JPH09217811A - Power transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce the size of an output gear by a method wherein a switching mechanism and an operation system are simplified through direct engagement between a transmission gear arranged on the outer periphery of a ring gear of which a planetary gear mechanism consists and the output gear of an output shaft. SOLUTION: A power transmission device comprises a continuously variable shift mechanism 3 having a friction roller 13 arranged in toroidal grooves 11a and 12a formed in an input disc 11, to which rotation of an engine E is transmitted through an input shaft 2, and an output disc 12, respectively; an axle shaft A arranged in parallel to the inlet shaft 2; and a planetary gear mechanism 4 to transmit rotation of the output disc 12 to the axle shaft A. Further, the power transmission device comprises a switching mechanism 5 formed in such a manner that the output disc 12 is coupled to a sun gear 15, a transmission gear 18 is arranged on the outer periphery of the ring gear 17, a transmission gear 18 is engaged with the output gear 6 of the axle shaft A, and the rotation direction of the axle shaft A is changed in coordination with a planetary gear 16.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a power transmission device equipped with a toroidal type continuously variable transmission mechanism, and more particularly, in an FF type (front engine / front drive type) automobile, the rotation of the engine is changed to an axle shaft. The present invention relates to a power transmission device suitable for transmission.

[0002]

2. Description of the Related Art A power transmission device of this type is shown in FIG. In the illustrated power transmission device 100, the rotation of the engine 101 is transmitted to a continuously variable transmission mechanism 103 by an input shaft 102, and the rotation output from the continuously variable transmission mechanism 103 is transmitted by a planetary gear mechanism 104 to an axle shaft 105 which is an output shaft. Communicate to. Axle shaft 10
5, an output gear 106 and a differential mechanism 107 are provided.

The continuously variable transmission mechanism 103 transmits the rotation of the input shaft 102 to the input disk 110 by the loading cam 108 and the cam roller 109. Input disk 11
0 and the output disk 111 facing this are formed with toroidal grooves 110a and 111a.
A plurality of friction rollers 112 are provided in a and 111a. The continuously variable transmission mechanism 103 changes the effective diameters of both disks 110 and 111 according to the angle of the friction roller 112,
Thereby, the gear ratio is changed steplessly.

The planetary gear mechanism 104 includes an output disk 11
1, a sun gear 114 connected to the No. 1 via a transmission shaft 113,
A plurality of planetary gears 115 and a ring gear 116 are provided. Also. A transmission gear 117 that engages with the output gear 106 of the axle shaft 105 is provided on one side of the planetary gear mechanism 104.

Further, the power transmission device 100 described above has the ring gear 11 in order to switch between forward and backward movement and to obtain a neutral state.
The first clutch C1 for restraining / releasing the rotation of No. 6, the second clutch C2 for restraining / releasing the rotation of the carrier 118 which supports each planetary gear 115, and the restraint / release between the ring gear 116 and the transmission gear 117. 3rd clutch C
3 between the carrier 118 and the transmission gear 117
A fourth clutch C4 for releasing is provided. Then, for example, by making the first and fourth clutches C1 and C4 in a restrained state, the axle shaft 105 is rotated forward,
By setting the second and third clutches C2 and C3 in the restrained state, the axle shaft 105 is rotated in the reverse direction, and by releasing all the clutches C1 to C4, the neutral state is obtained.

As such a power transmission device, for example, a device similar to the one disclosed in Japanese Patent Laid-Open No. 61-99760 is described.

[0007]

However, in the conventional power transmission device as described above, the sun gear 11 is provided between the input shaft 102 and the axle shaft (output shaft) 105.
4, a planetary gear mechanism 104 composed of a planetary gear 115 and a ring gear 116, and an independent output gear 11
Since 7 is provided, the output gear 106 is increased in size for the purpose of obtaining a predetermined reduction ratio, and four clutches C1 to C4 are required to obtain the forward and reverse and neutral states, and the operating system of the switching mechanism. However, the conventional structure described above causes torque fluctuation due to the gear ratio and requires a computer for fail-safe control. There is a problem of high cost, and it has been a problem to solve these problems.

[0008]

SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned conventional problems, and an object of the present invention is to provide a power transmission device which can reduce the occupied space and the cost.

[0009]

According to a first aspect of the present invention, there is provided a power transmission device including a toroid formed on an input disk to which rotation of a power source is transmitted via an input shaft and an output disk facing the input disk. A continuously variable transmission mechanism having a plurality of friction rollers provided in a groove, an output shaft arranged in parallel with the input shaft and having an output gear, and a planetary gear mechanism transmitting the rotation of the output disc to the output shaft. , The output disc is connected to the sun gear of the planetary gear mechanism, a transmission gear is provided on the outer periphery of the ring gear of the planetary gear mechanism, and the transmission gear and the output gear of the output shaft are engaged to form a planetary gear of the planetary gear mechanism. The configuration is provided with a switching mechanism that changes the rotation direction of the output shaft in cooperation with the gear, and the above configuration is a means for solving the problems.

According to another aspect of the present invention, there is provided a power transmission device.
As a switching mechanism, the switching mechanism includes a carrier that supports the planetary gear, a second transmission gear that is provided on the carrier, a second output gear that is provided on the output shaft and that engages with the second transmission gear, and a second transmission gear.
The first clutch for restraining / releasing the rotation of the transmission gear and the second clutch for restraining / releasing the output shaft and the second output gear are provided. As a means.

According to another aspect of the present invention, there is provided a power transmission device.
The planetary gear mechanism includes a first sun gear, an inner planetary gear that is supported at a constant position and engages with the first sun gear, and an outer planetary gear mechanism that is also supported at a constant position and engages with an inner planetary gear and a ring gear. A planetary gear is provided, and the switching mechanism includes a second sun gear that engages with the outer planetary gear, a first clutch that restrains and releases between the output disc and the first sun gear, and a restraint between the output disc and the second sun gear. The second clutch to be released is provided, and the above configuration is used as means for solving the problem.

[0012]

In the power transmission device according to the first aspect of the present invention, the rotation of the power source is transmitted to the output shaft via the input shaft, the continuously variable transmission mechanism and the planetary gear mechanism, and at this time, the continuously variable transmission mechanism. The rotation output from is transmitted to the sun gear of the planetary gear mechanism, and the rotation output from the planetary gear mechanism is transmitted by the transmission gear provided on the outer periphery of the ring gear and the output gear engaged with this. When the rotation at this time is the forward direction, the reverse rotation and the neutral state of the output shaft are obtained by the switching mechanism that changes the rotation direction of the output shaft in cooperation with the planetary gear of the planetary gear mechanism.

In the power transmission device according to the first aspect of the present invention, the transmission gear provided on the outer periphery of the ring rear constituting the planetary gear mechanism and the output gear of the output shaft are directly engaged with each other. It is not necessary to provide gears and clutches, and the operating system of the switching mechanism can be simplified.

In the power transmission device according to the second aspect of the present invention, when the first clutch is in the released state and the second clutch is in the locked state, the rotation of the power source causes the input shaft, the continuously variable transmission mechanism, the sun gear, and the planetary gear to rotate. It is transmitted to the output shaft via the gear, the carrier, the second transmission gear, and the second output gear to rotate the output shaft. At this time, since the ring gear is not restrained at all, it does not hinder the rotation of the first output gear engaged with the first transmission gear on the outer circumference thereof.

When the first clutch is in the restrained state and the second clutch is in the released state, the rotations of the second transmission gear and the carrier and the revolution of the planetary gear are restrained, and the rotation of the power source is infinitely variable. It is transmitted to the output shaft via the speed change mechanism, the sun gear, the planetary gear, the ring gear, the first transmission gear and the first output gear, and the output shaft is rotated in the reverse direction.

Further, when the first and second clutches are released, the rotation of the input shaft is transmitted to the output shaft via the sun gear, planetary gear, ring gear, first transmission gear and first output gear. However, since the ring gear is fixed by the load on the output shaft side, the planetary gear revolves in response to this, and the output shaft is in a neutral state in which rotation is not transmitted.

As described above, in the power transmission device according to the second aspect of the present invention, switching between the two clutches causes switching between forward and reverse and neutral.

In the power transmission device according to the third aspect of the present invention, when the first clutch is in the locked state and the second clutch is in the released state, the rotation of the power source causes the input shaft, the continuously variable transmission mechanism, and the first sun gear to rotate. Is transmitted to the output shaft via the internal and external planetary gears, the ring gear, the transmission gear, and the output gear to rotate the output shaft.

When the first clutch is in the released state and the second clutch is in the locked state, the rotation of the power source rotates the input shaft, the continuously variable transmission mechanism, the second sun gear, the outer planetary gear, the ring gear, the transmission gear and It is transmitted to the output shaft via the output gear and rotates the output shaft in the reverse direction.

Further, when the first and second clutches are released, the rotation of the continuously variable transmission mechanism is not transmitted to either the first or second sun gear, so that rotation is not transmitted to the output shaft. It becomes a state.

As described above, in the power transmission device according to the third aspect, switching between the two clutches enables switching between forward and reverse and neutral.

[0022]

According to the power transmission device of the first aspect of the present invention, the transmission gear provided on the outer periphery of the ring rear constituting the planetary gear mechanism and the output gear of the output shaft are directly engaged. , It is not necessary to provide another gear or clutch between them, the switching mechanism and the operating system can be simplified correspondingly, and the output gear can be downsized, so that the entire occupied space can be reduced. For example, it is extremely advantageous when it is mounted on the vehicle body as a power transmission device of an automobile. In addition to this, forward and reverse and neutral states are obtained, and torque fluctuation due to the gear ratio is small, so that it is a fail safe. Can be controlled easily, and cost reduction can be realized as a complicated control device becomes unnecessary.

According to the power transmission device of the second aspect of the present invention, the same effect as that of the first aspect can be obtained, and particularly, the forward and backward movement and the neutral state can be obtained by switching the two clutches. Therefore, the operating system of the switching mechanism can be greatly simplified as compared with the conventional one, and thereby the entire occupied space can be reduced.

According to the power transmission device of the third aspect of the present invention, the same effects as those of the first and second aspects can be obtained. Particularly, in the present invention, the second sun gear is the switching mechanism. Since the second sun gear is included in the planetary gear mechanism, the structure can be further simplified, and the structure on the output shaft side can be further simplified or the shaft length can be shortened as compared with the second aspect. Can be planned.

[0025]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 is a diagram for explaining an embodiment of a power transmission device according to claims 1 and 2 of the present invention. The illustrated power transmission device 1 is provided with a toroidal type continuously variable transmission mechanism, and has an FF type (front engine
A front drive type vehicle equipped with an axle shaft A that outputs the rotation of an engine E that is a power source.
To communicate.

The power transmission device 1 transmits the rotation of the engine E to the continuously variable transmission mechanism 3 through the input shaft 2, and the continuously variable transmission mechanism 3
The rotation output from the planetary gear mechanism 4 and the switching mechanism 5
Is transmitted to the axle shaft A via. The axle shaft A is arranged in parallel with the input shaft 2 and includes first and second output gears 6, 7 and a differential mechanism 8.

The continuously variable transmission mechanism 3 transmits the rotation of the input shaft 2 to the input disk 11 by the loading cam 9 and the cam roller 10. Toroidal grooves 11a and 12a are formed in the input disk 11 and the output disk 12 facing the input disk 11, and a plurality of friction rollers 13 are provided in both grooves 11a and 12a. The continuously variable transmission mechanism 3 changes the effective diameters of both the disks 11 and 12 according to the angle of the friction roller 13, thereby changing the speed ratio steplessly.

The continuously variable transmission 3 shown in the figure has the input disk 1 on the side opposite to the engine E with respect to the output disk 12.
1, the transmission shaft 14 having the input shaft 11 inserted through the shaft center is connected to the output disk 12, and the input shaft 11 is input from the engine side and output to the engine side. Therefore, the planetary gear mechanism 4 and the switching mechanism 5 are arranged between the engine E and the continuously variable transmission mechanism 3.

The planetary gear mechanism 4 is provided with a sun gear 15 connected to the output disk 12 via a transmission shaft 14, a plurality of planetary gears 16, and a ring gear 17. The outer periphery of the ring gear 17 has an axle shaft. A first transmission gear 18 that engages with the A first output gear 6 is provided.

A second transmission gear 19 that engages with the second output gear 7 of the axle shaft A is provided on the side of the continuously variable transmission 3 of the planetary gear mechanism 4. It is connected to a carrier 20 that supports the planetary gears 16. Further, a first clutch C1 for restraining / releasing the rotation of the second transmission gear 19 is provided on the device case side (not shown).
And a second clutch C2 for restraining / releasing the space between the second output gear 7 and the axle shaft A.

That is, in this embodiment, the carrier 20,
By the second transmission gear 19, the second output gear 7, and the first and second clutches C1 and C2, the rotation direction of the axle shaft (output shaft) A is changed in cooperation with the planetary gear 16 of the planetary gear mechanism 4. The switching mechanism 5 is configured.

In the power transmission device 1 described above, when the first clutch C1 is released and the second clutch C2 is locked while the engine E is rotating, the engine E is rotated by the input shaft 2 and the continuously variable transmission. It is transmitted to the axle shaft A via the mechanism 3, the transmission shaft 14, the sun gear 15, the planetary gear 16, the carrier 20, the second transmission gear 19 and the second output gear 7, and causes the axle shaft A to rotate forward.
At this time, the planetary gears 16 rotate and revolve. Further, since the ring gear 17 is not restrained at all, it does not hinder the rotation of the first output gear 6 engaged with the first transmission gear 18 on the outer periphery thereof.

Next, when the first clutch C1 is in the restrained state and the second clutch C2 is in the released state, the rotation of the second transmission gear 19 and the carrier 20 and the revolution of the planetary gear 16 are restrained, and the rotation of the engine E is prevented. , Input shaft 2, continuously variable transmission mechanism 3, transmission shaft 14, sun gear 15, planetary gear 16, ring gear 17, first transmission gear 18, and first
It is transmitted to the axle shaft A via the output gear 6, and the axle shaft A is rotated in the reverse direction.

Furthermore, the first and second clutches C1,
When C2 is released, the rotation of the input shaft 2 causes the sun gear 15, the planetary gear 16, the ring gear 17, and the first transmission gear 18 to rotate.
And the state of being transmitted to the axle shaft A via the first output gear 6, but the load on the output shaft side, that is, the axle shaft A does not rotate due to the contact between the tire and the ground, and thus the ring Since the gear 17 is in a fixed state, the axle shaft A is in a neutral state in which rotation is not transmitted.

Thus, in the above power transmission device 1,
By switching between the two clutches C1 and C2, switching between forward and reverse and neutral is performed, so that the switching operation system is simplified. Further, since a large reduction ratio of about 5 can be obtained only with the planetary gear mechanism, it is not necessary to reduce the speed with the output gears 6 and 7, the output gears 6 and 7 can be downsized, and torque fluctuations due to the gear ratio can be achieved. It is easy to perform fail-safe control because there are few, and complicated control equipment is not required, which can realize cost reduction.

In the above structure, when the radius of the sun gear 15 is 20 mm and the radius of the ring gear 17 is 80 mm, the first transmission gear / the first output gear = 1, the second transmission gear /
At the gear ratio of the second output gear = 9/5, on the forward rotation side, when the sun gear θ1 = 5, the carrier θ2 = 9/5, and the ring gear θ3 = 1, (1/4 · θ1) − (5/4 / Θ
The formula of 2) + (θ3) = 0 holds. Therefore, the first and second output gears 6 and 7 can rotate at the same rotation speed, and the reduction ratio at this time is 5. Further, on the reverse rotation side, a reduction ratio -4 is obtained by-(80/20).

FIG. 2 is a diagram for explaining an embodiment of a power transmission device according to claims 1 and 3 of the present invention. In addition,
The same components as those in the previous embodiment are designated by the same reference numerals and detailed description thereof will be omitted.

The power transmission device 31 transmits the rotation of the engine E to the continuously variable transmission mechanism 3 via the input shaft 2, and the rotation output from the continuously variable transmission mechanism 3 via the planetary gear mechanism 34 and the switching mechanism 35. Transmit to shaft A. The axle shaft A is arranged in parallel with the input shaft 2 and includes an output gear 36 and a differential mechanism 8.

The planetary gear mechanism 34 uses a Ravigneaux type planetary gear mechanism and is supported by a first sun gear 45 connected to the transmission shaft 14 from the output disk 12 and a first sun gear. A plurality of inner planetary gears 46 that engage with 45, as well as the individual inner planetary gears 46 and ring gears 1 that are also supported in fixed positions.
7, a plurality of outer planetary gears 56 that engage with 7 are provided, and a transmission gear 38 that engages with the output gear 36 is provided on the outer periphery of the ring gear 17.

Further, the planetary gear mechanism 34 is provided with a second sun gear 55 which engages with the outer planetary gear 56, and the transmission shaft 14 restrains / releases between the output disk 12 and the first sun gear 45. A first clutch C11 for
A second clutch C12 for restraining / releasing between the output disk 12 and the second sun gear 55 is provided, and in this embodiment, the second sun gear 55, the first and second clutches C1.
1 and C12 form a switching mechanism 35 that changes the rotational direction of the axle shaft A in cooperation with the planetary gear (46) of the planetary gear mechanism 34.

In the power transmission device 31 described above, when the first clutch C11 is in the restrained state and the second clutch C12 is in the released state, the rotation of the engine E is the rotation of the input shaft 2, the continuously variable transmission mechanism 3, the transmission shaft 14, First sun gear 45, planetary gears 46 and 56 inside and outside, ring gear 17, transmission gear 38
And is transmitted to the axle shaft A via the output gear 36 to rotate the axle shaft A forward.

When the first clutch C11 is in the released state and the second clutch C12 is in the locked state, the rotation of the engine E is caused by the input shaft 2, the continuously variable transmission mechanism 3, the transmission shaft 14,
It is transmitted to the axle shaft A via the second sun gear 55, the outer planetary gear 56, the ring gear 17, the transmission gear 38, and the output gear 36 to rotate the axle shaft A in the reverse direction.

Further, the first and second clutches C1
When C1 and C12 are released, the rotation of the continuously variable transmission mechanism 3 is not transmitted to the first and second sun gears 45 and 55, so that the axle shaft A is in a neutral state where rotation is not transmitted.

As described above, in the power transmission device 31 described above, it is possible to obtain the same operation and effect as those of the previous embodiment. Further, the second sun gear 55 is used as the switching mechanism 35, but since the second sun gear 55 is substantially included in the planetary gear mechanism 34, the structure can be further simplified and the above-described embodiment can be used. Since the number of the output gears 36 is one as compared with the above, it is possible to further simplify the structure on the side of the axle shaft A or shorten the axial length.

In the above structure, the radius of the first sun gear 45 is 20 mm and the radius of the second sun gear 55 is 25 mm.
When the radius of the ring gear 17 is 100 mm, the gear ratio of transmission gear / output gear = 1, on the forward rotation side, ring gear radius / first sun gear radius = 100/20.
And the reduction ratio is 5. On the reverse rotation side, − (ring gear radius / first sun gear radius) = − (1
00/25), and a reduction ratio of -4 is obtained.

[Brief description of drawings]

FIG. 1 is a diagram illustrating an embodiment of a power transmission device according to claims 1 and 2 of the present invention.

FIG. 2 is a diagram illustrating an embodiment of a power transmission device according to claims 1 and 3 of the present invention.

FIG. 3 is a diagram illustrating a conventional power transmission device.

[Explanation of symbols]

 A Axle shaft (output shaft) C1 C11 1st clutch (switching mechanism) C2 C12 2nd clutch (switching mechanism) E Engine (power source) 1 31 Power transmission device 2 Input shaft 3 Continuously variable transmission mechanism 4 34 Planetary gear mechanism 5 35 switching mechanism 6 1st output gear 7 2nd output gear (switching mechanism) 11 input disc 11a 12a groove 12 output disc 13 friction roller 15 sun gear (planetary gear mechanism) 16 planetary gear (planetary gear mechanism) 17 ring gear (planetary gear) 18) First transmission gear 19 Second transmission gear (switching mechanism) 20 Carrier (switching mechanism) 36 Output gear 38 Transmission gear 45 First sun gear (planetary gear mechanism) 46 Inner planetary gear (planetary gear mechanism) 55 Second sun gear (Switching mechanism) 56 Outer planetary gear (planetary gear mechanism)

Claims (3)

[Claims] 1. A continuously variable transmission mechanism in which a plurality of friction rollers are provided in a toroidal groove formed in an input disk to which rotation of a power source is transmitted via an input shaft and an output disk facing the input disk, An output shaft arranged in parallel with the input shaft and provided with an output gear, and a planetary gear mechanism for transmitting the rotation of the output disc to the output shaft are connected to the sun gear of the planetary gear mechanism. A transmission gear is provided on the outer circumference of the ring gear, and a switching mechanism that engages the transmission gear with the output gear of the output shaft and changes the rotation direction of the output shaft in cooperation with the planetary gear of the planetary gear mechanism is provided. A power transmission device characterized by the above. 2. A switching mechanism, a carrier supporting a planetary gear, a second transmission gear provided on the carrier, a second output gear provided on the output shaft and engaging with the second transmission gear, and a second transmission. A first clutch that restrains and releases the rotation of the gear, and a second clutch that restrains and releases between the output shaft and the second output gear.
The power transmission device according to claim 1, further comprising a clutch. 3. The planetary gear mechanism includes a first sun gear, an inner planetary gear supported at a fixed position and engaging with the first sun gear, and an inner planetary gear and a ring gear also supported at the fixed position. And a second sun gear that engages with the outer planetary gear, a first clutch that restrains / releases between the output disc and the first sun gear, an output disc and a second planetary gear.
The power transmission device according to claim 1, further comprising a second clutch that restrains and releases the space between the sun gears.