second shaft, 1
Reference numeral 3 is a differential device which is arranged on a third axis parallel to the first axis and the second axis and differentially rotates.

The transmission 203 has the output shaft 2 of the torque converter 1 as an input shaft. Further, the transmission 203 has a first planetary gear unit 216 and a second planetary gear unit 217, and has first and second clutches C for selectively engaging the respective elements of both planetary gear units 216, 217.
1, C2, first, second and third brakes B1, B2, B
3 and the first and second one-way clutches F1 and F2.

The first planetary gear unit 216
Is a third brake B3 and a second brake B3 arranged in parallel with each other.
A ring gear R ₁ connected to the drive unit case 9 via a one-way clutch F2, a sun gear S ₁ formed on a sun gear shaft 220 that is externally fitted to the output shaft 2 and rotatably supported, and a counter drive gear 224. linked carrier CR _1, and with brought into meshing between the ring gear R ₁ and the sun gear S _1, a pinion P, which is rotatably supported by the carrier CR _1
It consists of _1A and P _1B .

The sun gear shaft 220 has the second
It is connected to the output shaft 2 via a clutch C2. The sun gear shaft 220 is connected to the drive unit case 9 via the first brake B1, and is also connected to the drive unit case 9 via the first one-way clutch F1 and the second brake B2 arranged in series. . Meanwhile, the second planetary gear unit 217, the ring gear R ₂ connected to the output shaft 2 through the first clutch C1, the sun gear S ₂ to the sun gear shaft 220 formed integrally with the sun gear S _1, the carrier CR Carrier CR linked to _1
2 and a pinion P ₂ which is meshed between the ring gear R ₂ and the sun gear S ₂ , is rotatably supported by the carrier CR ₂ , and is integrally formed with the pinion P ₁ .

Then, the counter drive gear 224
Is engaged with a counter driven gear 226 fixed to a counter shaft which is integral with the output shaft 205 of the motor 204, and constitutes a transmission means. The motor 204 includes a stator 228 and a rotor 229.
28 is fixed to the drive unit case 9, and the rotor 229 is fixed to the output shaft 205. Then, the output shaft 205
The output gear 30 is fixed to the output gear 30, and the output gear 30 meshes with the ring gear 31 of the differential device 13.

Next, the operation of the drive device for the hybrid type vehicle having the above-mentioned structure will be described. At the first speed in the engine drive mode and the engine / motor drive mode, the first clutch C1 is engaged and the second one-way clutch F2 is locked. Then, the rotation of the input shaft 2 is transmitted to the ring gear R ₂ via the first clutch C1, and in this state, the rotation of the ring gear R ₁ is blocked by the second one-way clutch F2.
The rotation of the carrier CR ₂ is significantly reduced while idling ₂ and this rotation is transmitted to the counter drive gear 224.

In addition, the engine drive mode and the engine
At the second speed in the motor drive mode, the first clutch C1 and the second brake B2 are engaged, and the first one-way clutch F1 is locked. And the input shaft 2
Is transmitted to the ring gear R ₂ via the first clutch C1 and the rotation of the sun gear S ₂ is stopped by the second brake B2 and the first one-way clutch F1. Therefore, the rotation of the ring gear R ₂ is reduced. let is be transmitted to the carrier CR _2, the carrier rotation CR ₂ is counter drive gear 2 while idling the ring gear R ₁
24 is transmitted.

Next, the engine drive mode and the engine
At the third speed in the motor drive mode, the first clutch C1, the second clutch C2, and the second brake B are engaged. Then, the rotation of the input shaft 2 depends on the first clutch C1.
Is transmitted to the ring gear R ₂ via the second clutch C2 and is transmitted to the sun gear S ₂ via the second clutch C2, so that the first and second planetary gear units 216 and 217 are directly connected. Therefore, the rotation of the output shaft 2 is transmitted to the counter drive gear 224 as it is.

By the way, in this embodiment, the automatic transmission case of the conventional automatic transmission can be used as it is, and the torque converter and the transmission on the first shaft can be used as they are. FIG. 9 is a schematic diagram of an automatic transmission corresponding to the third embodiment of the present invention. In the figure, 1 is a torque converter, 203 is a transmission, and 24
Reference numeral 0 is an auxiliary transmission, and 13 is a differential device.
The torque converter 1 and the transmission 203 are arranged on the first shaft. The torque converter 1, the transmission 203, and the auxiliary transmission 240 are housed in the automatic transmission case 9a.

In this case, the rotations of the carriers CR ₁ and CR ₂ are transmitted to the counter shaft 225 via the counter drive gear 224 and the counter driven gear 226. Therefore, instead of the auxiliary transmission 240 of the conventional automatic transmission, the motor 204 (FIG. 8) is attached to the counter shaft 225.
By fixing the automatic transmission shown in FIG.
It is possible to change to the drive device of the hybrid vehicle shown in FIG. In this case, the torque converter 1 and the transmission 20
Since the motor 3, the motor 204, the output gear 30, and the differential device 13 are integrally housed in the drive device case 9, the automatic transmission case 9a of the conventional automatic transmission can be used as it is, and the first shaft The torque converter 1 and the transmission 203 can be used as they are.

[Brief description of drawings]

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

FIG. 2 is a first cross-sectional view of a drive device for a hybrid vehicle showing a first embodiment of the present invention.

FIG. 3 is a second cross-sectional view of the drive device for the hybrid vehicle showing the first embodiment of the present invention.

FIG. 4 is a third cross-sectional view of the drive device for the hybrid vehicle showing the first embodiment of the present invention.

FIG. 5 is a schematic view of an automatic transmission corresponding to the first embodiment of the present invention.

FIG. 6 is a schematic diagram of a drive device for a hybrid vehicle showing a second embodiment of the present invention.

FIG. 7 is a schematic diagram of an automatic transmission according to a second embodiment of the present invention.

FIG. 8 is a schematic view of a drive device for a hybrid vehicle showing a third embodiment of the present invention.

FIG. 9 is a schematic diagram of an automatic transmission corresponding to a third embodiment of the present invention.

[Explanation of symbols]

 1 Torque converter 3, 103, 203 Transmission 4, 104, 204 Motor 9 Drive device case 24, 124, 224 Counter drive gear 26, 126, 226 Counter driven gear 30 Output gear C1 1st clutch

Claims (2)

[Claims] 1. (a) a first shaft; (b) a transmission that is arranged on the first shaft and that receives a rotation from an engine to change gears; and (c) is parallel to the first shaft. A second shaft; (d) a transmission unit that connects the first and second shafts and transmits the rotation from the transmission to the second shaft; and (e) is arranged on the second shaft. A drive device for a hybrid vehicle, comprising: a motor; and (f) a clutch that selectively transmits the rotation from the engine to the second shaft. 2. The drive device for a hybrid vehicle according to claim 1, wherein a fluid transmission device is arranged on an input side of the transmission.