JPH06280960A - Toroidal type continuously variable transmission - Google Patents

Abstract

(57) [Summary] [Purpose] In a toroidal continuously variable transmission, by supplying oil according to the direction of rotation between the roller and the disk, power loss due to splashing of oil and agitation resistance reduction due to agitation of oil are reduced. Plan. [Structure] Oil supply nozzles 6 and 7 having oil ejection ports 6a, 6b and 7a, 7b are provided toward a rolling surface whose rotation direction between the input / output disks 5a and 5b and the roller 5c is the closing side.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a lubrication and cooling mechanism for a toroidal type continuously variable transmission.

[0002]

2. Description of the Related Art As a lubricating mechanism for a toroidal type continuously variable transmission, there is, for example, one described in JP-A-62-283256 or JP-A-2-47458. The lubrication mechanism described in Japanese Patent Application Laid-Open No. 62-283256 is to provide an oil passage for lubricating oil inside the roller supporting member (trunnion) and guide the oil to the contact portion between the roller and the input / output disk. On the other hand, the lubrication mechanism disclosed in Japanese Utility Model Laid-Open No. 2-47458 is to provide an oil passage for lubrication having an opening at the ends of the rollers facing each other and supply oil to the contact portion between the roller and the input / output disk. is there.

[0003]

However, in these lubricating mechanisms, a large centrifugal force acts on the oil when the disk rotates at a high speed, which results in the oil being blown off to the outer peripheral side, and the contact portion between the disk and the roller is lost. Not always well lubricated. Furthermore, none of these lubrication mechanisms supplies oil in consideration of the rotational direction between the roller and the disk. Therefore, the supplied oil may be splashed by the rotating roller or disk depending on the direction of rotation between the roller and the disk. Since the oil bounces off by receiving momentum from the roller or disk, unnecessary bounce off of oil also leads to power loss.

Depending on the direction of rotation between the roller and the disc, the oil may be agitated between the roller and the disc, and the agitation resistance of the oil may cause power resistance to the roller or the disc. The present invention has been made in view of such problems, and by supplying oil in accordance with the rotation direction between the roller and the disk, power loss due to splashing of oil and agitation resistance due to stirring of oil. An object of the present invention is to provide a toroidal type continuously variable transmission equipped with a lubrication mechanism capable of reducing the number of the toroidal type continuously variable transmissions.

[0005]

In order to achieve this object, a toroidal type continuously variable transmission according to the present invention comprises an input disk, an output disk, a pair of rollers that are in rotary contact with both disks, and the rollers. Has a roller support member that is rotatable about the rotation shaft portion and that is movable in the rotation shaft portion direction, and a hydraulic cylinder that moves the roller support member in the rotation shaft portion direction. In a toroidal type continuously variable transmission, an oil supply nozzle that supplies oil to a rolling surface between an input / output disk and a roller is arranged between the input / output disk and between a pair of rollers. . This oil supply nozzle has an oil ejection port toward the rolling surface where the rotation direction of the input / output disk and the roller is the closing side.

The oil supply nozzle may be formed so as to have a pair of oil jets at an interval of 180 degrees, and these oil jets may be directed to the rolling surface of the pair of rollers on the closing side. Further, the oil supply nozzle can be formed to include a first nozzle having an oil ejection port facing the upper end of the roller and a second nozzle having an oil ejection port facing the lower end of the roller. .

In this case, it is preferable that the oil supply amount from the first nozzle be larger than the oil supply amount from the second nozzle. The term "closed side" used in this specification is defined as follows. As shown in FIG. 4, the rollers A and B rotate about their axes y in the directions of arrows a and b, respectively, and the input / output disk rotates about their axes x in the directions of arrows c and d, respectively. If so, the side of the rolling surface between the roller A and the input disc or the side of the rolling surface between the roller B and the output disc is defined as the “closed side”. That is,
The side in which both the roller and the disk rotate in the winding direction is the "closing side". As is clear from FIG. 4, there are two "closed sides" between the pair of rollers and the input / output disk, and they are located diagonally with respect to the axis x or y.

Further, the "closed side" is opposite to the roller rotation axis y between the upper end side and the lower end side of the roller.
That is, the above-mentioned "closing side" is the closing side of the upper end side of the roller, and the lower side of the roller is the side indicated as "lower end closing side".

[0009]

Since the oil ejection port of the oil supply nozzle faces the closing side of the roller and the input / output disk in the rotational direction of each other, the oil supplied to the rolling surface is accompanied by the rotation of the roller and the input / output disk. The contact surfaces are caught and lubricated. In this case, the oil is supplied in the direction in which it is wound around the contact surface between the roller and the disk, so that the oil is not splashed and the stirring resistance due to the stirring of the oil does not increase.

As shown in FIG. 4, the closing side is located on the diagonal of each axis of the roller and the input / output disk. Therefore, by using an oil supply nozzle having a pair of oil jets at intervals of 180 degrees, it is possible to supply oil to both closed sides with one nozzle, and improve the supply efficiency. Furthermore, by providing two nozzles toward both the upper end and the lower end of the roller, it is possible to effectively supply oil to the upper and lower closed sides,
It is possible to improve the lubrication efficiency of both the roller and the input / output disk. In this case, the amount of oil supplied to the upper end of the roller can be made larger than the amount of oil supplied to the lower end of the roller. This is because the lower end side of the roller is lubricated to some extent by the oil leaking from the piston chamber, and therefore, it is less necessary to supply the oil toward the upper end of the roller.

[0011]

1 is a schematic configuration diagram of an embodiment of a toroidal type continuously variable transmission according to the present invention. The output torque of the engine 1 including the first cylinder # 1 to the fourth cylinder # 4 is selectively transmitted to the first transmission unit A and the second transmission unit B via the starting clutch 2. The first transmission unit A has a gear reduction mechanism 3 including a torque converter and a planetary gear mechanism, and a forward / reverse switching mechanism (not shown), and the second transmission unit B has a toroidal type continuously variable transmission 5. Become. The output torque of the engine 1 is output to the transmission output shaft 4 via the first transmission section A when the starting clutch 2 is in the off state, and via the second transmission section B when the starting clutch 2 is in the on state. To be done.

The first transmission unit A is mainly used when a relatively large gear ratio is required at the time of starting or accelerating, and the second transmission unit B is mainly operated at a relatively small gear ratio at the time of high speed traveling. Is used when. The toroidal type continuously variable transmission 5 that constitutes the second speed change portion B is arranged so as to face the input disk 5a that is rotated by the input of engine torque and the input disk 5a coaxially with each other.
An output disk 5b for outputting torque and a roller 5c for rotationally contacting both of these disks and transmitting torque from the input disk 5a to the output disk 5b are provided. As shown in FIG. 2, the pair of rollers 5c is rotatably supported by a roller supporting member 5d, and the roller supporting member 5d can be displaced in the axial direction (vertical direction in FIG. 2) by a hydraulic cylinder mechanism described later. By
The tilt angle of the roller 5c is changed, and the gear ratio can be continuously obtained according to the tilt angle.

A shaft member 5e extends downward from the lower end of the roller support member 5d. A pair of upper piston 5f and lower piston 5g extend vertically in the shaft member 5e in the circumferential direction of the shaft member 5e. Is formed in this way. The upper piston 5f and the lower piston 5g are separated from each other by a partition wall 5h fixed to the transmission case. The upper piston 5f and the partition wall 5h are separated from each other by an upper hydraulic chamber 5i and a lower piston. Lower hydraulic chambers 5j are formed between 5g and the partition wall portion 5h.

When the hydraulic pressure is sent to the upper hydraulic chamber 5i, the hydraulic pressure acts on the upper piston 5f, and the roller support member 5d is displaced upward. On the other hand, when the hydraulic pressure is sent to the lower hydraulic chamber 5j, the hydraulic pressure acts on the lower piston 5g, and the roller support member 5d is displaced downward. When the roller support member 5d is moved up and down by such a hydraulic cylinder mechanism, the roller 5c is moved in accordance with the amount of displacement along with the displacement in the vertical direction.
Is tilted, and the gear ratio of the toroidal type continuously variable transmission 5 is changed.

In this toroidal type continuously variable transmission 5, an upper oil supply nozzle 6 is arranged near the upper ends of a pair of rollers 5c, and a lower oil supply nozzle 7 is arranged near the lower ends of the rollers 5c. The upper and lower oil supply nozzles 6 and 7 are located at the center of the pair of rollers 5c facing each other and in the middle between the input disk 5a and the output disk 5b.

These oil supply nozzles 6 and 7 are shown in FIG.
As shown in FIG. 5, the nozzle has a linear nozzle shape, and oil jet ports 6a, 6b and 7a, 7b are formed at both ends. These oil jets 6a, 6b and 7
The a and 7b are provided toward the rolling surface between the roller 5c and the input / output disks 5a and 5b. Further, the oil ejection ports 6a and 6b of the upper oil supply nozzle 6 and the oil ejection ports 7a and 7b of the lower oil supply nozzle 7 are respectively directed to the closing side rolling surface between the roller 5c and the input / output discs 5a and 5b. Has been. Input disk 5a, output disk 5
b, the pair of rollers 5c are respectively indicated by arrows e, f, g and h in FIG.
As shown in FIG. 3, the upper end side of the roller 5c is the side closer to the “upper end closed side”, and the lower end side of the roller 5c is the side closer to the “lower end closed side”. Becomes That is, the closing side of the upper end side and the lower end side of the roller 5c are opposite to each other with respect to the rotation axis of the roller 5c. Therefore, the oil outlets 6a and 6b of the upper oil supply nozzle 6 face the upper end closed side, and the oil outlets 7a and 7b of the lower oil supply nozzle 7 face the lower end closed side.

Oil is supplied to the upper and lower oil supply nozzles 6 and 7 through a controller (not shown). The controller determines the oil supply amount using parameters such as vehicle speed and engine speed, and supplies oil to each oil supply nozzle. Further, the controller determines the oil supply amount such that the oil supply amount to the upper oil supply nozzle 6 is larger than the oil supply amount to the lower oil supply nozzle 7 by a fixed ratio R. The fixed ratio R may be a constant, or the roller 5c or the input / output disk 5 may be used.
It is also possible to use variables such as the rotational speeds of a and 5b as parameters.

As shown in FIG. 3, the toroidal type continuously variable transmission 5 is provided with two sets of units each consisting of an input disk 5a, an output disk 5b and a pair of rollers 5c in the transmission output shaft direction. The above-mentioned oil supply nozzles have the same structure.

[0019]

Since the oil is supplied to the rolling surface on the closing side between the roller and the input / output disk, the oil is not splashed and is transmitted so as to be caught in the contact surface between the roller and the disk, thereby improving the lubrication efficiency. Can be increased. Also,
Since the oil is not agitated, the drive loss due to the oil agitation is also eliminated.

[Brief description of drawings]

FIG. 1 is a schematic configuration diagram of a toroidal type continuously variable transmission.

FIG. 2 is a vertical sectional view of an embodiment of the toroidal type continuously variable transmission according to the present invention.

FIG. 3 is a plan view of the toroidal type continuously variable transmission shown in FIG. 2 as seen from above.

FIG. 4 is a schematic diagram showing a relationship between a roller and a rotation direction of an input / output disk.

[Explanation of symbols]

 1 engine 2 start clutch 3 gear reduction mechanism 4 transmission output shaft 5 toroidal type continuously variable transmission 5a input disc 5b output disc 5c roller 5d roller support member 5e shaft member 5f upper piston 5g lower piston 6 upper oil supply nozzle 7 lower Side oil supply nozzle 6a, 6b, 7a, 7b Oil jet port

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Hidetoshi Nobumoto 3-1, Shinchi, Fuchu-cho, Aki-gun, Hiroshima Mazda Motor Corporation

Claims (4)

[Claims] 1. An input disk, an output disk, a pair of rollers that are in rotary contact with both of these disks, and a pair of rollers that rotatably support the rollers and that are rotatable about a rotary shaft portion. In a toroidal type continuously variable transmission having a roller support member movable in a direction and a hydraulic cylinder moving the roller support member in the rotation shaft direction, a rolling surface between the input / output disk and the roller. An oil supply nozzle for supplying oil to the input / output disk and between the pair of rollers, wherein the oil supply nozzle is closed on the side where the input / output disk and the roller rotate in a mutually rotating direction. A toroidal type continuously variable transmission characterized in that it has an oil ejection port toward the rolling surface that becomes 2. The oil supply nozzle has a pair of oil jets at intervals of 180 degrees, and these oil jets are respectively directed toward the rolling surface of the pair of rollers on the closing side. The toroidal type continuously variable transmission according to claim 1. 3. The oil supply nozzle comprises a first nozzle having an oil ejection port facing the upper end of the roller and a second nozzle having an oil ejection port facing the lower end of the roller. The toroidal type continuously variable transmission according to claim 2 or 3. 4. The toroidal type continuously variable transmission according to claim 4, wherein the oil supply amount from the first nozzle is larger than the oil supply amount from the second nozzle.