JPH07139600A - Toroidal type continuously variable transmission - Google Patents

Abstract

PURPOSE:To provide a toroidal type continuously variable transmission capable of reducing its size weight, and cost, and preventing reduction of transmission efficiency. CONSTITUTION:An output shaft 50 is arranged in series on the same axial line L in relation to an input shaft 10, one end part of the output shaft 50 and one end part of the input shaft 10 are folded in axial line L direction in such a way that one side is set to an inner side and the other side is set to an outer side. An output disk 22 is arranged opposing to an input disk 21 in such a condition that the output disk 22 exists on the output end side of the output shaft 50 in relation to the input disk 21. A bearing 60 receiving a thrust load acting in a direction for separating them from each other in relation to the input and output shafts 10, 50, is arranged between the input and output shafts 10, 50.

Description

Detailed Description of the Invention

[0001]

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

[0002]

2. Description of the Related Art A toroidal type continuously variable transmission has been conventionally known as a continuously variable transmission for automobiles (Japanese Patent Laid-Open No. 6-58242).
No. 4-3362).

In this toroidal type continuously variable transmission, an input disk to which engine torque is input, an output disk for outputting torque to the drive wheel side, and both disks are rotationally contacted so that the torque of one disk is changed to the other. It has a toroidal speed changer constituted by two power rollers which are transmitted to the disk. The power roller is rotatably supported by a roller supporting member, and the power roller is displaced by displacing the roller supporting member in the axial direction thereof.
The tilt angle of the rotor changes, and a gear ratio corresponding to this tilt angle is obtained.

The toroidal type continuously variable transmission described in the above publication is provided with one toroidal transmission portion, but the transmission torque capacity is increased without increasing the outer diameter of the toroidal transmission portion. If necessary, a pair of toroidal transmission units that function in parallel for torque transmission may be arranged in series on the same axis, with the input disks of the two toroidal transmission units arranged back to back.

By the way, in a general toroidal type continuously variable transmission, for example, between the input shaft and the input disk,
A loading cam device for transmitting the rotational force of the input shaft to the input disc and pressing the input disc toward the output disc is provided.

Therefore, since a thrust load in the direction of separating the input disk and the output disk from each other acts on both disks, a thrust bearing for receiving the thrust load of the shaft is required when there is only one toroidal transmission. become. In that case, if the above-mentioned thrust load is received by the transmission casing via the thrust bearing, the case
Since the rigidity of the singing becomes a problem, various shaft support structures capable of canceling the thrust load have been conventionally proposed.

FIG. 6 is a skeleton diagram showing the structure of a conventional toroidal-type continuously variable transmission having a structure similar to the toroidal-type continuously variable transmission described in the above publication.

The input shaft 10 extending over the entire length of the casing 1 with the left end of the drawing as an input end has radial bearings 11 and 12 provided on front and rear walls 2 and 3 of the casing 1, respectively. It is rotatably supported by.

The toroidal transmission unit 20 is arranged in a pressure contact state between an input disk 21 and an output disk 22 rotatably arranged on the input shaft 10 and annular surfaces 21a and 22a of the disks 21 and 22 facing each other. The two discs 2 are formed by the two power rollers 23 and 24 which are rotated, and as the power rollers 23 and 24 roll.
1 and 22 are adapted to rotate in opposite directions.

Behind the input disk 21, with respect to the input disk 21, according to the input torque of the input shaft 10,
A loading cam device 30 for applying a thrust load to the left in the drawing is provided. The loading cam device 30 includes a cam disk 31 fixed to the input shaft 10.
And a plurality of cam rollers 32 arranged between the cam surfaces formed on the facing surfaces of the cam disk 31 and the input disk 21, respectively. Therefore, a thrust load directed to the right in the figure acts on the input shaft 10.

On the other hand, the output disk 22 is fixed on a hollow output disk shaft 40 which is rotatably supported coaxially with the outer circumference of the input shaft 10. Therefore, a thrust load directed to the left in the figure acts on the output disc shaft 40. A drive gear 41 is fixed on the output disc shaft 40 behind the output disc 22.

The output shaft 50 is arranged outside the casing 1 as a counter shaft parallel to the input shaft 10. A driven gear 51 meshing with a drive gear 41 is fixed to the output shaft 50, and an output disc shaft is provided. The rotational torque of 40 is transmitted to the output shaft 50.

The casing 1 is formed with a wall portion 4 extending parallel to the wall portion 2 in the space between the drive gear 41 and the wall portion 2 on the input end side of the input shaft 10. A thrust bearing 13 that receives a thrust load to the right of the input shaft 10 is interposed between the flange 10a formed on the input shaft 10 and the wall surface of the wall portion 4 on the input end side of the input shaft 10. ing.

A flange 40a is formed on the output disk shaft 40 at the input end side of the input shaft 10. Between the flange 40a and the wall surface of the wall portion 4 on the drive gear 41 side, the output disk shaft 40 is provided. A thrust bearing 42, which receives a thrust load of 40 to the left, is interposed back-to-back and adjacent to the thrust bearing 13. That is, the thrust bearings 13, 42 are
The flange 10a of the input shaft 10 and the output disc shaft 4
No. 0 flange 40a receives a thrust load in a direction in which they approach each other. Therefore, the thrust load to the right of the input shaft 10 and the thrust load to the left of the output disk shaft 40 are mutually at the wall portion 4. It is designed to be offset.

[0015]

However, in the configuration of the toroidal type continuously variable transmission shown in FIG.
However, since it is arranged between the input disk 21 and the wall portion 4, it is impossible to provide the output shaft coaxially with the input shaft 10. Therefore, the output shaft 50 is arranged in parallel with the input shaft 10 as a counter shaft, and the output is taken out between the wall portion 4 and the output disk 22 via the drive gear 41 and the driven gear 51.

Therefore, the outer shape of the transmission is increased, and the weight and cost are increased. Further, the gears 41, 51 are used to extract the output of the transmission.
There is also a problem that the transmission efficiency is reduced due to the use of.

In view of the above-mentioned circumstances, it is an object of the present invention to provide a toroidal type continuously variable transmission which is small in size, light in weight, inexpensive, and capable of preventing a decrease in transmission efficiency.

[0018]

In the toroidal type continuously variable transmission according to the present invention, the output shaft thereof is arranged in series on the same axis line with respect to the input shaft, and the minus end portion of the output shaft and the input end are connected to each other. The-end portion of the shaft is superposed in the axial direction in such a relationship that one side is inside and the other side is outside. Further, the output disc is arranged so as to face the input disc in such a manner that it exists on the output end side of the output shaft with respect to the input disc.

Further, a bearing for receiving a thrust load acting on the input / output shaft in a direction to separate them from each other is arranged between the input / output shafts.

1 of a toroidal type continuously variable transmission according to the present invention
According to one aspect, a loading cam for transmitting the rotational force of the input shaft to the input disc and pressing the input disc toward the output disc between the input shaft and the input disc. A device is interposed, and a bearing for receiving the thrust load is disposed inside the loading cam device.

According to another aspect of the toroidal type continuously variable transmission of the present invention, a radial bearing is interposed between the input and output shafts, and the radial bearing serves as one of the input and output shafts. -Located inside a bearing that rotatably supports the thing.

[0022]

In the toroidal type continuously variable transmission according to the present invention, the output shaft thereof is arranged in series on the same axis line with respect to the input shaft, and the-end portion of the output shaft and the input shaft are connected. -The end portion is axially superposed in a relationship in which one side is the inner side and the other side is the outer side, and the output disc is opposed to the input disc in such a manner that the output disc is on the output end side of the output shaft with respect to the input disc Since it is arranged, the counter shaft is not required, and the space for installing the gear for deriving the output is also unnecessary. Therefore, the toroidal type continuously variable transmission that is small, lightweight and inexpensive is easy. Can be obtained.

There is also an advantage that the torque transmission efficiency is improved because the gear is not used for taking out the output of the transmission.

[0024]

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

FIG. 1 is a sectional view showing the construction of a toroidal type continuously variable transmission according to a first embodiment of the present invention, and FIG. 2 is a skeleton diagram thereof. In addition, in FIG. 1 and FIG.
Members corresponding to the respective members in FIG. 6 are shown with the same reference numerals. In addition, the left-right direction in the following description is the left-right direction in the drawing.

1 and 2, the input shaft 10 having a relatively short length with the left side (front side) as an input end has a hollow cylindrical portion 10b coaxially at the right end portion (rear end portion). Further, a large-diameter flange 10c having a spline groove formed on the outer peripheral surface is provided at the rear end of the cylindrical portion 10b. The input shaft 10 is connected to the outer peripheral surface of the cylindrical portion 10b by a casing.
The casing 1 is rotatably supported by the casing 1 by an angular contact bearing 11 which is interposed between the casing 1 and the front wall portion 2 and mainly receives a load in the radial direction.

The output shaft 50 is arranged in series on the same axis L with respect to the input shaft 10 with its right end as an output end, and extends over substantially the entire length of the casing 1. The left end portion of the output shaft 50 is the cylindrical portion 10 of the input shaft 10.
The small-diameter portion 50a to be inserted into the
The left end of the output shaft 50 is rotatably supported by the input shaft 10 by a radial bearing 70 interposed between the outer peripheral surface of a and the inner peripheral surface of the cylindrical portion 10b of the input shaft 10.

Therefore, the right end portion of the input shaft 10 and the left end portion of the output shaft 50 are superposed in the direction of the axis L with the output shaft 50 inside and the input shaft 10 outside.
The radial bearing 70 is arranged inside an angular contact bearing 11 that rotatably supports the input shaft 10 on the front wall portion 2 of the casing 1.

The output shaft 50 is provided with a flange 50b at the right end of the small diameter portion 50a, and is rotatable with respect to the rear wall portion 3 of the casing 1 mainly by an angular contact bearing 53 which receives a load in the radial direction. Is supported by. Further, a connecting member 55 for connecting a propeller shaft (not shown) to the output shaft 50 is spline-coupled to the right end portion (output end) of the output shaft 50.

The toroidal transmission unit 20 includes an input disk 21 rotatably arranged on the output shaft 50 and an output shaft 50.
Output disc 2 fixed by spline coupling to
2 and the annular surfaces 21a of the disks 21 and 22 facing each other,
Two power rollers 2 arranged in a pressure contact state between 22a.
3, 24, and power rollers 23, 24
The two disks 21 and 22 are rotated in the opposite directions with the rolling. The output shaft 50 has a locking ring 56 for preventing the output disc 22 from moving to the right, that is, in the direction away from the input disc 21.
Is fitted.

An annular cam disk support member 15 is spline-coupled to the outer periphery of the flange 10c of the input shaft 10 having a spline groove formed on the outer peripheral surface thereof.
Further, on the outer peripheral surface of the cam disc support member 15,
A spline groove is formed only in the central portion of the input / output shafts 10, 50 with respect to the direction of the axis L, and the cam disk 31 of the loading cam device 30 is splined thereto. A screw groove is formed at the left end of the outer peripheral surface of the cam disc support member 15, and a nut 16 is screwed into this screw groove to lock the cam disc 31. Then, a plurality of cam rollers 32 are provided between the cam surfaces formed on the facing surfaces of the cam disk 31 and the input disk 21, respectively.
Are arranged.

An angular contact bearing 60, which mainly receives a thrust load, is interposed between the inner peripheral surface of the cam disk supporting member 15 and the outer peripheral surface of the output shaft 50. The inner race 60a of the bearing 60 arranged inside the loading cam device 30.
Has a ball receiving surface that faces diagonally rightward, and is fitted on the output shaft 50 in a state where the left end surface of the ball receiving surface abuts the right end surface of the flange 50b of the output shaft 50. The outer race 60b of the bearing 60 is an inner race 60b.
The cam disc supporting member 15 has a ball receiving surface facing diagonally leftward so as to face the ball receiving surface of a and is fitted on the inner peripheral surface of the cam disc supporting member 15. A projecting edge portion 15a is formed at the right end of the inner peripheral surface of the bearing 60, and the right end surface of the outer race 60b of the bearing 60 is in contact with the wall surface facing the left side of the projecting edge portion 15a. Further, the left end surface of the outer race 60b is a flange 10c of the input shaft 10.
Is in contact with the right end surface of.

In the above structure, when a torque is input to the input shaft 10, this torque is transmitted to the cam disk 31. Then, due to the action of the loading cam device 30, a pressing force is exerted in the direction in which the cam disc 31 and the input disc 21 are separated from each other according to the input torque, that is, in the direction in which the input disc 21 approaches the output disc 22. This pressing force works and the input disk 21
The traction force is generated at the contact point between the output disk 22 and the power rollers 23 and 24 interposed between the disks 21 and 22 to transmit the power.

In this case, the output disk 22 is the output shaft 50.
Since it is fixed to, the pressing force acts in a direction to separate the output shaft 50 and the cam disc support member 15 in the axis L direction. The angular contact bearing 60 is interposed between the inner peripheral surface of the cam disk support member 15 and the outer peripheral surface of the output shaft 50, so that
By the reaction from the ding cam device 30, the cam disk 3
1. The angular contact bearing 60 receives the leftward thrust load acting on the input shaft 10 through the cam disk support member 15 and the outer race 60b of the bearing 60. In other words, the thrust load to the left acting on the input shaft 10 is received by the thrust load receiving surface facing the input shaft 10 on the side opposite to the input shaft 10 side.

Further, the output shaft 5 is connected via the output disk 22.
The rightward thrust load acting on 0 will be received by the angular contact bearing 60 having the rightward thrust load bearing surface. Therefore, the thrust load acting on the input shaft 10 and the output shaft 50 in the direction of separating them from each other in the axis L direction is
It will be received and offset by the bearing 60. A thrust bearing may be used instead of the angular contact bearing 60.

As is clear from the above description, in this embodiment, the output shaft 50 is arranged in series on the same axis L with respect to the input shaft 10, and the output shaft 50 is connected to the left end portion of the output shaft 50. The right end portion of the shaft 10 is overlapped in the direction of the axis L with the output shaft 50 being the inner side and the input shaft 10 being the outer side, and the output disc 22 is positioned relative to the input disc 21 with the output shaft 50.
Since it is arranged facing the input disk 21 so that it exists on the output end side, the counter shaft is not necessary, and the space for providing the gear for deriving the output is also unnecessary. It is possible to easily obtain a small, lightweight and inexpensive toroidal type continuously variable transmission.

There is also an advantage that the torque transmission efficiency is improved by not using the gear for deriving the output.

FIG. 3 is a skeleton diagram showing a second embodiment of the present invention.

The present embodiment has a configuration in which the input / output relationship is reversed with respect to the configuration of the first embodiment shown in FIG. That is, the input shaft 10 is extended with the right side of the drawing as the input end, and the output shaft 50 having the left side of the drawing as the output end.
Are arranged in series on the same axis with respect to the input shaft 10, and the left end portion of the input shaft 10 and the right end portion of the output shaft 50 have the output shaft 50 outside and the input shaft 10 inside. The bearings are superposed in the axial direction, and the radial bearing 70 is interposed in the superposed portion. The input disk 21 is the input shaft 10
The output disk 22 is fixed on the input shaft 10 and is rotatably provided on the input shaft 10.

The loading cam device 30 is provided on the output disk 22 side, and acts on the inside of the loading cam device 30 in a direction to separate the input shaft 10 and the output shaft 50 from each other in the axial direction. A bearing 60 is arranged to receive a thrust load. Further, the output disc 22 is arranged so as to face the input disc 21 such that the output disc 22 exists on the output end side of the output shaft 50 with respect to the input disc 21.

Even with such a configuration, the above-mentioned first
It is clear that the same effect as the embodiment can be obtained.

FIG. 4 is a skeleton diagram showing the third embodiment of the present invention.

In the present embodiment, the loading cam device 30 provided on the input disk 21 side in the structure shown in FIG. 2 is moved to the output disk 22 side, and the output disk 22 is also output shaft 50 together with the input shaft 10. The third embodiment is the same as the first embodiment except that it is rotatably provided on the upper side, and therefore further description will be omitted.

Further, FIG. 5 is a skeleton diagram showing a fourth embodiment of the present invention.

This embodiment has a configuration in which the input / output relation is reversed from that of the third embodiment shown in FIG. 4, similarly to the relation of the second embodiment with respect to the first embodiment. 5 is clear from FIG. 5, the corresponding members are only given the same reference numerals, and detailed description thereof is omitted.

[Brief description of drawings]

FIG. 1 is a sectional view showing the structure of a toroidal type continuously variable transmission according to a first embodiment of the present invention.

FIG. 2 is a skeleton diagram used to explain the configuration of FIG.

FIG. 3 is a skeleton diagram for explaining the configuration of a toroidal type continuously variable transmission according to a second embodiment of the present invention.

FIG. 4 is a skeleton diagram for explaining the structure of a toroidal type continuously variable transmission according to a third embodiment of the present invention.

FIG. 5 is a skeleton diagram for explaining the configuration of a toroidal type continuously variable transmission according to a fourth embodiment of the present invention.

FIG. 6 is a skeleton diagram for explaining the configuration of a conventional toroidal type continuously variable transmission.

[Explanation of symbols]

 1 Casing 10 Input Shaft 20 Toroidal Speed Change Unit 21 Input Disc 22 Output Disc 23, 24 Power Roller 30 Loading Cam Device 31 Cam Disc 32 Cam Roller 50 Output Shaft 60 Angular Contact Bearing 70 Radial Bearing

Claims (3)

[Claims] 1. An input shaft, serially arranged on the same axis with respect to the input shaft, and one end of the input shaft is inside the other end of the input shaft and the other is outside. And an input disc disposed on the axis of the input / output shaft, facing the input disc in a manner that the output shaft is present on the output end side of the output shaft with respect to the input disc. And a toroidal speed changer constituted by an output disk arranged on the axis and a power roller tiltably tilted between the output disk and the input / output disk, and the input / output shaft A toroidal-type continuously variable transmission, which is provided between the input and output shafts and which receives a thrust load acting in a direction to separate them from each other. 2. The rotational force of the input shaft is transmitted to the input disc between the input shaft and the input disc,
Further, a loading cam device for pressing the input disc toward the output disc side is interposed, and a bearing for receiving the thrust load is arranged inside the loading cam device. The toroidal type continuously variable transmission according to claim 1. 3. A radial bearing is interposed between the input and output shafts, and the radial bearing is arranged inside a bearing that rotatably supports one of the input and output shafts in a casing. 1. The method according to claim 1, wherein
Alternatively, the toroidal type continuously variable transmission described in 2.