JP2003034152A - Power transmission unit - Google Patents

Abstract

(57) [Abstract] [Problem] To be able to perform starting, creep running, and hill hold with excellent torque transmission efficiency, low speed and high torque output, and to provide functions of a starter motor and a generator. To provide a novel power transmission unit that is compact and has excellent on-board performance. SOLUTION: An output shaft 2 for outputting torque to an input shaft 1 and a transmission TM to which a torque is transmitted from an engine EG, and a first electromagnetic clutch AC / C capable of connecting and disconnecting the input shaft 1 and the output shaft 2. L, a first planetary gear PGS1 capable of transmitting the reduced rotation of the input shaft 1 to the generator motor MG operable as a generator and a motor, and a reduced transmission of the rotation of the input shaft 1 to the output shaft 2 A second planetary gear PGS2, a second electromagnetic clutch BC / L for connecting and disconnecting the second planetary gear PGS2 and the output shaft 2, and a brake BRK for fixing and releasing the ring gear 13 of the first planetary gear PGS1. And provided.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a power transmission unit for transmitting power between a prime mover and a transmission of a vehicle, and for starting and generating electricity.

[0002]

2. Description of the Related Art Conventionally, generally, in an automobile equipped with an automatic transmission, a torque converter is used as a means for transmitting power between an engine as a prime mover and the automatic transmission. Such a technique is disclosed in, for example, Automotive Engineering Complete Book No. 9
Volume 1 (Published by Sankaido on November 20, 1980)
It is described on page 49. Further, as another power transmission means, a clutch is known, and an automatic clutch system for automatically connecting and disconnecting the clutch as required is proposed from the requirement of simplicity of operation. Those using a dry type single plate clutch are known.

[0003]

However, since the torque converter transmits power through a fluid, power loss due to slippage occurs and fuel consumption is poor. On the other hand, the means using the clutch does not easily cause power loss, but it is difficult to transmit the low speed / high torque which is an advantage of the torque converter. That is, in order to perform low-speed / high-torque transmission, the friction surface is slid to perform torque transmission, but in this case, heat is generated. For this reason, it is difficult to perform so-called creep running that gradually advances due to idling rotation of the engine, or so-called hill hold that stops on an uphill. Therefore, in order to achieve the hill hold, it has been proposed to automatically generate a braking force in the braking device. However, in this case, it is necessary to mount a device capable of actively generating a braking force, which causes an increase in vehicle cost.

Further, the conventional starting device for the prime mover and the conventional power generating device for the vehicle are provided separately from the above-mentioned power transmission device, and each requires a space for installation.
There was a demand for improved vehicle mountability.

The present invention has been made by paying attention to the above-mentioned conventional problems, and it is excellent in torque transmission efficiency and low speed / low speed.
A new power transmission unit capable of high torque output, capable of starting / creeping and hill-holding, and having a starter motor and a generator while being compactly formed and excellent in vehicle mountability. Is mainly provided, and further, it is aimed at downsizing and cost reduction.

[0006]

In order to achieve the above-mentioned object, a power transmission unit of the present invention comprises an input member for transmitting torque from a prime mover and an output member for outputting torque to a transmission, and the input member. A direct connection switching clutch that can connect and disconnect the output member, a first planetary gear that can transmit the rotation of the input member by reducing the rotation of the input member, and a rotation of the input member to a generator and a motor that can operate as a motor. A second planetary gear that can be decelerated and transmitted to the output member, and a second planetary gear switching unit that switches between a state in which the second planetary gear performs a speed change operation with respect to either the input member or the output member and a state in which the speed change operation is not performed. And are provided.

According to a second aspect of the present invention, in the power transmission unit according to the first aspect, the first planetary gear has a state in which the first planetary gear shifts with respect to the input member, and a state in which the shift operation is not performed. The first planetary gear switching means for switching to is provided.

According to a third aspect of the present invention, in the power transmission unit according to the first or second aspect, the second planetary gear switching means transmits torque between the second planetary gear and the input member or the output member. The means is a transmission switching clutch that can connect and disconnect the path.

According to a fourth aspect of the present invention, in the power transmission unit according to the first or second aspect, the second planetary gear switching means fixes or releases the fixing element of the second planetary gear. The means is characterized by being a brake.

According to a fifth aspect of the present invention, in the power transmission unit according to any one of the first to fourth aspects, the first
The planetary gear switching means is a brake for fixing and releasing the fixing element of the first planetary gear.

The invention according to claim 6 is the power transmission unit according to any one of claims 1 to 4, wherein
The planetary gear switching means is a transmission switching clutch capable of connecting and disconnecting the torque transmission path between the input member and the first planetary gear.

Further, the invention according to claim 7 is the power transmission unit according to any one of claims 1 to 6, wherein:
In the first planetary gear, the carrier is connected to the input member,
A generator motor is connected to the sun gear, and the ring gear is a fixed element. The invention according to claim 8 is the power transmission unit according to claim 7, characterized in that the ring gear of the first planetary gear can be fixed and released by a brake as a first planetary gear switching means. The means to do so. The invention described in claim 9 is the power transmission unit according to claim 7,
The carrier and the input member of the first planetary gear can be connected and disconnected by the transmission switching clutch as the first planetary gear switching device.

The invention described in claim 10 is the power transmission unit according to any one of claims 1 to 9,
In the second planetary gear, the sun gear is connected to the input member,
The means is characterized in that the carrier is connected to the output member and the ring gear is a fixed element. According to an eleventh aspect of the invention, in the power transmission unit according to the tenth aspect, the ring gear of the second planetary gear can be fixed and released by a brake as a second planetary gear switching unit. The means to do so. According to a twelfth aspect of the present invention, in the power transmission unit according to the tenth aspect, any one of the carrier and the output member of the second planetary gear or the sun gear and the input member serves as the second planetary gear switching unit. The device is configured to be connectable and disconnectable by means of g.

According to a thirteenth aspect of the present invention, in the power transmission unit according to any one of the first to ninth aspects,
In the second planetary gear, the ring gear is connected to the input member, the carrier is connected to the output member, and the sun gear is a fixed element. According to a fourteenth aspect of the present invention, in the power transmission unit according to the thirteenth aspect, the sun gear of the second planetary gear is configured to be fixed and released by a brake. According to a fifteenth aspect of the present invention, in the power transmission unit according to the thirteenth aspect, any one of the carrier and the output member of the second planetary gear or the ring gear and the input member serves as the second planetary gear switching unit. The means is characterized in that it can be connected and disconnected.

[0015]

According to the present invention, when the prime mover is started, the generator motor is driven as an electric motor. The rotation of the generator motor is decelerated in the first planetary gear and transmitted to the input member, which is then transmitted to the prime mover to start the prime mover. Since the first planetary gears are decelerated in this way, the required output of the generator motor can be suppressed, and the generator motor can be downsized, and thus the device can be downsized. Further, when the input member is rotating due to driving of the prime mover or coasting, the rotation of the input member is transmitted to the generator motor, and power can be generated as necessary.

When the prime mover is driven, the direct coupling switching clutch is released, and the second planetary gear switching means causes the second planetary gear to shift to the input member or the output member. Accordingly, when the rotation transmitted from the prime mover to the input member is transmitted from the input member to the output shaft via the second planetary gear, the second planetary gear is decelerated. In this way, the torque transmission of the prime mover is the second
Since it is performed by a planetary gear, it is more efficient than transmitting torque by a torque converter, and the torque can be increased without heat generation. Effective during hill hold.

Further, while the prime mover is being driven, the direct coupling switching clutch is engaged, and the second planetary gear switching means switches the second planetary gear to a state in which gear shifting is not performed. Thus, the rotation input from the prime mover to the input member is efficiently transmitted from the direct coupling switching clutch to the output member at a ratio of 1: 1. In this case, it is possible to travel by performing a normal gear shift with the transmission.

As described above, the power transmission unit of the present invention is installed between the prime mover and the transmission to transmit torque between the prime mover and the transmission, and also functions as a starter and a generator of the prime mover. Since it has both, it is excellent in vehicle mountability. Furthermore, during power transmission, efficient torque transmission without energy loss can be performed, and further, torque can be increased without heat generation as needed. In addition, when operating as a starter, the rotation of the generator motor is decelerated and transmitted to the prime mover, while when operating as a generator, the generator motor is rotated at an increased speed, which helps reduce the size of the generator motor. Therefore, it is possible to achieve the effect that the entire unit can be made compact.

According to the second aspect of the invention, the first planetary gear switching means can switch to a state in which the first planetary gear does not perform the speed change operation with respect to the input member. Therefore, during normal running or acceleration running when the input member rotates at high speed,
By switching the first planetary gears to the state in which the speed change operation is not performed, the generator motor can be prevented from rotating at high rotation speed, and the required capacity of the generator motor can be suppressed by that amount, and the size can be reduced.

According to the third aspect of the invention, when the transmission switching clutch as the second planetary gear switching means is engaged, the second planetary gear is connected to the input member and the output member so that the gear shift operation is possible. Become. On the other hand, when the transmission switching clutch is released, the second planetary gear is in a state in which gear shifting cannot be performed because the connection between either the input member or the output member is cut off. In the invention according to claim 4, when the fixing element of the second planetary gear is fixed by the brake as the second planetary gear switching means, the second planetary gear is changed in speed when the rotation is input from the input element. To transmit rotation to the output element. On the other hand, when the fixing of the fixing element is released by the brake, the fixing element is rotated together and the gear shift operation is disabled.

In the invention described in claim 5, when the fixing element of the first planetary gear is fixed by the brake as the first planetary gear switching means, the first planetary gear is rotated from the input element of the first planetary gear. When input, the gear shift operation is performed to transmit the rotation to the output element. On the other hand, when the fixing of the fixing element is released by the brake, the fixing element is rotated together and the gear shift operation is disabled. In the invention according to claim 6, when the transmission switching clutch as the first planetary gear switching means is engaged, the first planetary gear is connected to the input member and the output member and is in a state capable of gear shifting operation. On the other hand, when the transmission switching clutch is released, the first planetary gear is disconnected from either the input member or the output member, so that the gear shift operation is disabled.

According to the seventh aspect of the invention, when the generator motor is operated as a starter motor, the rotation of the generator motor is input to the sun gear in the first planetary gear, decelerated from the carrier and output to the input member. It Therefore, the input member is rotated at a speed slower than the rotation of the generator motor. On the other hand, when the prime mover is driven and the input member is rotating, the rotation of the input member is input from the carrier in the first planetary gear, speeded up from the sun gear, and output to the generator motor. Therefore, the generator motor is rotated at a speed higher than the rotation of the input member. Also,
According to the invention described in claim 7, when the ring gear is fixed by the brake of the invention described in claim 8, the first planetary gear performs the deceleration and speed-up operations as described above. When the fixing of the ring gear is released by, the above deceleration and speed-up operations are not performed. Also,
In the invention according to claim 7, when the transmission switching clutch according to claim 9 is connected, torque can be transmitted between the carrier of the first planetary gear and the input member, and the gear shift is performed in the first planetary gear. However, when the transmission switching clutch disconnects the carrier and the input member of the first planetary gear, torque is not transmitted between the carrier and the input member, and the first planetary gear becomes inoperable. Become.

According to the tenth aspect of the present invention, when the prime mover is driven and the input member is rotating, the rotation of the input member is input from the sun gear in the second planetary gear, decelerated from the carrier, and directed to the output member. Is output. Therefore, the torque of the prime mover is increased and transmitted from the output member to the transmission. Further, in the invention described in claim 10, when the ring gear is fixed by the brake of the invention described in claim 11, the second planetary gear performs the deceleration operation as described above, but by the brake. When the fixing of the ring gear is released, the above deceleration operation is not performed. According to the invention of claim 10, claim 1
When the transmission switching clutch described in 2 is connected, torque can be transmitted between the sun gear of the second planetary gear and the input member or the carrier and the output member, and the gear shifting operation can be performed in the second planetary gear. When the sun gear is disconnected from the input member or the carrier is disconnected from the output member, the second planetary gear does not transmit torque to the input member or the output member, and the second planetary gear becomes inoperable.

In the thirteenth aspect of the present invention, when the prime mover is driven and the input member is rotating, the rotation of the input member is input from the ring gear in the second planetary gear, decelerated from the carrier, and directed to the output member. Is output. Therefore, the torque of the prime mover is increased and transmitted from the output member to the transmission. Further, in the invention of claim 13, when the sun gear is fixed by the brake of the invention of claim 14, the second planetary gear performs the deceleration operation as described above, but by the brake. When the fixing of the sun gear is released, the above deceleration operation is not performed. According to the invention of claim 13, claim 1
When the transmission switching clutch described in 5 is connected, torque can be transmitted between the ring gear of the second planetary gear and the input member or the sun gear and the output member, and the gear shifting operation can be performed in the second planetary gear. When the ring gear is disconnected from the input member or the sun gear is disconnected from the output member, the second planetary gear does not transmit torque to the input member or the output member, and the second planetary gear becomes inoperable.

[0025]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings. (Embodiment 1) First, the configuration will be described. The power transmission unit MGU of the first embodiment corresponding to the inventions described in claims 1 to 3, 5, 7, 7, 8, 10 and 12 of the present application is shown in FIG.
As shown in, engine EG and transmission TM
, That is, at a position where the torque converter is arranged in a general automatic transmission.
As the transmission, a so-called automatic transmission, a manual transmission, a continuously variable transmission such as a CVT, or the like is used.

First, the outline of the structure of the power transmission unit MGU will be described with reference to FIG.
In U, the input shaft 1 as an input member in the claims to which the driving force is input from the engine EG and the output shaft 2 as an output member in the claims to output the driving force to the transmission TM are coaxial. Provided outside the input shaft 1 and the output shaft 2, coaxially with the shafts 1 and 2, two planetary gears, a first planetary gear PGS1 and a second planetary gear PGS2, and a direct connection switching in the claims. The first electromagnetic clutch A-C / L as the clutch and the second claim of the claims.
Second electromagnetic clutch B-C / L as planetary gear switching means
2 electromagnetic clutches, a generator motor MG that operates as a generator and an engine, and a brake BRK as a first planetary gear switching unit in the claims.

As shown, the first electromagnetic clutch A-
The C / L is provided so that the input shaft 1 and the output shaft 2 can be connected and disconnected. In addition, the first planetary gear PGS1
Is connected to the input shaft 1 so that the carrier 12 can transmit torque, and the sun gear 11 is connected to the rotor 1 of the generator motor MG.
6 is attached, and the ring gear 13 can be fixed and released by the brake BRK. In addition,
When the ring gear 13 is fixed and the sun gear input / carrier output is performed, the first planetary gear PGS1 is 1 /
Sun gear 11 and ring gear 1 so that the speed is reduced to 3.
The number of teeth of 3 is set.

The second planetary gear PGS2 is a carrier 2
2 is a second electromagnetic clutch B-C / with respect to the output shaft 2.
The sun gear 21 is configured to be connectable and disconnectable by L.
Is connected to the carrier 12 of the first planetary gear PGS1 and the ring gear 23 is fixed to a housing H described later. The second planetary gear PGS2 is formed with the number of teeth reduced to 1 / 2.5 when the ring gear 23 is fixed and the sun gear input / carrier output is performed.

Next, the details of the above-mentioned power transmission unit MGU will be described with reference to the sectional view of FIG.

One end of the input shaft 1 is connected to a crankshaft 6 of the engine EG via vibration absorbing means 5.
The vibration absorbing means 5 has high rigidity in the rotation direction,
A well-known one is used which is provided with an elastic plate for absorbing bending vibration that has low rigidity in the bending direction and a damper plate that has low rigidity in the rotating direction and high rigidity in the bending direction, and the crankshaft 6 of the engine EG is used. When the torque is input from, it absorbs bending vibration and torsional vibration.

In the figure, H is a housing for accommodating the power transmission unit MGU of the first embodiment. This housing H has four discs 41, 42, 43, which have a hole in the center.
44, a circular pipe 45, 46 for connecting the discs 41, 42, 43, 44 and a connecting member 47 to form a cylindrical shape, and input to the inner circumference of the discs 41, 44 via bearings 49, 49. The shaft 1 and the output shaft 2 are rotatably supported. Further, in the middle part of the disc 41, the circular pipe 40 is
Are combined. Oil chamber seal members 50, 50 are provided next to both bearings 49, 49 to seal the oil chamber OR on the inner circumference of the housing H. In addition, both bearings 49, 49
The axial dimension is controlled by. Further, air-cooling fins 48 are radially formed on the outer circumference of the circular pipe 45 of the largest diameter portion of the housing H as shown in the sectional view of FIG.

On the outer periphery of the input shaft 1, a magnetic path forming ring 3 made of a non-magnetic material and formed in a disk shape having a hole in the center is formed.
1 is connected. By forming the magnetic path forming ring 31 with a non-magnetic material, a magnetic path short circuit of the electromagnetic solenoid 653 described later is prevented.

At the outer peripheral end of the magnetic path forming ring 31,
The input circular pipe 32 is connected. This input pipe 32 is
In the drawing, the left end is connected to the carrier 12 of the first planetary gear PGS1 via the rotating body 33, and the sun gear 21 of the first planetary gear PGS1 is connected to the outer periphery of the middle part. A disk 32a is connected to the inner side of the portion. A first electromagnetic clutch A-C / L is provided between the input circular pipe 32 and the output shaft 2, the details of the configuration of which will be described later. The magnetic path forming ring 31 is axially supported by the thrust bearing 51. In addition, in the middle part of the input circular pipe 32,
A plurality of oil supply holes 32b are formed to guide the lubricating oil in the outer diameter direction.

In the outer diameter direction of the input circular pipe 32, a sun gear circular pipe 38 on the left side in the drawing and an output circular pipe 39 on the right side in the drawing are input circles with the sun gear 21 of the second planetary gear PGS2 interposed therebetween. It is provided on the outer circumference of the tube 32 with a space. The output circular pipe 39 is connected to the output shaft 2 by a disc 39a, and the disc 39a is axially supported by a thrust roller 52.

In the outer diameter direction of the output circular pipe 39, there is provided a carrier circular pipe 37 having a substantially U-shaped cross section in which discs 37a and 37b are connected to each other with a space provided therebetween. The second electromagnetic clutch B-C / L is provided between the pipe 37 and the output circular pipe 39, and the details of the configuration will be described later. An oil supply hole 37d is penetrated through the circular pipe 37 to guide the oil in the outer diameter direction.

The second planetary gear PGS2 is a carrier 2
2 is coupled to the disk 37a of the carrier circular tube 37, and the ring gear 23 is coupled to the inner circumference of the circular tube 46 of the housing H, that is, fixed to the housing H. The sun gear 21 is connected to the input circular pipe 32 as described above.

The first planetary gear PGS1 is a sun gear 1
1 is connected to a sun gear circular pipe 38 provided in the outer diameter direction of the input circular pipe 32, and the sun gear circular pipe 38 is
Is coupled to the sun gear connecting circular pipe 36 which is floatingly supported on the outer circumference of the circular pipe 46 of the housing H via a disc 36a, and the sun gear connecting circular pipe 36 is connected to the circular pipe 36b via the disc 36a. Are combined. The circular pipe 36b has bearings 53, 53 on the outer circumferences of the left and right ends in the figure.
The rotor 16 of the generator motor MG is attached to the outer periphery of the intermediate portion. A starter 17 is attached to the inner circumference of the circular pipe 45 so as to face the rotor 16. Therefore, the sun gear 11 of the first planetary gear PGS1 is configured to rotate together with the rotor 16. Incidentally, the first planetary gear PGS1 and the second planetary gear P
The GS2 is provided in front and back (left and right in the drawing) with the disk 36a interposed therebetween. Next to the bearing 53, the air chamber AR in which the generator motor MG is installed and the oil chamber OR described above.
Sealing members 55, 55 for separating the and are provided.
Further, the circular pipe 36b has thrust roller 54 at both ends.
Supported by.

Further, the ring 35a in which the ring gear 13 of the first planetary gear PGS1 is formed is connected with a ring gear connecting circular pipe 35 on the outer periphery thereof, and between the ring gear connecting circular pipe 35 and the circular pipe 40 of the housing H. Brake BR
K is provided. The ring gear connecting circular pipe 35 is provided with a plurality of oil supply holes 35d so as to guide the oil in the outer diameter direction.

Next, each electromagnetic clutch A-C / L, B-C
/ L and the brake BRK will be described. First, as described above, the first electromagnetic clutch A-C / L is provided between the output shaft 2 and the input circular pipe 32, and is provided at the innermost side of the above-described configuration. The first electromagnetic clutch A-C / L includes a main clutch 60A, a first rotating body 61A, a second rotating body 62A, a cam mechanism 63A, a sub clutch 64A, and a fastening mechanism 65A.

The main clutch 60A is alternately mounted on the outer periphery of the output shaft 2 and the inner periphery of the input circular pipe 32 by spline coupling so that they can be relatively moved in the axial direction and cannot be relatively moved in the rotational direction. It is located in. Also,
One end of the main clutch 60A is restricted from moving in the axial direction by the disc 32a, and the other end is adjacent to the first rotating body 61A.

The first rotating body 61A is mounted on the output shaft 2 by spline coupling so as to be relatively movable in the axial direction but not relatively movable in the rotating direction. Further, a second rotary body 62A is provided so as to face the first rotary body 61A. The second rotating body 62A includes a disc 621 and a circular pipe 6 fixed to the inner circumference of the disc 621 as shown in the figure.
22 is formed into an annular shape having an L-shaped cross section, and is floated between the output shaft 2 and the input circular pipe 32.
That is, as shown in FIG. 4, oil oil is filled between the inner circumference of the second rotating body 62A and the output shaft 2, and thus the second rotating body 62A is in a floating state on the output shaft 2. Supported.

The first rotating body 61A and the second rotating body 62A
A cam mechanism 63A is provided between and. The cam mechanism 63A is arranged radially on the first rotating body 61A (see FIG. 4) and, as shown in FIG. 5, a thrust roller 632 mounted rotatably about an axis by a holding plate 631. The second rotary member 62A is provided with a cam groove 633 radially formed at a position facing the thrust roller 632, as shown in FIG.

Although not shown in the drawings, the second rotary body 62A has a first spring as shown in FIG. It is urged in the direction of coming into contact with the rotating body 61A. Therefore, the cam mechanism 63A includes the second rotating body 62A.
Is rotating with the first rotating body 61A, as shown in FIG.
In the initial state shown in (a), the cam groove 633 is arranged substantially at the center, and no axial force is generated. On the other hand, when relative rotation occurs between the two rotary bodies 61A and 62A as shown in FIG. 6B, the cam groove 633 of the second rotary body 62A is generated.
Rides on the thrust roller 632, which causes a relative displacement sh in the axial direction of the second rotary body 62A as shown in the figure, and a pressing force FP is generated.

A multi-plate sub-clutch 64A is axially movable relative to the circular pipe 622 of the second rotary body 62A and the portion of the input circular pipe 32 that faces the outer circumference of the circular pipe 622. In addition, the second rotating body 62A and the input circular pipe 32 are mounted so that they cannot be moved relative to each other in the rotation direction and are fastened.
It is provided so as to restrict the relative rotation with respect to and permit these relative rotations in the unfastened state.

The engaging mechanism 65A for engaging and disengaging the sub clutch 64A includes an armature 651 and an electromagnetic solenoid 653. The amateur 6
The reference numeral 51 is arranged between the second rotating body 62A and the sub-clutch 64A and is coupled to the input circular pipe 32 by spline coupling so as to be relatively movable in the axial direction and not relatively movable in the rotational direction to press the sub-clutch 64. It is installed as possible.

The electromagnetic solenoid 653 is provided in the housing H, and when energized, forms a magnetic path indicated by a dotted line A in the drawing, and the armature 651 is connected to the sub-clutch 6 by the sub-clutch 6.
The sub-clutch 64A is engaged by sucking in the direction of 4A.

Therefore, in the engagement mechanism 65A, when the electromagnetic solenoid 653 is energized, the amateur 651 engages the sub-clutch 64A by the generated attractive force. Therefore, in a state where the input circular pipe 32 and the output shaft 2 are relatively rotating, relative rotation occurs between the second rotating body 62A and the first rotating body 61A, and the cam mechanism 63A performs a cam operation to double the rotation. By outputting the force, the main clutch 60A is engaged, and the first electromagnetic clutch A-C / L is in the engaged state. In this case, the boost output of the cam mechanism 63A causes the main clutch 6 to operate.
Tightly tighten 0A to transmit a large torque. On the other hand, when the electromagnetic solenoid 653 is not energized, the sub-clutch 64A is released, the second rotating body 62A is rotated by the first rotating body 61A, the cam mechanism 63A does not perform the cam operation, and the main clutch 60A is released. Then, the first electromagnetic clutches A-C / L are in the disengaged state.

Next, the second electromagnetic clutch B-C / L will be described. The basic structure is the first electromagnetic clutch A.
-Since it is common with C / L, a brief description will be given. The second electromagnetic clutch B-C / L is provided with both planetary gears PGS1 and PGS.
It is arranged so as to overlap the GS2 in the axial direction, and is provided between the output circular pipe 39 and the carrier circular pipe 37 as described above,
The second electromagnetic clutch B-C / L also includes a main clutch 60B, a first rotating body 61B, a second rotating body 62B, a cam mechanism 63B, a sub clutch 64B, and a fastening mechanism 65B.

The main clutch 60B is the output circular tube 3
9 and the carrier circular pipe 37 are alternately arranged so as to be relatively movable in the axial direction but not relatively rotatable.

The first rotary body 61B is mounted on the output circular pipe 39 so as to be relatively movable in the axial direction but not relatively rotatable. The second rotating body 62B is floatingly supported between the output circular pipe 39 and the carrier circular pipe 37. The cam mechanism 63B is similar to the first electromagnetic clutch A-C / L in that the thrust roller 63 held by the first rotating body 61B.
2 and a cam groove formed in the second rotating body 62B (not shown)
Is equipped with.

The sub-clutch 64B includes the second rotary member 6
The 2B circular pipes 622 and the carrier circular pipes 37 are alternately arranged so that they can be relatively moved in the axial direction and cannot be relatively rotated. The fastening mechanism 65B includes an armature 651 mounted on the carrier circular tube 37 so as to be able to press the sub-clutch 64B, and an electromagnetic solenoid 65 provided in the housing H to attract the armature 651 when energized.
3 and 3. Therefore, when the electromagnetic solenoid 653 of the fastening mechanism 65B is energized, the sub clutch 64
B is engaged, whereby relative rotation occurs between the first rotating body 61B and the second rotating body 62B, the cam mechanism 63B outputs a boosted force, and the main clutch 60B is engaged, whereby the output circular pipe 39 and the carrier circular tube 37 are connected. When the electromagnetic solenoid 653 of the engagement mechanism 65B is not energized, the sub clutch 64B is released, the main clutch 60B is released, and the coupling between the output circular pipe 39 and the carrier circular pipe 37 is released. .

In FIG. 2, 18 is a generator motor MG.
To the inverter (not shown), and the electric power wiring that supplies the electric power to the inverter and outputs the electric power generated by the generator motor MG.
Further, in the figure, 19 is each electromagnetic clutch A-C / L,
Electromagnetic solenoid 65 for B-C / L and brake BRK
3 is an electric power wiring for supplying electric power to 3.

Next, the brake BRK will be described. The structure of the brake BRK is also the first electromagnetic clutch A-.
Since it is common with C / L, a brief description will be given. This brake BRK is arranged in the outer radial direction of both planetary gears PGS1, PGS2 and the second electromagnetic clutch B-C / L, and as described above, between the ring gear connecting circular pipe 35 and the circular pipe 40 of the housing H. Provided and main clutch 60
K, first rotary body 61K, second rotary body 62K, cam mechanism 6
It is provided with 3K, a sub clutch 64K, and a fastening mechanism 65K.

The main clutch 60K is arranged alternately in the ring gear connecting circular pipe 35 and the circular pipe 40 so as to be relatively movable in the axial direction and not relatively rotatable.

The first rotating body 61K is mounted on the ring gear connecting circular pipe 35 so as to be relatively movable in the axial direction and not relatively rotatable. The second rotating body 62K is floatingly supported between the ring gear connecting circular pipe 35 and the circular pipe 40. The cam mechanism 63K includes the first electromagnetic clutch A.
Like -C / L, it has a thrust roller 632 held by the first rotary body 61K and a cam groove (not shown) formed in the second rotary body 62K.

The sub-clutch 64K includes the second rotary member 6
The 2K circular pipes 622 and the circular pipes 40, which are relatively movable in the axial direction and cannot be relatively rotated, are alternately arranged. The fastening mechanism 65K includes an armature 6 mounted on the circular pipe 40 so as to press the sub clutch 64K.
51 and an electromagnetic solenoid 653 which is provided in the housing H and attracts the armature 651 when energized. Therefore, the electromagnetic solenoid 65 of the fastening mechanism 65K
When electricity is applied to 3, the sub clutch 64K is engaged,
As a result, relative rotation occurs between the first rotating body 61K and the second rotating body 62K, the cam mechanism 63K outputs a boosted force, and the main clutch 60K is engaged, whereby the ring gear connecting circular pipe 35 and the circular pipe. 40 and 40 are combined. When the electromagnetic solenoid 653 of the engagement mechanism 65K is not energized, the sub clutch 64K is released, the main clutch 60K is released, and the ring gear connection circular pipe 35 and the circular pipe 40 are disconnected. .

Next, the operation of the power transmission unit MGU will be described with reference to the operation explanatory diagram of FIG. (At engine start)
When starting the engine EG, the first electromagnetic clutch A
-C / L and the second electromagnetic clutch B-C / L are disengaged, and the brake BRK is engaged to operate to generate the generator motor MG.
Is initially operated as a motor. In this case, the generator gear motor MG rotates the sun gear connecting circular pipe 36, and the sun gear connecting circular pipe 36 is input to the sun gear 11 of the first planetary gear PGS1 to be supplied to the carrier 1
It is decelerated from 2 to 1/3, transmitted to the input circular pipe 32, and further transmitted from the input shaft 1 to the crankshaft 6 of the engine EG.

This state is shown in the operation explanatory view of FIG. 7, and the rotation of the generator motor MG is decelerated (torque increased) by the first planetary gear PGS1 in this way, and the engine E is rotated.
Since it is input to G, the drive torque required to start the engine EG in the generator motor MG can be made lower than in the case where the reduction ratio is not obtained, and the generator motor MG can be made compact. . That is, in the present embodiment, conventionally, in the automatic transmission, the power transmission unit MG is installed in the limited space for installing the torque converter.
U is installed, and therefore, the structure is such that the generator motor MG is arranged on the outer side of the rotating body, but it is aimed to make the structure as compact as possible as a whole. In such a structure, the generator motor Reducing the required drive torque of the MG is very effective in terms of downsizing.

Further, if the engine EG speed becomes equal to or higher than a predetermined speed and it becomes unnecessary to apply torque from the generator motor MG, the generator motor MG can be operated as a generator. In this case, the first planetary gear is used. In the gear PGS1, the carrier input / sun gear output is used for speed-up operation, and the rotor 16 is speeded up by 3 times, so that efficient power generation can be performed.

(Starting, creeping, hill hold) When starting after starting the engine EG, or
Fig. 6 is used when creeping in which the vehicle gradually moves forward or backward without stepping on the accelerator, or when performing hill hold to keep the vehicle speed at 0 km / h on an uphill road.
, The engine EG is driven, and the generator motor M
G is turned ON / OFF as required to release the first electromagnetic clutch A-C / L, while the second electromagnetic clutch B-
C / L is engaged, and brake BRK is turned on depending on the situation.
(Tighten) / OFF (release). Brake BR here
When K is turned off, the first planetary gear PGS1 does not perform the torque transmission operation, and the drive torque of the engine EG is
From the input circular pipe 32 to the sun gear 21 of the second planetary gear PGS2
Is input to the carrier circular tube 37, is decelerated from the carrier 22 to 1/2, is output to the carrier circular tube 37, and is further transmitted from the output circular tube 39 to the output shaft 2 via the second electromagnetic clutch B-C / L. . This state is shown in the operation explanatory view of FIG. 8, and as described above, the driving torque of the engine EG is the second planetary gear PG.
It is decelerated (torque increased) by S2 and transmitted from the output shaft 2 to the transmission TM. Therefore, it is possible to smoothly start the vehicle and also to perform the creep running smoothly. At this time, in the second electromagnetic clutch B-C / L, slip control is not performed, and there is an effect that it is possible to increase torque and perform start and creep running without causing heat generation.

On the other hand, when the brake BRK is engaged, the first planetary gear PGS1 is in a torque transmittable state. In this case, when the generator motor MG is driven as a motor, the drive torque generated in the generator motor MG is decelerated to 1/3 and is input to the sun gear 21 of the second planetary gear PGS2 together with the drive torque of the engine EG, and the transmission TM It is possible to output a larger torque. That is, the torque of the engine EG can be assisted. On the other hand, when the generator motor MG is operated as a generator, part of the driving torque of the engine EG is consumed in the generator motor MG, and the transmission T
The torque input to M decreases. Thus, when the brake BRK is engaged, the generator motor M is further
By operating G as a motor or a generator, the torque input to the transmission TM can be increased or decreased, and more detailed control can be performed. This control is particularly effective for hill hold.

Further, in the first embodiment, when the vehicle starts or creeps, the engine EG is not driven and only the generator motor MG can be used to start or creep. That is, as described above, when the brake BRK is engaged in addition to the second electromagnetic clutch B-C / L and the generator motor MG is driven as a motor, the motor drive torque is 1/0 in the first planetary gear PGS1. It is decelerated to 3 and input from the carrier 12 to the sun gear 21 of the second planetary gear PGS2, and further decelerated to 1 / 2.5 in the second planetary gear PGS2, and the transmission TM
Entered in. Therefore, the output torque of the generator motor MG is increased 7.5 times, and even the small generator motor MG assists the driving force of the engine EG,
Further, it is possible to improve fuel efficiency by starting or creeping with the driving force of only the generator motor MG.

(During steady running / acceleration) After starting as described above, as shown in FIG. 6, with the engine EG being driven, the generator / motor MG is either a motor or a generator. The first electromagnetic clutch A-C /
L is released, the second electromagnetic clutch B-C / L is engaged, and the brake BRK is released. This state is shown in the operation explanatory view of FIG. 9, and the driving force of the engine EG is directly output from the input shaft 1 to the output shaft 2 via the first electromagnetic clutch A-C / L. The reduction ratio is 1.

(Deceleration Regeneration) When performing regeneration during deceleration, as shown in FIG. 6, the engine EG is not operated, the generator motor MG is operated as a generator, and the first electromagnetic clutches A-C are used.
/ L is engaged and the second electromagnetic clutch B-C / L is released. The brake BRK is engaged according to the vehicle speed, or slip control is performed or released.

For example, at a low speed of 50 km / h or less, the brake BRK is engaged. In this case, the drive wheel torque input from the transmission TM is as shown in FIG.
As shown in the operation explanatory diagram of No. 1, the first electromagnetic clutch A-C /
After passing L, the first planetary gear PGS1 receives carrier input and sun gear output, and the speed is tripled to generate the generator motor M.
G generates electricity. Therefore, efficient regenerative power generation becomes possible.

Further, for example, at a medium or high speed of 50 km / h or more, the brake BRK is appropriately turned off or slip control is executed. When the brake BRK is turned off, the first planetary gear PGS1 does not transmit torque, and the generator motor MG does not perform regenerative power generation. Therefore, only engine braking due to the rotation of the engine EG acts and steering stability can be ensured.
In addition, by performing slip control on the brake BRK as necessary, only part of the drive wheel torque input from the transmission TM is transmitted to the generator motor MG, and regenerative power generation can be performed gently. The braking force generated by the resistance on the drive side can be adjusted.

As described above, the first embodiment
Then, without using the torque converter, the first and second
Since the torque is transmitted using the planetary gears PGS1 and PGS2, the first and second electromagnetic clutches AC / L and BC / L, and the brake BRK, the torque transmission efficiency is excellent. Moreover, both planetary gears PGS1 and PG1 are used at the time of starting, creeping, and hill-holding even though the electromagnetic clutches A-C / L, B-C / L and the brake BRK are used.
In S2, the speed is reduced to transmit the torque, and the low speed / high torque output can be achieved without using the slip control with heat generation in the electromagnetic clutches AC / L, BC / L and the brake BRK. Therefore, according to the first embodiment applied to a vehicle, it is possible to perform start / creep / hill hold without heat generation.

Further, the engine E is driven by the generator motor MG.
Although the G is started, at the time of starting, the first planetary gear PGS1 is decelerated to 1/3 and the engine EG is decelerated.
Since the torque of the generator motor MG can be transmitted to the engine, the generator motor MG can be downsized.

Further, in the first embodiment, the output of the generator motor MG is decelerated at the time of starting, and at the same time the first planetary gear PGS1 that performs a speed change operation to increase the speed of the generator motor MG at the time of power generation, at the time of starting, etc. Since the second planetary gear PGS2 that reduces the torque when the torque of the engine EG is output to the transmission TM is provided, the number of required electromagnetic clutches can be reduced and the cost can be reduced. That is, it is possible to perform the above-described two types of speed change with one planetary gear. For example, in the first embodiment, switching means for connecting and disconnecting the sun gear 11 of the first planetary gear PGS1 and the input shaft 1 is provided, and the carrier 12 of the first planetary gear PGS1 is directly connected to the output shaft 2. So this is possible. By the way, 1
The applicant of the present application has disclosed a device for transmitting power by switching between three planetary gears and three clutches.
I am applying for No. 4. However, when comparing the planetary gear and the electromagnetic clutch, the electromagnetic clutch is more expensive, and the device of the first embodiment has the number of planetary gears increased as compared with the invention of this prior application. By reducing the number of electromagnetic clutches, the overall cost can be reduced.

Furthermore, in the first embodiment, the first
The first planetary gear PGS1, the second planetary gear PGS2, and the second electromagnetic clutch B-C / L are provided so as to overlap in the outer diameter direction of the electromagnetic clutch A-C / L, and further, the brake BRK is provided so as to overlap in the outer diameter direction. Provided, and further outside the generator motor MG
Since the above configuration is provided, the entire configuration of the device can be made compact both in the axial direction and the outer diameter direction, and thus high vehicle mountability can be obtained.

(Second Embodiment) Next, a power transmission unit MGU having the power transmission unit of the second embodiment will be described. The second embodiment is defined in claims 1 to 3, 5, and 5.
It corresponds to the invention described in 7, 8, 10, and 12. In the description of the second embodiment, the same components as those in the first embodiment will be designated by the same reference numerals and the description thereof will be omitted.

The second embodiment is an example in which a band brake is provided as a brake (first planetary gear switching means) BRK for fixing the ring gear 13 of the first planetary gear PGS1, as shown in FIG. As shown in FIG. 12, the brake BRK includes a brake shoe 24 provided on the outer circumference of a ring gear connecting circular pipe 35 and the brake shoe 2
4 and a brake band 25 mounted so as to be opposed thereto. Further, both ends of the brake band 25 are biased in the fastening direction by springs 26 and 27, while one end of the brake band 25 is movable in the direction opposite to the biasing force of the spring 26 by a hydraulic actuator 28. It is composed. That is, this brake B
The RK is fastened by the urging force of the springs 26 and 27 to fix the ring gear connection circular pipe 35 when the hydraulic actuator 28 is not operated, and when the hydraulic actuator 28 is actuated, the fastening is released and the ring gear 23 is unfixed. The hydraulic actuator 28 is configured to be activated when it is detected that the vehicle speed is equal to or higher than a predetermined speed. An electromagnetic actuator may be used instead of the hydraulic actuator 28, or a centrifugal weight that automatically releases the fastening when rotating at a speed higher than a set speed is used, or when the vehicle is stopped and at a low speed, it faces the electromagnet. The ring gear connecting circular pipe 35 may be fixed by an amateur, and the structure may be used in which the electromagnet is de-energized for a certain speed or more and the fastening is released by the return spring.

Since the band brake used as the brake BRK has a small axial dimension, the generator motor M
G is provided side by side behind the brake BRK (right side in the figure). That is, the outer circumference of the sun gear connection circular pipe 36 is supported by the pair of bearings 53, and the rotor 16 is mounted between the bearings 53. The ring gear connecting circular pipe 35 is supported in the housing H in the axial direction by the thrust roller 201, and the sun gear connecting circular pipe 36.
The thrust roller 202 to move the housing H in the axial direction.
Supported by. Further, in the second embodiment, the housing H is formed by the disks 341, 342, 343, 344, the connecting member 347, and the circular tubes 345, 346.

In the above-described second embodiment, since the brake BRK which is released when the vehicle speed reaches the predetermined vehicle speed is used, the operation at the time of starting is slightly different from that of the first embodiment. This will be described. . That is, in the second embodiment, when starting, the brake BRK is switched between ON and OFF depending on the vehicle speed as shown in the operation explanatory view of FIG. When the vehicle speed is less than the predetermined speed, the brake BRK is engaged (ON),
The generator motor MG is rotated at a triple speed of the input shaft 1. In this case, if the generator motor MG is operated as a generator,
Power can be efficiently generated, and if the generator motor MG is driven as a motor, the engine EG can be assisted. On the other hand, when the vehicle speed exceeds the predetermined speed, the brake BRK is released, and the rotor 16 of the generator motor MG is driven around freely.

In the second embodiment described above, since the band brake is used as the brake BRK, the radial dimension of the device can be reduced and the device can be made compact. Note that other operational effects are the same as those in the first embodiment, and therefore description thereof is omitted.

(Third Embodiment) Next, a power transmission unit MGU to which the power transmission unit of the third embodiment is applied will be described. The third embodiment is characterized in that
It corresponds to the invention described in 4, 6, 7, 9, 13, and 14. In addition, in describing the third embodiment,
The same configurations as those in the first embodiment are designated by the same reference numerals as those in the first embodiment, and the description thereof will be omitted.

FIG. 13 is a skeleton diagram showing the power transmission unit MGU of the third embodiment. In the third embodiment, the first planetary gear P provided on the outer periphery of the input shaft 1
In the GS1, the generator motor MG is attached to the sun gear 11, and the carrier 12 is configured to be connectable and disconnectable by an electromagnetic clutch C / L as a first planetary gear switching unit.
The ring gear 13 is fixed to the housing H.

The sun gear 21 of the second planetary gear PGS2 can be fixed and released by the brake BRK as the second planetary gear switching means, and the carrier 2
2 is connected to the output shaft 2 and the ring gear 23 is connected to the input shaft 1. The second planetary gear PGS2 has a ring gear input and a carrier output, and the number of teeth is set so that the reduction ratio is between 1/1 and 1/2.

Next, the operation of the third embodiment will be described. (At engine start) When starting the engine EG,
The first planetary gear PGS1 is engaged by engaging the electromagnetic clutch C / L.
The carrier 12 and the input shaft 1 are connected, while the first electromagnetic clutch A-C / L is released and the brake BRK is released, and in this state, the generator motor MG is driven as a motor. Therefore, similarly to the first embodiment, the rotation of the generator motor MG is decelerated by the first planetary gear PGS1 and transmitted to the engine EG, and the engine EG can be started with a small output.

(At the time of starting, creeping, and hillholding) At the time of starting, the electromagnetic clutch C / L is released, the first electromagnetic clutch A-C / L is engaged, and the brake BRK is released.
Brake operation. As a result, the rotation of the engine EG is decelerated by the ring gear input / carrier output and transmitted to the output shaft 2 in the second planetary gear PGS2.

The same operation as described above is performed during creep and hill hold, but in these cases, the electromagnetic clutch C / L is further engaged, and the generator motor MG is operated as a generator so that the transmission TM is transmitted. By reducing the transmitted torque, or vice versa, by operating the generator motor MG as a motor to assist the engine torque, the transmission T
The torque input to M can be controlled.

(During Acceleration / Steady Running) During acceleration and steady running, the electromagnetic clutch C / L is released, the first electromagnetic clutch A-C / L is engaged, and the brake BRK is released. Therefore, the driving force of the engine EG is transmitted to the transmission TM at a ratio of 1: 1. In addition, at this time, the rotor 16 of the generator motor MG runs around freely.

(During deceleration regeneration) During deceleration regeneration, the electromagnetic clutch C / L is engaged from the above state and the generator motor MG is operated as an electric motor.

In the first embodiment described above, the second planetary gear PGS2, which is decelerated at the time of starting, is decelerated by the ring gear input and the carrier output.
Since the reduction ratio is kept low, the speed is reduced at the time of starting, and the speed is reduced to 1: 1 in the acceleration / steady running state.
The torque step that occurs when the state is changed to the state where torque is transmitted is reduced. That is, FIG. 14 shows an example of the gear ratio in the transmission TM, but when gear shifting is performed in the second planetary gear PGS2 of the third embodiment, the difference from the gear ratio 11.65 in the first speed is shown. Is smaller, the torque step can be suppressed, and the driver is unlikely to feel uncomfortable.

(Fourth Embodiment) Next, a power transmission unit MGU according to a fourth embodiment will be described. The fourth embodiment corresponds to the invention described in claims 1, 4, 7, 13, and 14. Since the fourth embodiment is a modification of the third embodiment, differences from the third embodiment will be described.

FIG. 15 is a skeleton diagram showing a power transmission unit MGU according to the fourth embodiment.
In the third embodiment, the electromagnetic clutch C / L is removed and the carrier 12 and the input shaft 1 are directly connected. In the fourth embodiment, since the rotor 16 of the generator motor MG is rotated at an increased speed while the engine EG is driven, a generator motor MG that can be driven at high rotation speed is used.

In the fourth embodiment, the number of electromagnetic clutches can be further reduced by one, so that the cost of the device can be further reduced.

The embodiment of the present invention has been described in detail above with reference to the drawings. However, the specific structure is not limited to this embodiment, and changes in design within the scope not departing from the gist of the present invention. Even if it exists, it is included in the present invention. For example, as an input member and an output member as an embodiment,
Although the input shaft 1 and the output shaft 2 are shown, these members are
Not limited to the shaft, a tubular member or the like may be used.

[Brief description of drawings]

FIG. 1 is a skeleton diagram showing a power transmission unit according to a first embodiment of the present invention.

FIG. 2 is a cross-sectional view showing the power transmission unit according to the first embodiment.

FIG. 3 is a cross-sectional view showing the main parts of the power transmission unit according to the first embodiment.

FIG. 4 is a cross-sectional view showing the main parts of the power transmission unit according to the first embodiment.

FIG. 5 is a cross-sectional view showing the main parts of the power transmission unit according to the first embodiment.

FIG. 6 is an operation explanatory diagram of the first embodiment.

FIG. 7 is an operation explanatory diagram at the time of starting of the first embodiment.

FIG. 8 is an operation explanatory diagram of the first embodiment such as at the time of starting.

FIG. 9 is an operation explanatory diagram of the first embodiment during acceleration / steady running.

FIG. 10 is an operation explanatory diagram during deceleration regeneration according to the first embodiment.

FIG. 11 is a sectional view showing a power transmission unit according to a second embodiment.

FIG. 12 is a cross-sectional view showing the main parts of the power transmission unit according to the second embodiment.

FIG. 13 is a skeleton diagram showing a power transmission unit according to a third embodiment.

FIG. 14 is an explanatory diagram of a gear ratio according to the third embodiment.

FIG. 15 is a skeleton diagram showing a power transmission unit according to a fourth embodiment.

[Explanation of symbols]

1 input axis 2 output shaft 5 Vibration absorption means 6 crankshaft 11 sun gear 12 career 13 ring gear 16 rotor 17 Starter 21 Sun Gear 22 career 23 ring gear 24 brake shoes 25 Brake Band 26,27 spring 28 Hydraulic actuator 31 Magnetic path forming ring 32 input tube 32a disc 32b Oil supply hole 33 rotating body 35 Ring gear connection circular pipe 35a ring 35d oil supply hole 36 Sun gear connection circular pipe 36a disc 36b circular tube 37 carrier tube 37a, 37b discs 37d Oil supply hole 38 Sun Gear Round Tube 39 Output circular tube 39a disc 40 tube 41, 42, 43, 44 disks 45 round tube 46 circular tubes 47 Connecting member 48 air cooled fins 49,49 bearings 50 Oil chamber seal member 51 thrust bearing 52 Thrust roller 53 bearings 54 Thrust roller 55 Seal member 60A main clutch 60B main clutch 60K main clutch 61A rotating body 61B rotating body 61K rotating body 62A rotating body 62B rotating body 62K rotating body 63A cam mechanism 63B cam mechanism 63K cam mechanism 64A sub clutch 64B sub clutch 64K sub clutch 65A fastening mechanism 65B fastening mechanism 65K fastening mechanism 201 thrust roller 202 thrust roller 341, 342, 343, 344 disks 345,346 circular tube 347 connecting member 621 disc 622 circular tube 631 holding plate 632 thrust roller 633 cam groove 651 amateur 653 Electromagnetic solenoid AR air chamber BRK brake AC / L First electromagnetic clutch B-C / L Second electromagnetic clutch C / L electromagnetic clutch EG engine FP pressing force H housing MG generator motor MGU power transmission unit OR oil chamber PGS1 1st planetary gear PGS2 Second planetary gear TM transmission

Continuation of front page (51) Int.Cl. ⁷ Identification code FI theme code (reference) F16H 3/66 B60K 9/00 ZHVE F term (reference) 3D039 AA02 AA03 AB01 AC39 AD02 AD23 AD53 3J028 EA25 EA27 EB04 EB33 EB35 EB37 EB62 EB63 EB66 FB03 FB06 FB12 FB14 FC13 FC24 FC62

Claims (15)

[Claims] 1. An input member for transmitting torque from a prime mover and an output member for outputting torque to a transmission, a direct connection switching clutch capable of connecting and disconnecting the input member and the output member, and operating as a generator and an electric motor. A first planetary gear capable of reducing the rotation of the input member and transmitting the same to a possible generator-motor, a second planetary gear capable of reducing the rotation of the input member and transmitting the same to the output member, and the second planetary gear Is provided with a second planetary gear switching unit that switches between a state in which the gear shift operation is performed and a state in which the gear shift operation is not performed for any one of the input member and the output member, and a power transmission unit. 2. The first planetary gear switching device is provided with a first planetary gear switching unit that switches between a state in which the first planetary gear shifts and does not shift the input member. The power transmission unit according to claim 1. 3. A transmission switching clutch capable of connecting and disconnecting a torque transmission path between the second planetary gear and the input member or the output member, wherein the second planetary gear switching means is a transmission switching clutch. Alternatively, the power transmission unit described in 2. 4. The power transmission unit according to claim 1, wherein the second planetary gear switching unit is a brake that fixes or unlocks a fixing element of the second planetary gear. 5. The power transmission unit according to claim 1, wherein the first planetary gear switching unit is a brake that locks and unlocks a fixed element of the first planetary gear. 6. The transmission switching clutch capable of connecting and disconnecting a torque transmission path between the input member and the first planetary gear, wherein the first planetary gear switching means is a transmission switching clutch. The power transmission unit according to any one. 7. The first planetary gear according to claim 1, wherein the carrier is connected to the input member, the sun gear is connected to the generator motor, and the ring gear is a fixed element.
The power transmission unit according to any one of 1. 8. The power transmission unit according to claim 7, wherein the ring gear of the first planetary gear has a structure in which the ring gear of the first planetary gear can be fixed and released by a brake serving as a first planetary gear switching unit. . 9. The power transmission unit according to claim 7, wherein the carrier of the first planetary gear and the input member can be connected and disconnected by a transmission switching clutch as a first planetary gear switching means. And a power transmission unit. 10. The second planetary gear according to claim 1, wherein the sun gear is connected to the input member, the carrier is connected to the output member, and the ring gear is a fixed element.
The power transmission unit according to any one of 1. 11. The power transmission unit according to claim 10, wherein the ring gear of the second planetary gear has a configuration in which the ring gear of the second planetary gear can be fixed and released by a brake serving as a second planetary gear switching unit. . 12. The power transmission unit according to claim 10, wherein one of a carrier and an output member of the second planetary gear or a sun gear and an input member is connected and disconnected by a transmission switching clutch as a second planetary gear switching means. A power transmission unit having a possible configuration. 13. The second planetary gear according to claim 1, wherein a ring gear is connected to the input member, a carrier is connected to the output member, and a sun gear is a fixed element.
The power transmission unit according to any one of 1. 14. The power transmission unit according to claim 13, wherein the sun gear of the second planetary gear has a structure in which the sun gear can be fixed and released by a brake. 15. The power transmission unit according to claim 13, wherein either the carrier and the output member of the second planetary gear or the ring gear and the input member are connected and disconnected by a transmission switching clutch serving as the second planetary gear switching means. A power transmission unit having a possible configuration.