JP2003039961A - Power transmission unit - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a new power transmission unit having excellent torque transmission efficiency, capable of low-speed/high-torque output to perform the starting/creep traveling or hill holding, and compactly formed while with a function of a power generator and a starter motor to have an excellent on- vehicle mountability. SOLUTION: This power transmission unit has an input circle pipe 32 connected to an input shaft 1, provided in an external diameter direction of an output shaft 2; a carrier connection circle pipe 34 connected to a carrier 12 and a sun gear connection circle pipe 36 connected to a sun gear 11 pinchingly provided inside and outside the input circle pipe 32; a rotor 16 of a power generating electric motor MG directly or indirectly installed to the sun gear connection circle pipe 36; a second clutch B-C/L provided between the output shaft 2 and the carrier connection circle pipe 34; a first clutch A-C/L provided between the carrier connection circle pipe 34 and the input circle pipe 32; and a third clutch C-C/L provided between the input circle pipe 32 and the sun gear connection circle pipe 36.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention is capable of transmitting power between a vehicle engine and a transmission, and
The present invention relates to a power transmission unit that can start an engine and generate 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 power transmission unit between an engine as a power source and the automatic transmission. Such a technique is described, for example, in Vol. 14 of Automotive Engineering Complete Book (published on November 20, 1980 by Sankaido Co., Ltd.).
It is described on page 9. Further, as another power transmission means, a clutch is known, and an automatic clutch system for automatically engaging and disengaging the clutch as required is proposed from the requirement of simplicity of operation. ,
A dry type single plate clutch is 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. In other words, in order to transmit low-speed / high-torque, the friction surface is slid to transmit torque, but heat is generated in this way, so-called creeping travel that gradually progresses due to engine idling rotation, and climbing. It is difficult to perform what is called a hill hold that stops on a slope. 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 that can actively generate a braking force, which increases the cost of the vehicle.

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 intended to provide.

[0006]

To achieve the above object, a power transmission unit of the present invention is provided in a torque transmission path between an engine and a transmission, and an input shaft for transmitting torque from the engine, and An output shaft that is provided coaxially with the input shaft and outputs torque to the transmission, a planetary gear that is provided coaxially with the input shaft and the output shaft and that transmits rotation between the input shaft and the output shaft, and this planetary gear A first clutch provided between the carrier and the drive shaft, a second clutch provided between the carrier and the output shaft, and a sun clutch of the planetary gear and the drive shaft. A third clutch,
It is provided between the brake that fixes the ring gear of the planetary gear to the housing, and the rotating body that rotates integrally with the sun gear and the housing, and can rotate the rotating body as a motor, and An input circular pipe (32) coupled to the input shaft (1) is provided with a space in the outer diameter direction of the output shaft (2), Between the circular pipe (32) and the output shaft (2), a carrier connecting circular pipe (34) connected to the carrier is provided with a space between the input circular pipe (32) and the output shaft (2). A sun gear connection circular pipe (36) as at least a part of the rotating body coupled to the sun gear is provided with a space in the outer diameter direction of the input circular pipe (32). Directly to this sun gear connection circular pipe (36) Alternatively, or indirectly, the rotor (16) of the generator motor (MG) is attached, and the second clutch (BC / L) is provided between the output shaft (2) and the carrier connecting circular pipe (34). Is provided so that the output shaft (2) and the carrier connecting circular pipe (34) can be fastened and unfastened, and the first clutch (A) is provided between the carrier connecting circular pipe (34) and the input circular pipe (32). -C / L) is provided so that the carrier connecting circular pipe (34) and the input circular pipe (32) can be fastened and unfastened, and between the input circular pipe (32) and the sun gear connecting circular pipe (36). , The third clutch (C-C / L) is provided so that the input circular pipe (32) and the sun gear connecting circular pipe (36) can be fastened and fastened to each other.

According to a second aspect of the present invention, in the power transmission unit according to the first aspect, the planetary gear is located on the outer diameter side of the carrier connecting circular pipe (34) and includes the first clutch and the first clutch. The three clutches are arranged side by side in the axial direction.

According to a third aspect of the present invention, in the power transmission unit according to the first or second aspect, the air chamber (AR) is provided at the outermost periphery and accommodates the generator motor (MG).
And an oil chamber (O
R) and the sun gear connecting circular pipe (3
6) Alternatively, the outer periphery of the rotating member (36c) integrated with the sun gear connecting circular pipe (36) is supported by the housing via a pair of bearings (53), and an oil chamber (OR) is provided next to the bearings (53). And a seal member (5) for partitioning the air chamber (AR)
5) is provided.

According to a fourth aspect of the present invention, in the power transmission unit according to any one of the first to third aspects, the ring gear connecting circular pipe (38) is integrated with the housing with a space in the outer diameter direction. Circular pipe (46) is provided, and a circular pipe (36c) coupled to the sun gear connecting circular pipe (36) is provided on the outer diameter side of the circular pipe (46).
The rotor (16) is attached to c), and the circular pipe (46) and the ring gear connecting circular pipe (3) are used as the brake.
8) An electromagnetic multi-disc brake having a multi-disc main clutch (60K) attached to the above 8) is used.

According to a fifth aspect of the present invention, in the power transmission unit according to any one of the first to third aspects, the ring gear connecting circular pipe (38) is integrated with the housing with a space in the outer diameter direction. Circular pipe (46) is provided, and a circular pipe (36c) coupled to the sun gear connecting circular pipe (36) is provided on the outer diameter side of the circular pipe (46).
The rotor (16) is attached to c), and the circular pipe (46) and the ring gear connecting circular pipe (3) are used as the brake.
8) has a multi-plate main clutch (400) attached to the cylinder and a mass body (405) supported by the circular pipe (36c), and the rotation speed of the circular pipe (36c) is predetermined. Below, the main clutch is released, while the circular pipe (36
A centrifugal brake that engages the main clutch when the rotation speed of c) exceeds a predetermined speed is used.

According to a sixth aspect of the present invention, in the power transmission unit according to any of the first to third aspects, the rotor (16) of the generator motor (MG) is provided on the outer periphery of the sun gear connecting circular pipe (36). Installed as the brake,
A band brake capable of fixing and releasing the disc (338) attached to the outside of the sun gear is used,
The brake is provided side by side with the generator motor (MG) in the axial direction.

[0012]

According to the present invention, when the engine is started, the first clutch is engaged, the second clutch and the third clutch are disengaged, and the brake is engaged. Drive as. Therefore, the rotation of the generator motor is input from the sun gear to the planetary gear, is decelerated in the planetary gear, is transmitted from the carrier to the input shaft via the first clutch, and the engine is started. As described above, the rotation of the generator motor is increased in torque by deceleration and input to the engine, so that the engine can be started even if the output torque of the generator motor is small.

When torque is required when the engine is running, such as when starting, creeping, or hillholding, the first clutch is disengaged, and the second clutch and the third clutch are opened. Engage and engage the brake. In this case, the rotation of the engine is input from the input shaft to the sun gear of the planetary gears via the third clutch, is decelerated, and is output from the carrier to the output shaft. Is output as. Further, at this time, if the generator motor is operated as a generator, a part of the engine torque is recovered as electric energy and the torque transmitted to the transmission is reduced, while if the generator motor is operated as a motor, The output assists the engine output, and the torque transmitted to the transmission is increased. Therefore, by simultaneously controlling the operation of the generator motor, the torque transmitted to the transmission can be delicately controlled.

On the other hand, during normal driving, the first to third
Engage the clutch and release the brake. In this case, the rotation of the engine is transmitted from the input shaft to the carrier of the planetary gears via the first clutch, and is transmitted from this carrier to the output shaft via the second clutch. Therefore,
The input shaft torque is transmitted to the output shaft at a ratio of 1: 1.

Further, in order to perform the regeneration for generating electric power by the driving wheel torque during traveling, a method of disconnecting the planetary gear and the input shaft, that is, the engine side in a state where the engine brake does not act, and a planetary gear There is a method in which the input shaft is connected and the operation is performed in the state where the engine brake is applied. The former is preferably performed at low speed and the latter is preferably performed at high speed.

In the case of regeneration in which the former engine brake does not act, the first clutch and the third clutch are released and the second clutch is engaged. In this case, the drive wheel torque input to the output shaft is input from the carrier in the planetary gear, increased in speed from the sun gear, and output toward the generator motor. 1
It is possible to regenerate more efficiently than the case of regenerating by torque transmission of.

In the latter case of regenerating the engine brake, the first to third clutches are engaged and the brake is released. In this case, the drive wheel torque input to the output shaft is input to the carrier via the second clutch, is transmitted from the carrier to the input shaft via the first clutch as it is, and the engine brake can be applied. Further, this rotation of the input shaft is input to the generator motor via the third clutch, and power can be generated by torque transmission of 1: 1. At this time, the braking force by the engine brake can be adjusted by adjusting the amount of regeneration in the generator motor.

As described above, according to the present invention, it is possible to prevent the power loss due to the slippage like the torque converter, and to reduce the engine output at a low speed without using the heat generation such as slipping the clutch and the disadvantageous control. It is possible to obtain an effect that efficient conversion of energy can be achieved by converting the torque into high torque and outputting the converted torque, and by delicately controlling the transmission torque. Further, in the present invention, the first to third
Since the clutches are coaxially arranged in triple layers inside and outside, the axial dimension of the unit can be shortened and high vehicle mountability can be obtained.

According to the second aspect of the invention, since the planetary gears are arranged side by side in the axial direction with the first clutch and the third clutch, the entire structure can be compactly arranged in the housing.

According to the third aspect of the invention, it is possible to seal the oil chamber and the air chamber by utilizing the rotary member provided on the outermost periphery of the oil chamber of the unit.

According to the invention of claim 4, since an electromagnetic multi-plate brake is used as the brake, the ring gear can be reliably fixed by a large braking force, and
Fine control can be executed.

In the invention according to claim 5, since the centrifugal brake is used as the brake, control is performed to switch the brake between the braking state and the non-braking state when the vehicle is stopped, at low speed, and at high speed. Is unnecessary, and the electrical configuration can be simplified.

According to the sixth aspect of the invention, since the band brake is used as the brake, the volume occupied by the brake in the housing can be reduced and the unit can be downsized.

[0024]

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 according to the first embodiment includes the power transmission unit MGU according to any one of claims 1 to 4.
The present invention corresponds to the invention described in (1), and is provided in the middle of the power transmission path of the engine EG and the transmission TM, that is, at the position where the torque converter is arranged in a general automatic transmission, as shown in FIG. The transmission TM may be a manual transmission or a CV.
T or the like can be used. This power transmission unit M
The GU includes an input shaft 1 connected to a crank shaft 6 (see FIG. 1) of the engine EG, an output shaft 2 connected to an input shaft (not shown) of the transmission TM, the output shaft 2 and the input shaft 1. A planetary gear PGS provided coaxially with the first gear, a first clutch A-C / L for connecting and disconnecting the carrier 12 of the planetary gear PGS with the input shaft 1, and the carrier 1
Second clutch B- for connecting and disconnecting 2 with the output shaft 2
C / L and a third clutch C-C / L for connecting and disconnecting the sun gear 11 of the planetary gear PGS with the input shaft 1.
A generator / motor MG for exchanging electric power between the sun gear 11 and a sun gear connecting circular pipe 36 which is an integral rotating body;
A brake BRK for fixing and releasing the ring gear 13, which is a fixing element of the planetary gear PGS, is provided. In addition, each clutch A-C / L, B-C / L, C-C
/ L is a wet electromagnetic multi-plate clutch. Moreover, the brake BRK also uses the same wet multi-plate type.

Next, the power transmission unit MGU of the first embodiment will be described in detail 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 includes an elastic plate for bending vibration absorption that has high rigidity in the rotational direction and low rigidity in the bending direction, and, conversely, a damper plate that has low rigidity in the rotational direction and high rigidity in the bending direction. A well-known one is used to absorb bending vibration and torsional vibration when torque is input from the crankshaft 6 of the engine EG.

In the figure, H is a housing for accommodating the power transmission unit MGU of the first embodiment. The housing H has disks 41, 42 and 43 having a hole in the center, circular tubes 45 and 46 and a connecting member 47. Is formed into a cylindrical shape by and the input shaft 1 and the output shaft 2 are rotatably supported on the inner circumferences of the disks 41 and 43 via bearings 49 and 49. In addition, the seal members 50,
50 is provided to seal the oil chamber OR formed in the housing H. Further, the axial dimension is controlled by both bearings 49, 49. 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 circumference of the input shaft 1, a magnetic path forming ring 3 formed of a non-magnetic material and formed in a disk shape having a hole in the center thereof.
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.

In the vicinity of the outer circumference of the magnetic path forming ring 31,
One end of the input circular pipe 32 is connected, and further, the input circular pipe 32
A disk 32b is provided at the other end (on the right side in the figure) of the magnetic path forming ring 31 so as to face the outer peripheral portion thereof. The planetary gear PGS is arranged between the disk 32b and the disk 43 of the housing H at the right corner of the housing H in the drawing. The magnetic path forming ring 31 and the input circular tube 32 are axially supported by the housing H by thrust rollers 51 and 52.

A carrier connecting circular pipe 34 coupled to the carrier 12 of the planetary gear PGS is provided between the input circular pipe 32 and the output shaft 2, and a space is provided in the outer radial direction of the input circular pipe 32. A sun gear connecting circular pipe 36 is provided which is vacantly connected to the sun gear 11 of the planetary gear PGS. The left end of the sun gear connecting circular pipe 36 in the drawing is provided on the outer periphery of the circular pipe 46 of the housing H.
c and the disk 36b. In addition, circular tube 3
The outer periphery of 6c is a bearing 5 supported by the housing H.
Both ends in the axial direction are supported by 3, 53. Also,
Next to the bearing 53, the air chamber A in which the generator motor MG is installed
Seal members 55, 5 for separating R from the oil chamber OR described above
5 are provided.

Further, a ring gear connecting circular pipe 38 coupled to the ring gear 13 of the planetary gear PGS is floatingly supported on the outer periphery of the sun gear connecting circular pipe 36 with oil interposed. The oil chamber OR is provided in each of the carrier connecting circular pipe 34, the input circular pipe 32, the sun gear connecting circular pipe 36, and the ring gear connecting circular pipe 38 which are provided inside and outside the quadruple.
A plurality of oil supply holes 34p, 32p, 36p, 38p are formed so as to guide the lubricating oil filled in the outer peripheral direction from the inner peripheral side.

The output shaft 2, the inner and outer quadruple circular tubes 34, 32, 36 and 38, and the circular tube 4 of the housing H are provided.
6 and the second clutch B-C / L in order from the inside,
First clutch, A-C / L, third clutch C-C / L,
A brake BRK is provided. That is, the second
The clutch B-C / L is provided between the output shaft 2 and the carrier connecting circular pipe 34, and is the first clutch A-C / L.
Is provided between the carrier connecting circular pipe 34 and the input circular pipe 32, and the third clutch C-C / L is provided between the input circular pipe 32 and the sun gear connecting circular pipe 36. The brake BRK has a ring gear connecting circular pipe 38 and a circular pipe 46.
It is provided between and.

Next, each clutch A-C / L, B-C /
The L, C-C / L and the brake BRK will be described. First, as described above, the first clutch A-C / L is provided between the output shaft 2 and the carrier connecting circular pipe 34, and includes the main clutch 60B and the first rotating body 61.
B, a second rotating body 62B, a cam mechanism 63B, a sub clutch 64B, and a fastening mechanism 65B.

The main clutch 60B is mounted on the outer circumference of the output shaft 2 and the inner circumference of the carrier connecting circular pipe 34 by spline coupling so that they can move relatively in the axial direction but not in the rotating direction. They are arranged alternately. Further, one end of the main clutch 60B is restricted from moving in the axial direction by a stopper surface 2s provided on the output shaft 2, and the first rotating body 61B is provided adjacent to the other end of the main clutch 60B.

The first rotary body 61B 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 rotational direction. Further, a second rotating body 62B is provided so as to face the first rotating body 61B. The second rotating body 62B includes a disc 621 and a circular pipe 6 fixed to the inner circumference of the disc 621 as shown in the figure.
22 and the output shaft 2
Is floated between the carrier connection circular pipe 34 and the carrier connection circular pipe 34. That is, as shown in FIG. 4, the second rotating body 62B
An oil oil is filled between the inner circumference of the output shaft 2 and the output shaft 2, so that the second rotating body 62B is supported by the output shaft 2 in a floating state.

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

Although not shown in the drawing, the second rotary body 62B is provided with a return spring in the form of, for example, a leaf spring provided between the second rotary body 62B and the first rotary shaft 62B, as shown in FIG. It is urged in the direction of coming into contact with the rotating body 61B. Therefore, the cam mechanism 63B includes the second rotating body 62B.
Is rotating together with the first rotating body 61B, 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 both rotary bodies 61B and 62B as shown in FIG.
Rides on the thrust roller 632, which causes a relative displacement sh in the axial direction of the second rotating body 62B as shown in the figure, and a pressing force FP is generated.

A multi-plate sub-clutch 64B moves axially relative to the circular pipe 622 of the second rotary body 62B and a portion of the carrier connecting circular pipe 34 that faces the outer circumference of the circular pipe 622. It is mounted so as to be capable of being relatively moved in the rotation direction, and is provided so as to restrict the relative rotation between the second rotating body 62B and the carrier connecting circular pipe 34 in the fastening state and allow these relative rotations in the fastening release state. .

The engaging mechanism 65B for engaging and disengaging the sub clutch 64B includes an armature 651 and an electromagnetic solenoid 653. The amateur 6
51 is disposed between the second rotating body 62B and the sub-clutch 64B and is coupled to the carrier connecting circular pipe 34 by spline coupling so as to be relatively movable in the axial direction and incapable of being relatively movable in the rotational direction. It is installed so that it can be pressed.

The electromagnetic solenoid 653 is provided in the housing H, and when energized, forms a magnetic path indicated by a dotted line in the drawing, so that the armature 651 is connected to the sub clutch 64.
The sub-clutch 64B is engaged by sucking in the direction of B. Therefore, the fastening mechanism 65B includes the electromagnetic solenoid 6
When power is supplied to 53, the amateur 651 engages the sub-clutch 64B by the generated suction force. Therefore, in the state where the carrier connecting circular pipe 34 and the output shaft 2 are relatively rotating, relative rotation is generated between the second rotating body 62B and the first rotating body 61B, and the cam mechanism 63B performs the cam operation. By outputting the boosted force, the main clutch 60B is engaged, and the second clutch B-C / L is in the engaged state. In this case, the boosted output of the cam mechanism 63B allows the main clutch 60B to be strongly engaged to transmit a large torque. And On the other hand, when the electromagnetic solenoid 653 is not energized, the sub clutch 6
4B is released, and the second rotating body 62B becomes the first rotating body 61B.
The cam mechanism 63B does not perform a cam operation, the main clutch 60B is released, and the second clutch B-C / L is in the disengaged state. Since the main clutch 60B of the second clutch B-C / L is arranged on the innermost side and has a large torque transmission capacity per area, the other main clutches 60A, 60C, which will be described later,
The plate thickness is thicker than that of 60K.

Next, the first clutch A-C / L, the third clutch C-C / L and the brake BRK will be described. The basic configuration of these is common to the second clutch B-C / L. I will explain it briefly. This first clutch A-C / L is, as described above, the carrier connection circular pipe 34.
Provided between the input circular pipe 32 and the main clutch 60
A, first rotary body 61A, second rotary body 62A, cam mechanism 6
3A, a sub clutch 64A, and a fastening mechanism 65A are provided.

The main clutch 60A is the input circular pipe 3
2 and the carrier connecting circular pipe 34 are alternately arranged so as to be relatively movable in the axial direction and not relatively rotatable.

The first rotating body 61A is mounted on the carrier connecting circular pipe 34 so as to be relatively movable in the axial direction and not relatively rotatable. The second rotating body 62A includes the input circular pipe 32.
Is floatingly supported between the carrier connection circular pipe 34 and the carrier connection circular pipe 34. The cam mechanism 63A includes a second clutch B-C.
Like / L, the thrust roller held by the first rotary body 61A and the cam groove (not shown) formed in the second rotary body 62A are provided.

The sub-clutch 64A includes the second rotating body 6
The 2A circular pipes 622 and the input circular pipes 32 are alternately arranged so as to be relatively movable in the axial direction and non-rotatable. The fastening mechanism 65A includes an armature 651 mounted on the input circular pipe 32 so as to press the sub-clutch 64A, and an electromagnetic solenoid 653 provided in the housing H to attract the armature 651 when energized.

Therefore, when the electromagnetic solenoid 653 of the fastening mechanism 65A is energized, the sub-clutch 64A is engaged, whereby the first rotary body 61A and the second rotary body 62 are engaged.
A relative rotation is generated between A and A, and the cam mechanism 63A outputs a boosted force to engage the main clutch 60A, whereby the input circular pipe 32 and the carrier connecting circular pipe 34 are coupled. When the electromagnetic solenoid 653 of the fastening mechanism 65A is not energized, the sub clutch 64A is released, the main clutch 60A is released, and the coupling between the input circular pipe 32 and the carrier connecting circular pipe 34 is released. It

As described above, the third clutch A-C / L is provided between the input circular pipe 32 and the sun gear connecting circular pipe 36, and has the main clutch 60C, the first rotary body 61C, and
Second rotating body 62C, cam mechanism 63C, sub-clutch 64
C, and a fastening mechanism 65C.

The main clutch 60C is the input circular pipe 3
2 and the sun gear connecting circular pipe 36 are alternately arranged so as to be relatively movable in the axial direction but not relatively rotatable.

The first rotating body 61C is mounted on the input circular pipe 32 so as to be relatively movable in the axial direction and not relatively rotatable. The second rotating body 62C is floatingly supported between the input circular pipe 32 and the sun gear connecting circular pipe 36. The cam mechanism 63C includes a thrust roller held by the first rotating body 61C and a cam groove (not shown) formed in the second rotating body 62C, like the second clutch B-C / L.

The sub-clutch 64C includes the second rotating body 6
The 2C circular pipes 622 and the sun gear connecting circular pipes 36, which are provided so as to be relatively movable in the axial direction and not relatively rotatable, are alternately arranged. The fastening mechanism 65C is
Sun gear connection circular pipe 36 that can press the sub clutch 64C
And an electromagnetic solenoid 653 which is provided in the housing H and attracts the armature 651 when energized.

Therefore, when the electromagnetic solenoid 653 of the engaging mechanism 65C is energized, the sub-clutch 64C is engaged, whereby the first rotary body 61C and the second rotary body 62 are engaged.
Relative rotation occurs with C and the cam mechanism 63C outputs a boosted force to engage the main clutch 60C, whereby the input circular pipe 32 and the sun gear connecting circular pipe 36 are coupled. When the electromagnetic solenoid 653 of the engagement mechanism 65C is not energized, the sub clutch 64C is released, the main clutch 60C is released, and the connection between the input circular pipe 32 and the sun gear connecting circular pipe 36 is released. It

The brake BRK is, as described above,
It is provided between the ring gear connecting circular pipe 38 and the circular pipe 46 of the housing H, and has a main clutch 60K and a first rotating body 61.
K, a second rotary body 62K, a cam mechanism 63K, a sub clutch 64K, and a fastening mechanism 65K.

The main clutches 60K are arranged alternately on the ring gear connecting circular pipe 38 and the circular pipe 46 so as to be relatively movable in the axial direction and non-rotatable relative to each other.

The first rotating body 61K is mounted on the ring gear connecting circular pipe 38 so as to be relatively movable in the axial direction and not relatively rotatable. The second rotary body 62K is floatingly supported between the ring gear connecting circular pipe 38 and the circular pipe 46. The cam mechanism 63K includes a second clutch B-C.
Like / L, it has a thrust roller 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 46, which are provided so as to be relatively movable in the axial direction and not relatively rotatable, are alternately arranged. The fastening mechanism 65K includes an armature 6 mounted on the circular pipe 46 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, when the electromagnetic solenoid 653 of the engaging mechanism 65K is energized, the sub-clutch 64K is engaged, and relative rotation occurs between the first rotating body 61K and the second rotating body 62K to cause the cam mechanism 63K. Outputs a boosted force to engage the main clutch 60K, whereby the ring gear connecting circular pipe 38 and the circular pipe 46 are coupled, and the ring gear connecting circular pipe 38 and the sun gear 11 are fixed to the housing H. Further, the electromagnetic solenoid 653 of the fastening mechanism 65K
Is de-energized, the sub-clutch 64K is disengaged and the main clutch 60K is disengaged.
The coupling between the ring gear connecting circular pipe 38 and the circular pipe 46 is released, the fixing of the ring gear connecting circular pipe 38 is released, and the sun gear 11 becomes free.

In FIG. 1, 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 drawing, 19 is each clutch A-C / L, B-
It is power wiring for supplying power to the electromagnetic solenoids 653 of the C / L, C-C / L and the brake BRK.

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, first
The clutch BR is engaged and the second and third clutches BC / L and CC / L are released, and the brake BR
With K in the engaged state, the generator motor MG is driven as a motor. Therefore, the rotation of the generator motor MG is input to the sun gear 11 and the ring gear 13 is fixed in the planetary gear PGS, so that the rotation is reduced from the carrier 12 and output. Furthermore, the carrier 12
Is transmitted from the first clutch A-C / L to the input circular pipe 32, and the input shaft 1 and the crankshaft 6 rotate,
The engine EG is started. In this case, the generator motor MG
Is increased in the planetary gear PGS and output to the engine EG. Incidentally, the reduction ratio Ns / Nc of the planetary gear PGS can be expressed by Ns / Nc = (ns + nr) / ns (where ns is the number of teeth of the sun gear, nr;
(The number of teeth of the ring gear), in the present embodiment,
The setting is Ns / Nc = 1 / 2.4. Therefore, the drive torque required to start the engine EG in the generator motor MG can be reduced as compared with the case where the reduction ratio is not obtained, and the generator motor MG can be downsized. That is, in the present embodiment, conventionally, the power transmission unit MGU is to be installed in the limited space where the torque converter is installed in the automatic transmission, and therefore, the generator motor MG is arranged outside. Despite the structure, it aims to be as compact as possible as a whole, and in such a structure, reducing the required drive torque of the generator motor MG is very effective in terms of compactness. Becomes

(Start-up / creep / hill-hold) During start-up after starting the engine EG, during creep running in which the accelerator is not stepped on, the vehicle is going uphill or the vehicle speed is 0 km / h. At the time of holding the hill hold, the second clutch B-C / L and the third clutch C-C / L are engaged, and the first clutch A-C / L is engaged.
L is released and the brake BRK is engaged.

Therefore, the rotation of the engine EG is input from the input shaft 1 to the sun gear 11 through the third clutch C-C / L, decelerated from the carrier 12, and the second clutch B-.
It is output to the output shaft 2 via C / L. In this way, the torque is increased in the planetary gear PGS while the driving force of the engine EG is being transmitted from the input shaft 1 to the output shaft 2.
Therefore, it is possible to smoothly start,
Creep and hill hold can also be performed.
At this time, the second clutch B-C / L and the third clutch C-C / L do not generate heat because they are simply engaged and do not slip, and a clutch having no torque converter is used. Despite the structure used, it is possible to start with high torque, creep, and hill hold without causing a large amount of heat generation in the clutch.

Further, in the above-mentioned state, when the generator motor MG is driven as a motor, the drive torque generated in the generator motor MG is combined with the engine torque and the planetary gear PG.
Since the speed is reduced by S and transmitted to the transmission TM, the torque of the engine EG can be assisted. On the other hand, when the generator motor MG is operated as a generator in the above-described state, a part of the drive torque of the engine EG is consumed in the generator motor MG, and the torque input to the transmission TM decreases. in this way,
By operating the generator motor MG as a motor or as a generator, the transmission TM
The torque input to can be increased or decreased, and more detailed control is possible. This control is particularly effective for hill hold.

In addition, as described above, the planetary gear PGS
In this case, since the reduction ratio can be obtained, when only the second clutch B-C / L is engaged and the generator motor MG is driven as an electric motor, the rotation of the generator motor MG is reduced by the planetary gears PGS and the output shaft is reduced. 2 and the transmission TM, and it is possible to perform the start and the creep running with the driving force of only the generator motor MG, and when the battery (not shown) is sufficiently charged, It is also possible to improve fuel efficiency by starting and creeping with the generator motor MG.

(During steady running / acceleration) During steady running and acceleration, all the clutches A-C / L, B-C / L and C-C / L are engaged while the engine EG is being driven. , And m, the brake BRK is released. Therefore, the engine EG rotates from the input shaft 1 to the first clutch A-C / L, the carrier connecting circular pipe 34, and the second clutch B.
It is output to the output shaft 2 via -C / L. In this case, the engine torque is directly output to the output shaft 2,
The reduction ratio is 1: 1.

At this time, the rotation of the input shaft 1 is input to the sun gear connecting circular pipe 36 in the planetary gear PGS via the third clutch C-C / L, and the rotor 16 of the generator motor MG rotates. , Can generate electricity. Alternatively, if the generator motor MG is driven as a motor, the drive torque is input to the input shaft 1. Therefore, when torque is required during acceleration, the motor may be driven as such. During the above-described steady running / acceleration, in the planetary gear PGS, the rotation of the input shaft 1 is input to the sun gear 11 via the third clutch C-C / L, and at the same time, the first clutch A-C / Although it is input to the carrier 12 via L, the ring gear 13 is in a free state due to the release of the brake BRK, and thus is in a rotating state.

(Deceleration Regeneration) When performing regeneration during deceleration, the drive of the engine EG is stopped or idle rotated to obtain the regenerative braking force associated with the charging of the generator motor MG, and the engine EG is rotated to apply engine braking. There is a case where the regenerative braking force is obtained at the same time as it is obtained. In the present embodiment, basically, the former is performed during low speed traveling, and the latter is performed during middle / high speed traveling.

When the engine EG is stopped or idled to perform regeneration, the second clutch B-C / L is engaged and the first clutch A-C / L and the third clutch C are engaged.
-C / L is released and brake BRK is engaged. Therefore, the disengagement of the first clutch A-C / L and the third clutch C-C / L completely disconnects the planetary gear PGS from the input shaft 1, and in this state, input from the drive wheel to the output shaft 2 is performed. The generated torque is the second clutch B-C / L.
It is input to the carrier 12 via and is output from the sun gear 11 at an increased speed. Therefore, the sun gear connecting circular pipe 36
The rotor 16 mounted on the circular pipe 36c connected to is rotated at an increased speed (2.4 times) to generate electric power in the generator motor MG. As described above, the generator motor MG is rotated three times and rotated to generate electric power, so that high power generation efficiency can be obtained. Also, in this case, a small braking force only by the regenerative power generation of the generator motor MG can be obtained.

On the other hand, when regenerating the engine EG together with rotation, all the clutches A-C / L, B-C /
L, C-C / L is fastened and the brake BRK
Let go. In this case, the torque on the drive wheel side input to the output shaft 2 is input to the carrier 12 via the second clutch B-C / L and further to the engine EG via the first clutch A-C / L. The so-called engine brake can be obtained by being transmitted and rotating the engine EG, and the rotation of the input shaft 1 is the third clutch C-C.
Is input to the sun gear connecting circular pipe 36 via / L, and power is generated in the generator motor MG. At this time, by releasing the brake BRK, the planetary gear PG
In S, no shift operation is performed.

As described above, the first embodiment
Then, without using the torque converter, the planetary gear P
GS and each clutch A-C / L, B-C / L, C-C
Since torque is transmitted using / L, the torque transmission efficiency is excellent. Moreover, since the planetary gear PGS and the clutches A-C / L, B-C / L, and C-C / L are used as described above, the planetary gear PGS is decelerated to transmit torque. It is possible to achieve low-speed / high-torque output without using a heat-generating means such as slipping the clutch. Therefore, in the first embodiment applied to the vehicle, it is possible to perform start / creep running and hill hold.

Further, in the first embodiment, all clutches AC / L, BC / L, CC / L, brake BRK, generator motor MG, input shaft 1 and output shaft 2 are provided. Since it is configured to have five layers around the
The axial dimension of the unit can be reduced, and the engine E
It is advantageous to be installed between the G and the transmission TM and is excellent in vehicle mountability. In addition, the first embodiment
Has a configuration in which the engine EG is started by the generator motor MG, but at the time of starting, it is possible to reduce the speed of the planetary gears PGS and transmit the torque of the generator motor MG to the engine EG, so that the generator motor MG can be downsized. it can. In particular, in the first embodiment, the generator motor MG
Is provided at the outermost periphery of the unit, and in this structure, if a large output torque is required for the generator motor MG, the outer dimensions increase, which leads to an increase in size and weight, but this can be suppressed.

(Other Embodiments) Other embodiments will be described below. However, the same components as those already described are denoted by the same reference numerals, and the description thereof will be omitted. The difference will be described.

(Second Embodiment) FIG. 7 is a sectional view of a power transmission unit MGU2 of the second embodiment. The difference from the first embodiment is that the second clutch B-C / L is in the axial direction. The orientation is opposite to that of the first embodiment. That is, the disc 201 which is the stopper surface of the main clutch 60A is coupled to the inner periphery of the left end of the carrier connection circular pipe 234 in the figure, and the inner periphery of the other end is formed of a non-magnetic material to the electromagnetic solenoid 653. The magnetic path forming ring 202, which forms a magnetic path around the armature 651 when energized, is coupled. Then, from the side of the disk 201, the main clutch 6
0A, a first rotary body 61A, a cam mechanism 63A, a second rotary body 62A, a sub clutch 64A, and a fastening mechanism 65A are provided.

Further, on the inner circumference of the disk 43 of the housing H,
An electromagnetic solenoid 653 of the fastening mechanism 65A is provided. Further, thrust rollers 204 and 205 that support the carrier connecting circular pipe 234 in the axial direction are provided between the thrust rollers 204 and 205 and the housing H. Further, a thrust roller 206 for axially supporting the sun gear connecting circular pipe 36 between the disc 36b and the housing H is provided.

In the second embodiment, the other structure is the same as that of the first embodiment, and the description thereof will be omitted. Further, the operation and effect are also the same as those in the first embodiment, and therefore the description thereof will be omitted.

(Third Embodiment) FIG. 8 is a sectional view of a power transmission unit MGU3 according to a third embodiment. The third embodiment is a modified example of the second embodiment, and
The third embodiment corresponds to the invention described in 3, 5 and is characterized in that a band brake is used as the brake BRK.

The difference from the first and second embodiments will be described. In the third embodiment, the ring gear connecting circular pipe 33 is provided.
8 is provided only in a portion of the planetary gear PGS in the outer diameter direction. The sun gear connection circular pipe 36 is not provided with the disc 36b and the circular pipe 36c shown in the first and second embodiments, and the outer periphery of the sun gear connection circular pipe 36 is directly supported by the bearings 53, 53, At the position sandwiched by the seal members 55, 55 on the inner periphery thereof, the generator motor MG
The rotor 16 is mounted on the outer circumference of the sun gear connecting circular pipe 36.

As shown in FIG. 9, the brake BRK is provided with a brake shoe 24 provided on the outer circumference of the ring gear connecting circular pipe 338 and a brake band 25 mounted so as to face the brake shoe 24. There is. Furthermore, this brake band 25 has springs 2 at both ends.
6, 27 is biased in the fastening direction, while one end of the brake band 25 is movable by the hydraulic actuator 28 in the direction opposite to the biasing force of the spring 26. That is, the brake BRK is provided with the springs 26, 2 when the hydraulic actuator 28 is not operating.
The ring gear connecting circular pipe 338 is fastened by the urging force of 7.
Is fixed and the hydraulic actuator 28 is actuated, the fastening is released and the ring gear connecting circular pipe 338 is released from the fixation and becomes rotatable. The hydraulic actuator 28
Is, for example, ON / O as shown in the operation explanatory diagram of FIG.
It is preferable that the brake BRK is released by operating at a predetermined vehicle speed or higher according to the vehicle speed so that FF switching is performed.

In the third embodiment, the brake BRK
As a band brake having a shorter dimension in the radial direction and the axial direction than the multi-disc brake, the power transmission unit MGU is arranged side by side with the generator motor MG in the axial direction.
The radial dimension in Embodiment 1 and Embodiment 2
It is possible to make the size smaller and to make it compact and further improve the vehicle mountability. In addition, other actions
The effect is the same as that of the first embodiment, and therefore the description is omitted.

(Embodiment 4) Embodiment 4 corresponds to the invention described in claims 1 to 3 and is an example in which a centrifugal brake is used as the brake BRK. Figure 10
FIG. 4 is a cross-sectional view showing a power transmission unit MGU4 of Embodiment 4, and the difference from Embodiment 1 will be described based on this drawing. This brake BRK is a circular pipe connected to a sun gear connecting circular pipe 36. 36c and a ring gear connecting circular pipe 38 are alternately coupled axially movable and immovably in a rotational direction, and a multi-plate clutch 400, and the multi-plate clutch 400 can be pressed via a thrust roller 406 to connect a ring gear. The first rotary body 401 is provided between the first rotary body 401 that is movably coupled to the circular pipe 38 in the axial direction and the second rotary body 402 that is opposed to the first rotary body 401 and floats. A spring 403 that urges in the direction of the multi-plate clutch 400 and a circular pipe 36c that can be oscillated in the radial direction and is urged to oscillate in the inner diameter direction by a spring 407. When the rotation speed of 36c increases, the arm 408 supporting the second rotating body 402 swings in the outer diameter direction against the urging force of the spring 407 by the centrifugal force, and the mass body 405 that moves leftward in the drawing. I have it.

Therefore, according to the fourth embodiment, when the rotation speed of the circular pipe 36c is lower than a predetermined speed or at a low speed, the brake BRK causes the mass body 405 to contact the ring gear connection circular pipe 38 and to prevent the spring. The first rotating body 401 pushes the multi-plate clutch 400 by the urging force of 403 and is fastened. On the other hand, when the vehicle speed is higher than a predetermined value, the mass body 405 is
Moves in the outer diameter direction against the urging force of the spring 407, whereby the arm 408 moves leftward in the drawing, and the second rotating body 402 supporting one end of the spring 403 moves away from the first rotating body 401. Therefore, the first rotating body 40
The pressing force of 1 to press the multi-plate clutch 400 is reduced and released. That is, the same effect as that shown in the operation explanatory view of FIG. 6 can be obtained. Regarding other actions and effects,
Since it is the same as the fourth embodiment, the description thereof is omitted.

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 can be made. Even if it exists, it is included in the present invention.

[Brief description of drawings]

FIG. 1 is a cross-sectional view showing a power transmission unit MGU according to a first embodiment.

FIG. 2 is a skeleton diagram showing the power transmission unit MGU according to the first embodiment.

FIG. 3 is a cross-sectional view showing the main parts of the first embodiment.

FIG. 4 is a cross-sectional view showing the main parts of the first embodiment.

FIG. 5 is an operation explanatory view of a main part of the first embodiment.

FIG. 6 is an operating characteristic diagram of the first embodiment.

FIG. 7 is a sectional view showing a power transmission unit MGU2 according to a second embodiment.

FIG. 8 is a sectional view showing a power transmission unit MGU3 according to a third embodiment.

FIG. 9 is a sectional view showing a brake (band brake) according to a third embodiment.

FIG. 10 is a sectional view showing a power transmission unit MGU4 according to a fourth embodiment.

[Explanation of symbols]

1 input axis 2s stopper surface 2 output shaft 5 Vibration absorption means 6 crankshaft 11 sun gear 12 career 13 ring gear 16 rotor 24 brake shoes 25 Brake Band 26,27 spring 28 Hydraulic actuator 31 Magnetic path forming ring 32 input tube 32b disc 34 Carrier connection circular pipe 36 Sun gear connection circular pipe 36b disc 36c circular tube 38 Ring gear connection circular pipe 41, 42, 43 disks 45,46 circular tube 47 Connecting member 48 air cooled fins 49 bearings 50 seal member 51,52 Thrust roller 53 bearings 55 Seal member 60A main clutch 60B main clutch 60C main clutch 60K main clutch 61A 1st rotating body 61B 1st rotating body 61C 1st rotating body 61K 1st rotating body 62A Second rotating body 62B Second rotating body 62C Second rotating body 62K 2nd rotating body 63A cam mechanism 63B cam mechanism 63C cam mechanism 63K cam mechanism 64A sub clutch 64B sub clutch 64C sub clutch 64K sub clutch 65A fastening mechanism 65B fastening mechanism 65C fastening mechanism 65K fastening mechanism 201 disk 202 Magnetic path forming ring 204,205,206 Thrust roller 234 Carrier connection circular pipe 338 Ring gear connection circular pipe 400 multi-plate clutch 401 rotating body 402 rotating body 403 spring 405 mass 406 Thrust roller 407 spring 408 arm AC / L first clutch B-C / L second clutch C-C / L third clutch AR air chamber OR oil chamber PGS planetary gear BRK brake EG engine MG generator motor MGU Electric generator unit TM transmission H housing

─────────────────────────────────────────────────── ─── Continuation of front page (51) Int.Cl. ⁷ Identification code FI theme code (reference) H02K 7/18 H02K 7/18 BF term (reference) 3D039 AA01 AA02 AA03 AA04 AB01 AC03 AC14 AC15 AC21 AC33 AD06 AD11 AD53 3J058 AA03 AA13 AA17 AA18 AA24 AA28 AA37 AA59 AA78 AA79 AA87 BA67 CB03 CB13 CC03 CC06 CC13 CC52 CC66 CC76 FA01 5H607 AA00 BB01 BB02 CC03 DD03 DD17 EE02 EE06 EE33 FF22 FF24

Claims (6)

[Claims] 1. An input shaft provided in a torque transmission path between an engine and a transmission for transmitting torque from the engine, and an output shaft provided coaxially with the input shaft for outputting torque to the transmission. A planetary gear that is provided coaxially with the input shaft and the output shaft and transmits rotation between the input shaft and the output shaft; a first clutch provided between the carrier of the planetary gear and the drive shaft; A second clutch provided between the carrier and the output shaft; a third clutch provided between the sun gear of the planetary gear and the drive shaft; a brake that fixes the ring gear of the planetary gear to the housing; A generator motor that is provided between the rotating body that rotates integrally with the sun gear and the housing, can rotate the rotating body as a motor, and can generate electric power by rotating the rotating body. An input circular pipe (32) coupled to the input shaft (1) is provided with a space in the outer diameter direction of the output shaft (2), and the input circular pipe (32) and the output shaft (2) are provided. ), A carrier connection circular pipe (34) coupled to the carrier is provided with a space between the input circular pipe (32) and the output shaft (2). A sun gear connecting circular pipe (36) as at least a part of the rotating body coupled to the sun gear is provided with a space in the outer diameter direction of (32), and is directly connected to the sun gear connecting circular pipe (36). Alternatively, indirectly, the rotor (16) of the generator motor (MG) is attached, and the second clutch (B-C / L) is provided between the output shaft (2) and the carrier connecting circular pipe (34). The output shaft (2) and the carrier connecting circular pipe (34) are provided so that they can be fastened and fastened. A first clutch (A / C / L) connects the carrier connecting circular pipe (34) and the input circular pipe (32) between the carrier connecting circular pipe (34) and the input circular pipe (32), and A third clutch (C-C / L) is provided between the input circular pipe (32) and the sun gear connecting circular pipe (36) so as to be able to release the engagement, and the input circular pipe (32) is provided.
And a sun gear connection circular pipe (36) are provided so that they can be fastened and fastened together. 2. The planetary gear is arranged on the outer diameter side of the carrier connecting circular pipe (34) and axially aligned with the first clutch and the third clutch. The power transmission unit according to Item 1. 3. A generator motor (M) provided at the outermost periphery.
The sun gear connecting circular pipe (36) or the sun gear connecting circular pipe (36) arranged between the air chamber (AR) housing G) and the oil chamber (OR) housing the clutch and brake. The outer periphery of the integral rotating member (36c) is supported by the housing via a pair of bearings (53), and an oil chamber (OR) and an air chamber (A) are provided next to the bearings (53).
The power transmission unit according to claim 1 or 2, further comprising a seal member (55) that separates R). 4. A circular pipe (4) which is integral with the housing and has a space in the outer diameter direction of the ring gear connecting circular pipe (38).
6) is provided, and the sun gear connecting circular pipe (3) is provided on the outer diameter side of the circular pipe (46).
A circular pipe (36c) coupled to 6) is provided, the rotor (16) is attached to the circular pipe (36c), and the circular pipe (46) and the ring gear connecting circular pipe (38) are used as the brakes. The power transmission unit according to any one of claims 1 to 3, wherein an electromagnetic multi-plate brake having a multi-plate main clutch (60K) mounted on is used. 5. A circular pipe (4) which is integral with the housing and has a space in the outer diameter direction of the ring gear connecting circular pipe (38).
6) is provided, and the sun gear connecting circular pipe (3) is provided on the outer diameter side of the circular pipe (46).
6) is provided with a circular pipe (36c), the rotor (16) is attached to the circular pipe (36c), and the circular pipe (46) and the ring gear connecting circular pipe (38) are used as the brakes. It has a multi-plate main clutch (400) mounted on the main body and a mass body (405) supported by a circular pipe (36c). Release the clutch, while
The power transmission unit according to claim 1, wherein a centrifugal brake that engages a main clutch when the rotation speed of the circular pipe (36c) exceeds a predetermined speed is used. 6. A rotor (1) of the generator motor (MG).
6) is attached to the outer circumference of the sun gear connecting circular pipe (36), and a band brake capable of fixing and releasing the disc (338) attached to the outside of the sun gear is used as the brake. The power transmission unit according to claim 1, wherein the power transmission unit is provided side by side with the electric motor (MG) in the axial direction.