JPH1163148A - Half-toroidal type continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a half-toroidal type continuously variable transmission by which motive power transmitting efficiency can be improved. SOLUTION: A variator 2 and a planetary gear mechanism 3 are provided, and the variator 2 is composed of mutually opposing input discs 8a and 8b to rotate by interlocking with an input shaft 5, output discs 9a and 9b and a power roller 10 rollingly connected between both discs so as to be freely tiltable, and the planetary gear mechanism is composed of a sun gear 22, a ring gear 25 arranged around this sun gear and plural planetary gears 23 rotatably supported between the sun gear and the ring gear by a carrier 24, and has a hydraulic piston 6 which is arranged between the input shaft and the input discs and presses the input discs to the output discs through the power roller, a counter shaft 14 which transmits rotation of the output discs to the sun gear and circulates motive power to the variator and a motive power transmitting shaft 7 to transmit rotation of the input shaft to the carrier of the planetary gear mechanism 3.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a half toroidal continuously variable transmission used as a transmission for an automobile, for example.

[0002]

2. Description of the Related Art A continuously variable transmission for use as, for example, an automobile transmission is known, for example, from Japanese Patent Publication No. 6-21625. The continuous transmission includes a toroidal type continuously variable transmission in which a power roller is tiltably contacted between an input disk and an output disk, and a planetary gear mechanism connected to the output disk. .

[0003] Then, an input is received from an input shaft that is rotationally driven by an engine, and power is output to an output shaft. The planetary gear mechanism has a sun gear driven by an input shaft and a planet carrier driven by an output disk, and is driven by an output shaft connected to a ring gear.

[0004] The continuous transmission disclosed in Japanese Patent Publication No. Hei 6-21625 is provided with a first planetary gear mechanism and a second planetary gear mechanism. Then, the planet carrier of the first planetary gear mechanism and the sun gear of the second planetary gear mechanism are driven by the output shaft of the continuous transmission, and the sun gear of the first planetary gear mechanism and the second planetary gear mechanism are driven. Are driven by the engine, the ring gear of the first planetary gear mechanism is configured as a low-speed output section, and the planet carrier of the second planetary gear mechanism is configured as a high-speed output section.

[0005]

However, since the conventional continuous transmission is a full toroidal type continuously variable transmission, a power roller which is tiltably rotatably connected between an input disk and an output disk. There is a problem that the spin loss at the contact surface is large and the power transmission efficiency is poor.

The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a half toroidal type continuously variable transmission capable of improving power transmission efficiency.

[0007]

In order to achieve the above object, the present invention provides an input shaft that is driven to rotate by a drive source, an output shaft that extracts power based on the rotation of the input shaft,
A variator and a planetary gear mechanism disposed between the input shaft and the output shaft, wherein the variator includes a pair of input disks facing each other that rotates in conjunction with the input shaft; and a pair of the input disks. A pair of output disks arranged coaxially between and rotating synchronously with each other, and a power roller rotatably contacted between the input disk and the output disk, wherein the planetary gear mechanism comprises:
In a half toroidal-type continuously variable transmission device including a sun gear, a ring gear disposed around the sun gear, and a plurality of planetary gears rotatably supported by a carrier between the sun gear and the ring gear. A hydraulic pressing mechanism for transmitting the rotation of the input disk to the output disk via a power roller, and transmitting the rotation of the output disk to the sun gear of the planetary gear mechanism, and powering the planetary gear mechanism to a variator. A first power transmission mechanism for circulating and a second power transmission mechanism for transmitting rotation of the input disk to a carrier of the planetary gear mechanism are provided.

[0008]

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 is a system diagram of a double cavity type half toroidal type continuously variable transmission according to a first embodiment. In FIG. 1, reference numeral 1 denotes a toroidal type continuously variable transmission, which includes a variator 2 and a planetary gear mechanism 3. The variator 2
An input shaft 5 rotatably supported by a fixed portion via a bearing or the like and having one end connected to a drive source 4 such as an engine.
It has.

The input shaft 5 is provided with a hydraulic piston 6 as a hydraulic pressing mechanism. Power is transmitted to the variator 2 via the hydraulic piston 6.
The variator 2 is provided with a power transmission shaft 7 that rotates in conjunction with the hydraulic piston 6, and the power transmission shaft 7 is provided with a pair of input disks 8a and 8b facing each other. Between the power transmission shaft 7, a pair of output disks 9a and 9b in a loosely fitted state are coaxially arranged and rotate in synchronization with each other.

The power transmission shaft 7 projects rearward from the input disk 8b constituting the variator 2, and a low speed clutch 28 is provided in the power transmission shaft 7. Further, between the input disks 8a and 8b and the output disks 9a and 9b, there are provided a plurality of power rollers 10 which are rotatably contacted. Output disks 9a, 9
b is connected to the power transmission shaft 7 via a loose fitting shaft 11 that loosely fits.

The variator 2 transmits the rotational driving force transmitted to the power transmission shaft 7 to the loose fitting shaft 11 via the input disks 8a and 8b, the power roller 10 and the output disks 9a and 9b, and outputs the speed ratio, that is, the output. Disks 9a, 9b
The value obtained by dividing the rotation speed of the power rollers 10 by the rotation speed of the input disks 8a and 8b is determined by the tilt angle of the power roller 10.

That is, when the power roller 10 is in a horizontal state, the speed ratio is in a neutral state of 1, and when the output disks 9a and 9b of each power roller 10 are tilted away from the power transmission shaft 7, The speed ratio is reduced in accordance with the
When the a and 9b sides tilt in the direction approaching the power transmission shaft 7, the speed ratio increases accordingly. A first gear 12 is fitted on the loose fitting shaft 11, and the first gear 12 meshes with a second gear 13 provided on a counter shaft 14.
A third gear 15 is provided at the other end of the counter shaft 14, and the third gear 15 is connected to a fifth gear via a fourth gear 16.
Gear 17 and is interlocked with the planetary gear mechanism 3.

The planetary gear mechanism 3 includes a sun gear 22, a plurality of planetary gears 23 meshing with the sun gear 22, a carrier 24 connecting the respective planetary gears 23, and a ring gear 25 meshing with the planetary gears 23. , A sun gear 22 is connected to the fifth gear 17, and a carrier 24 is connected to a low speed clutch 28 via a central shaft 26. An output shaft 27 is provided on the ring gear 25. Further, a high-speed clutch 29 is provided between the ring gear 25 and the carrier 24 of the planetary gear mechanism 3 to connect / disconnect the two.

Next, the operation of the first embodiment will be described.

First, when the low speed clutch 28 is connected and the high speed clutch 29 is released, the power transmission shaft 7 and the center shaft 2
6 is connected. Therefore, the rotation of the input shaft 5 is
Power transmission shaft 7 → low speed clutch 28 → center shaft 26 → path for transmitting to carrier 24 of planetary gear mechanism 3, hydraulic piston 6 → input disks 8a, 8b → power low 10 → output disks 9a, 9b → first Gear 12 → Second gear 1
3 → counter shaft 14 → third gear 15 → fourth gear 16
→ the fifth gear 17 → the transmission to the sun gear 22 of the planetary gear mechanism 3 and the transmission to the planetary gear mechanism 3, and the transmission to the variator 2 using the differential of the planetary gear mechanism 3. An infinite gear ratio can be obtained by the combination.

At this time, the rotating sun gear 2
If the relative speed between 2 and the carrier 24 is “0”, the output rotation speed is “0”. That is, the vehicle can be started from a stopped state without the need for a start clutch, and starting and retreating can be performed by changing the relative speed.

On the other hand, when the variator 2 is tilted to the speed increasing side, that is, the power roller 10 is tilted in a direction in which the output disks 9a and 9b approach the power transmission shaft 7, the rotation speed of the counter shaft 14 is increased in accordance with the tilt. Accordingly, the rotation speed of the sun gear 22 of the planetary gear mechanism 3 increases, and the rotation speed of the output shaft 27 increases.

When the above-described speed change operation is performed, power circulates from the sun gear 22 at low speed and from the carrier 24 at retreat. That is, the circulation torque at the time of low speed is divided into the first circulation torque and the second circulation torque in the variator 2 after entering the first gear 12. The first circulating torque is transmitted through the path of the output disk 9a → the power roller 10 → the input disk 8a → the hydraulic piston 6 → the input shaft 5, while the second circulating torque is transmitted from the output disk 9b → the power roller 10 → the input disk 8b. → Power transmission shaft 7 → Hydraulic piston 6 → Input shaft 5 for transmission.

As described above, the input disk 8 is connected to the variator 2.
A torque is applied from the output disks 9a, 9b to the input disks 8a, 8b instead of from the output disks 9a, 9b, which is a so-called power circulating state. However, by using the half toroidal method, the spin loss on the contact surface is small, and the transmission efficiency can be improved.

Next, when the high-speed clutch 29 is connected and the low-speed clutch 28 is released, the rotation of the input shaft 5 causes the loose fitting shaft 11 to rotate via the output disks 9a, 9b, and the first gear 12, The power is transmitted to the second gear 13, the counter shaft 14 rotates, and the rotation of the counter shaft 14 is controlled by the third gear 1.
5, and transmitted to the sun gear 22 of the planetary gear mechanism 3 via the fourth gear 16 and the fifth gear 17.

The rotation of the sun gear 22 is transmitted to the ring gear 25 via the planetary gear 23 and transmitted to the output shaft 27.
Accordingly, the input shaft 5 is directly connected to the output shaft 27. While maintaining this state, the variator 2 is moved to the speed increasing side, that is, the power roller 10 is moved to the output disk 9a,
When the 9b side is tilted in a direction approaching the power transmission shaft 7,
The rotation speed of the counter shaft 14 increases in accordance with the tilt, the rotation speed of the sun gear 22 of the planetary gear mechanism 3 increases, and the rotation speed of the output shaft 27 increases. The speed ratio of the entire device 1 increases.

FIG. 2 shows a second embodiment, in which a hydraulic piston 6 as a hydraulic pressing mechanism is provided on the output disk 9a, 9b side of the variator 2;
This is the same as the embodiment, and the description is omitted.

FIG. 3 shows a third embodiment, which is a half-toroidal type having a variator 2 and first and second planetary gear mechanisms 3a and 3b between an input shaft 5 and an output shaft 27. 1 shows a step transmission. In FIG. 3, reference numeral 1 denotes a toroidal-type continuously variable transmission, which includes a variator 2 and first and second planetary gear mechanisms 3a and 3b. The variator 2 includes an input shaft 5 rotatably supported on a fixed portion via a bearing or the like and having one end connected to a drive source 4 such as an engine.

The input shaft 5 is provided with a hydraulic piston 6 as a hydraulic pressing mechanism. Power is transmitted to the variator 2 via the hydraulic piston 6.
The variator 2 is provided with a power transmission shaft 7 that rotates in conjunction with the hydraulic piston 6, and the power transmission shaft 7 is provided with a pair of input disks 8a and 8b facing each other. Between the power transmission shaft 7, a pair of output disks 9a and 9b in a loosely fitted state are coaxially arranged and rotate in synchronization with each other.

The power transmission shaft 7 projects rearward from the input disk 8b constituting the variator 2, and the power transmission shaft 7 is connected to the first planetary gear mechanism 3a. The input disks 8a and 8b and the output disk 9
A plurality of power rollers 10 rotatably contacted with each other are provided between the power rollers 10a and 9b. Output disks 9a, 9b
Is connected to the power transmission shaft 7 via a loose fitting shaft 11 that loosely fits.

The variator 2 transmits the rotational driving force transmitted to the power transmission shaft 7 to the loose fitting shaft 11 via the input disks 8a, 8b, the power roller 10, and the output disks 9a, 9b, and outputs the speed ratio, that is, the output. Disks 9a, 9b
The value obtained by dividing the rotation speed of the power rollers 10 by the rotation speed of the input disks 8a and 8b is determined by the tilt angle of the power roller 10.

That is, when the power roller 10 is in the horizontal state, the speed ratio is in the neutral state of 1, and when the output disks 9a and 9b of each power roller 10 are tilted away from the power transmission shaft 7, The speed ratio is reduced in accordance with the
When the a and 9b sides tilt in the direction approaching the power transmission shaft 7, the speed ratio increases accordingly. A first gear 12 is fitted on the loose fitting shaft 11, and the first gear 12 meshes with a second gear 13 provided on a counter shaft 14.
A third gear 15 is provided at the other end of the counter shaft 14, and the third gear 15 is connected to a fifth gear via a fourth gear 16.
Gear 17 and is interlocked with the second planetary gear mechanism 3b.

The first planetary gear mechanism 3a includes a sun gear 18, a plurality of planetary gears 19 meshing with the sun gear 18, a carrier 20 connecting the respective planetary gears 19, and a ring gear 21 meshing with the planetary gears 19. , And the sun gear 18 is connected to the power transmission shaft 7.

The second planetary gear mechanism 3b includes a sun gear 22, a plurality of planetary gears 23 meshing therewith,
A carrier 24 for linking the planetary gears 23 and a planetary gear 2
3, a sun gear 22 is connected to the fifth gear 17, and a carrier 24 is connected to the carrier 20 of the first planetary gear mechanism 3a via a center shaft 26. I have. An output shaft 27 is provided on the ring gear 25.

A low-speed clutch 28 for restraining and releasing the rotation of the ring gear 21 is provided between the ring gear 21 and the fixed portion of the first planetary gear mechanism 3a. A high-speed clutch 29 is provided between the ring gear 25 and the carrier 24 so as to contact and separate them.

Next, the operation of the third embodiment will be described.

First, when the low speed clutch 28 is connected and the high speed clutch 29 is released, the first planetary gear mechanism 3a
Ring gear 21 is fixed, the rotation of the sun gear 18 is transmitted to the carrier 20 via the planetary gear 19, and the rotation of the center shaft 26 is the carrier 24 of the second planetary gear mechanism 3b.
And the relative speed of rotation of the rotating sun gear 22 is transmitted to the ring gear 25.

Therefore, first, when the low speed clutch 28 is connected and the high speed clutch 29 is released, the rotation of the input shaft 5 is changed to the power transmission shaft 7 → the sun gear 18 of the first planetary gear mechanism 3 a → the planetary gear 19. → Carrier 20 → Center axis 26 →
The path to be transmitted to the carrier 24 of the second planetary gear mechanism 3b and the hydraulic piston 6 → input disks 8a, 8b → power low 10 → output disks 9a, 9b → first gear 12 →
Second gear 13 → counter shaft 14 → third gear 15 → fourth gear 16 → fifth gear 17 → second planetary gear mechanism 3
b is transmitted to the second planetary gear mechanism 3b through two paths, that is, the path transmitted to the sun gear 22 of FIG.
By using the differential of the planetary gear mechanism 3b in combination with the variator 2, an infinite speed ratio can be obtained.

At this time, the rotating sun gear 2
If the relative speed between 2 and the carrier 24 is “0”, the output rotation speed is “0”. That is, the vehicle can be started from a stopped state without the need for a start clutch, and starting and retreating can be performed by changing the relative speed.

On the other hand, when the variator 2 is tilted to the speed increasing side, that is, the power roller 10 is tilted in a direction in which the output disks 9a and 9b approach the power transmission shaft 7, the rotation speed of the counter shaft 14 is increased in accordance with the tilt. As a result, the rotation speed of the sun gear 22 of the second planetary gear mechanism 3b increases, and the rotation speed of the output shaft 27 increases accordingly.

When the above-described speed change operation is performed, the power circulates from the sun gear 22 at low speed and from the carrier 24 at reverse. That is, the circulation torque at the time of low speed is divided into the first circulation torque and the second circulation torque in the variator 2 after entering the first gear 12. The first circulating torque is transmitted through the path of the output disk 9a → the power roller 10 → the input disk 8a → the hydraulic piston 6 → the input shaft 5, while the second circulating torque is transmitted from the output disk 9b → the power roller 10 → the input disk 8b. → Power transmission shaft 7 → Hydraulic piston 6 → Input shaft 5 for transmission.

When the above-described shifting operation is performed, the power circulates from the sun gear 22 at low speed and from the carrier 24 at retreat, and the input disks 8a, 8b
Instead, a torque is applied from the output disks 9a and 9b to the input disks 8a and 8b, that is, a so-called power circulation state is obtained.
However, by using the half toroidal method, the spin loss at the contact surface is small, and the transmission efficiency can be improved.

Next, when the high speed clutch 29 is connected and the low speed clutch 28 is released, the rotation of the input shaft 5 causes the loose fitting shaft 11 to rotate via the output disks 9a and 9b, and the first gear 12 The power is transmitted to the second gear 13, the counter shaft 14 rotates, and the rotation of the counter shaft 14 is controlled by the third gear 1.
5, the second gear via the fourth gear 16 and the fifth gear 17
Is transmitted to the sun gear 22 of the planetary gear mechanism 3b.

The rotation of the sun gear 22 is transmitted to the ring gear 25 via the planetary gear 23 and transmitted to the output shaft 27.
Accordingly, the input shaft 5 is directly connected to the output shaft 27. While maintaining this state, the variator 2 is moved to the speed increasing side, that is, the power roller 10 is moved to the output disk 9a,
When the 9b side is tilted in a direction approaching the power transmission shaft 7,
The rotation speed of the counter shaft 14 increases according to the tilt, and accordingly, the sun gear 2 of the second planetary gear mechanism 3b
2, the rotation speed of the output shaft 27 increases, and the speed ratio of the entire toroidal-type continuously variable transmission 1 increases.

[0041]

As described above, according to the present invention, by using the half-toroidal type continuously variable transmission, the spin loss at the contact surface is small, and the power transmission efficiency can be improved. In addition, by combining the variator and the planetary gear mechanism, an infinite speed ratio can be obtained, and if the relative speed between the rotating sun gear and the carrier is “0”, the output rotation speed is “0”. By changing the relative speed,
Start and retreat are possible.

[Brief description of the drawings]

FIG. 1 is a system diagram of a half toroidal type continuously variable transmission according to a first embodiment of the present invention.

FIG. 2 is a system diagram of a half toroidal type continuously variable transmission according to a second embodiment of the present invention.

FIG. 3 is a system diagram of a half toroidal type continuously variable transmission according to a third embodiment of the present invention.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 2 ... Variator 3 ... Planetary gear mechanism 4 ... Drive source 5 ... Input shaft 6 ... Hydraulic piston 8a, 8b ... Input disk 9a, 9b ... Output disk 10 ... Power roller 14 ... Counter shaft 27 ... Output shaft 28 ... Low speed clutch 29 ... High speed clutch

Claims (1)

[Claims] An input shaft rotatably driven by a drive source;
An output shaft for taking out power based on the rotation of the input shaft, a variator and a planetary gear mechanism disposed between the input shaft and the output shaft, wherein the variator rotates in conjunction with the input shaft. A pair of input disks opposed to each other, a pair of output disks coaxially disposed between the pair of input disks and rotating in synchronization with each other, and a tiltably rolling contact between the input disk and the output disk The planetary gear mechanism comprises a sun gear, a ring gear disposed around the sun gear, and a plurality of rotatably supported by a carrier between the sun gear and the ring gear. A half-toroidal-type continuously variable transmission, comprising: a planetary gear; A first power transmission mechanism that transmits the rotation of the output disk to the sun gear of the planetary gear mechanism and circulates the power of the planetary gear mechanism to the variator; and a rotation of the input disk to the carrier of the planetary gear mechanism. And a second power transmission mechanism for transmitting the power.