JP2576534Y2 - Toroidal type continuously variable transmission - Google Patents

Description

[Detailed description of the invention]

[0001]

The toroidal type continuously variable transmission according to the present invention is used, for example, as a transmission for an automobile.

[0002]

2. Description of the Related Art The use of a toroidal-type continuously variable transmission as schematically shown in FIGS. This toroidal type continuously variable transmission supports an input disk 2 concentrically with an input shaft 1 and an output disk 4 at an end of an output shaft 3 as disclosed in, for example, Japanese Utility Model Application Laid-Open No. 62-71465. It is fixed. An inner surface of a casing containing the toroidal-type continuously variable transmission or a support bracket provided in the casing has a pivot that is twisted with respect to an extension of the central axis of the input shaft 1 and the output shaft 3. Trunnion 5 swinging around (not shown) ,
5 are provided. That is, each of these trunnions 5, 5
In the axial direction (front and back directions in FIGS. 2 and 3)
The above-mentioned pivots are protruded concentrically, and each of the above-mentioned
The trunnions 5 and 5 are swingably displaceable.

Each of the trunnions 5, 5 is made of a metal material having sufficient rigidity, and the pivots are provided on outer surfaces of both ends. Power rollers 7 are provided around displacement shafts 6 provided at the center of each trunnion 5, respectively.
7 is rotatably supported. The power rollers 7 are sandwiched between the input and output disks 2 and 4.

The inner surfaces 2a and 4a of the input and output disks 2 and 4 which are opposed to each other have a concave cross-section having a circular arc centered on the pivot. Then, the peripheral surface 7a of each of the power rollers 7, 7 formed on the spherical convex surface,
7a is in contact with the inner side surfaces 2a, 4a.

A loading device 8 of a loading cam type is provided between the input shaft 1 and the input disk 2, and the input disk 2 is connected to the output disk 4 by the pressing device 8.
Elastically. The pressurizing device 8 includes a cam plate 9 that rotates together with the input shaft 1, and a plurality (for example, four) of rollers 11, 11 held by a holder 10. On one side surface (the right side surface in FIGS. 2 and 3) of the cam plate 9, a cam surface 12 which is a concave and convex surface extending in the circumferential direction is formed, and the outer surface of the input disk 2 (see FIGS. A similar cam surface 13 is also formed on the left side). The plurality of rollers 11, 11 are rotatable about an axis in a radial direction with respect to the center of the input shaft 1.

When the cam plate 9 rotates with the rotation of the input shaft 1 constituting the toroidal-type continuously variable transmission as described above, a plurality of rollers 11, 11 are formed by the cam surface 12.
The input disk 2 is pressed against the cam surface 13 on the outer surface. As a result, the input disk 2 is pressed by the plurality of power rollers 7, 7 and at the same time, the pair of cam surfaces 12,
13 and a plurality of rollers 11, 11 based on meshing,
The input disk 2 rotates. Then, the rotation of the input disk 2 is transmitted to the output disk 4 via the plurality of power rollers 7, 7, and the output shaft 3 fixed to the output disk 4 rotates.

When the rotation speed of the input shaft 1 and the output shaft 3 is changed, and when the deceleration is first performed between the input shaft 1 and the output shaft 3, as shown in FIG. 5 and 5 are swung so that the peripheral surface 7 of each power roller 7
The displacement shafts 6, 6 are inclined so that a, 7a abut the center portion of the inner surface 2a of the input disk 2 and the outer portion of the inner surface 4a of the output disk 4, respectively.

Conversely, when increasing the speed, the trunnions 5, 5 are swung as shown in FIG. 3 so that the peripheral surfaces 7a, 7a of the power rollers 7, 7 Each of the displacement shafts 6 is tilted so as to abut against the outer peripheral portion of 2a and the central portion of the inner surface 4a of the output disk 4, respectively.

The inclination angles of the displacement shafts 6, 6 are shown in FIGS.
, An intermediate speed ratio can be obtained between the input shaft 1 and the output shaft 3.

Further, in order to increase the power that can be transmitted by the toroidal type continuously variable transmission constructed and operated as described above, a toroidal type continuously variable transmission as shown in FIGS.
On the other hand, arrangement in parallel (in tandem) with respect to the power transmission direction has been conventionally proposed, as disclosed in Japanese Patent Application Laid-Open No. 2-163549. FIG. 4 shows a structure in which a pair of toroidal-type continuously variable transmissions described in this publication are arranged in tandem.

Reference numeral 14 denotes a cylindrical torque transmitting shaft. A needle bearing 22 is provided between an inner peripheral surface of one end (left end in FIG. 4) of the torque transmitting shaft 14 and an outer peripheral surface of an end of the input shaft 1. The torque transmission shaft 14 is arranged concentrically with the input shaft 1, and the input shaft 1 and the torque transmission shaft 14 are rotatable independently of each other.

A pair of input disks 2, 2 are provided around the torque transmission shaft 14 with a space therebetween. Inner peripheral edge of each input disk 2, 2 and torque transmission shaft 14
Ball splines 15 and 15 are provided between the outer peripheral surface 14a and the input discs 2 and 2, respectively. The input discs 2 and 2 cannot rotate with respect to the torque transmission shaft 14 with respect to the torque transmission shaft 14. The shaft 14 is supported so that it can be displaced in the axial direction (the left-right direction in FIG. 4).
Also, the inner surfaces 2a, 2a of the input disks 2, 2 are concave surfaces having a circular cross section, respectively.

A pair of output disks 4, 4 are provided between the pair of input disks 2, 2 so as to freely rotate and axially displace with respect to the torque transmission shaft 14. The inner surfaces 4a and 4a of the output disks 4 and 4 (in the present specification, the inner surfaces of the disks 2 and 4 mean the side surfaces of the disks 2 and 4 facing each other). It has a concave surface.

In the portion between the output disks 4, 4,
A ring-shaped output gear 18 is provided. The output gear 18 is fixedly provided on an outer peripheral surface of an intermediate portion of a cylindrical sleeve 19. The sleeve 19 is supported on the outer peripheral surface of the intermediate portion of the torque transmission shaft 14 so as to rotate with respect to the torque transmission shaft 14 and to be slightly displaceable in the axial direction. The pair of output disks 4 and 4 are spline-engaged with the outer peripheral surfaces of both ends of the sleeve 19.

A cam plate 9 is provided at one end of the torque transmission shaft 14.
Are rotatably supported via thrust ball bearings 16. The cam plate 9 and the input shaft 1 are connected to a flange plate 17.
The cam plate 9 rotates together with the input shaft 1 by the coupling. Then, between the cam surface 12 formed on the inner side surface (the right side surface in FIG. 4) of the cam plate 9 and the cam surface 13 formed on the outer side surface of one input disk 2 (the left side in FIG. 4).
A plurality of rollers 1 rotatably held by a holder 10
1, and constitutes a pressure device 8 that presses one of the input disks 2 in a direction away from the cam plate 9 in the axial direction of the torque transmission shaft 14.

The other side which does not face the pressurizing device 8 (FIG. 4)
A stopper 20 and a disc spring 21 are provided between the input disk 2 (to the right of FIG. 2) and the torque transmission shaft 14 to prevent the input disk 2 from moving away from the pressurizing device 8. This constitutes a restricting stopper means.

Further, between the inner surfaces 2a, 2a of the pair of input disks 2, 2, and the inner surfaces 4a, 4a of the pair of output disks 4, 4, a twist is formed with respect to the torque transmitting shaft 14. a trunnion which swings about a pivot (not shown) in the position, the peripheral surface 7a and a spherical convex surface, a plurality of power rollers rotatably supported on the displacement shaft 6 supported by the trunnion 5 7 are provided. That is, these
Both ends of each trunnion 5, 5 in the axial direction (front and back directions in FIG. 4)
At the center, the above-mentioned pivots are protruded concentrically with each other.
The trunnions 5, 5 can be freely displaced as a center.
I have. Then, based on the pressing force of the pressurizing device 8, the peripheral surface 7a of each power roller 7 is brought into contact with the input, output, and the inner side surfaces 2a, 4a of the disks 2, 4.

In the structure having a pair of toroidal-type continuously variable transmissions configured as described above, the rotational torque input from one input shaft 1 is applied to the flange plate 1.
7, the cam plate 9 and the pressure device 8 are transmitted to one of the input disks 2.
Rotate with. Then, with the rotation of the torque transmission shaft 14, the other input disk 2 also rotates in synchronization with the one input disk 2.

The rotational movement of the pair of input disks 2, 2, which rotates synchronously via the torque transmission shaft 14, is transmitted via a plurality of power rollers 7 to the pair of output disks 4, 2.
4 to rotate the sleeve 19 in which the two output disks 4 and 4 are splined. Then, the rotational movement of the sleeve 19 is taken out by the output gear 18.

[0020]

[Problems to be Solved by the Invention] The toroidal type continuously variable transmission of the present invention reduces the generation of vibration and noise during use by improving the weight balance while considering the case of being incorporated into an actual car. It is to suppress.

When the transmission is incorporated into a front-engine rear-wheel drive vehicle, the rear end of the crankshaft of the engine and the front end of the propeller shaft are located on substantially the same straight line. It is preferred that the parts are arranged substantially evenly around the straight line.

On the other hand, in the case of a structure in which a pair of toroidal-type continuously variable transmissions as shown in FIG. 4 is arranged in tandem, the input shaft 1 communicating with the crankshaft and the output shaft communicating with the propeller shaft are directly used. Cannot be arranged on the same straight line. That is, the take-out shaft to which the gear meshing with the output gear 18 is fixed is located laterally from the extension of the input shaft 1,
It is unavoidable that the output gear 18 is shifted by a total distance of the radius of the gear and the radius of the gear. Therefore, when the take-out shaft is used as it is as the output shaft, the rear end of the crankshaft of the engine and the front end of the propeller shaft cannot be located on the same straight line.

For this reason, conventionally, for example,
The input shaft 1 and the output shaft are arranged concentrically, and the front end of the output shaft and the rear end of the take-out shaft are connected by gears. That is, as shown in FIG. 5, two take-out shafts 23, 23 are arranged in parallel to the input shaft 1 beside the input shaft 1, and are fixed to the front ends of the take-out shafts 23, 23. Gear 2
4 and 24 are meshed with the output gear 18.

On the other hand, the gears 25 fixed to the rear ends of the take-out shafts 23 are engaged with the gears 27 fixed to the front end of the output shaft 26. With this configuration, torque can be transmitted between the input shaft 1 and the output shaft 26 that are arranged concentrically with each other. Note that the pair of input data
Disks 2 and 2 are splines around both ends of the input shaft 1.
The input shaft 1 is rotatable together with the input shaft 1.
The center of the outer surface of the input disk 2 on the right side of FIG.
Abutting against the end surface of the inner ring of the rolling bearing through
Prevents displacement of output disks 4 and 4 in the direction of retreat
ing. On the other hand, outside the input disk 2 on the left side in FIG.
The central part of the side surface of the rolling bearing is
Large thrust load is applied to the inner ring end face
In case of evacuation from each of the output disks 4, 4,
A slight displacement in the direction is allowed. The disc spring
The peripheral surfaces 7a, 7a of the power rollers 7, 7 and the respective
A preload is applied to the contact portions of the disks 2 and 4 with the inner surfaces 2a and 4a.
Provided to give.

However, in the case of the structure shown in FIG. 5, since the transmission mechanism by the gears 25 and 27 is provided at the rear end of the transmission, it is inevitable that the rear end of the transmission becomes heavy.
When assembling the transmission to an automobile, the front end of the transmission is connected to the rear end of the engine. Therefore, the rear end of the transmission is a free end, but if the rear end is heavy, vibration and noise tend to increase during operation of the engine, which is not preferable. In addition, in the case of the structure shown in FIG. 5, it is difficult to make the centers of the input disks 2, 2 and the output disks 4, 4 coincide with the centers of the power rollers 7, 7, so that sufficient transmission efficiency is not necessarily obtained. I can't get it.

That is, with the operation of the transmission, each roller 1
If 1, 11 presses the outer surface of the output disks 4, 4, the input disk 2 and output disk 4 provided on the left side of FIG. 5, by squeezing the disc spring, to the left in FIG. Move slightly. As a result, the center of curvature of the inner surfaces 2a, 4a of the disks 2, 4 and the inner surfaces 2a, 4a
The center of curvature of the power roller 7 with which the peripheral surface 7a abuts is displaced, and the contact state of the surfaces 2a, 4a, 7a becomes poor, and the transmission efficiency between the input disk 2 and the output disk 4 becomes poor. Will get worse.

The toroidal-type continuously variable transmission of the present invention has been devised in view of the above-mentioned circumstances.

[0028]

The toroidal-type continuously variable transmission according to the present invention includes a casing, a fixed partition provided inside the casing, a through hole provided in a part of the partition, and An input shaft rotatably supported in the casing, a drive gear fixed to the input shaft, and an input shaft which is disposed in parallel with the input shaft in the casing with a center portion of the through hole inserted therethrough; An output shaft that is rotatable independently of the shaft, and the inner surface of each is an arc-shaped concave surface,
A pair of output disks fixed at intervals around the output shaft, a portion between the pair of output disks, and
An inner rotating cylinder rotatably supported around the output shaft at an inner portion of the through hole, and at both ends of the inner rotating cylinder,
A pair of input discs supported so as to be freely displaceable in the axial direction with respect to the inner rotary cylinder, and a portion between the pair of input discs and an inner portion of the through hole, which rotates around the inner rotary cylinder. An outer rotating cylinder freely supported, a rolling bearing provided between the outer rotating cylinder and the partition wall for supporting a radial load and a thrust load applied to the outer rotating cylinder, and an outer periphery of an intermediate portion of the outer rotating cylinder. Fixed on the surface,
A driven gear meshing with the driving gear, and both ends of the outer rotary cylinder are supported so as to be freely displaceable only in the axial direction of the outer rotary cylinder, and one side thereof is provided on the outer surface of the pair of input disks. A pair of cam plates opposed to each other, a cam surface formed on at least one side surface of one side surface of each cam plate and the outer side surface of the pair of input discs, the cam surface being circumferentially uneven. A plurality of rollers arranged radially between one side surface of each of the cam plates and the outer side surfaces of the pair of input disks; a portion fixed to the outer rotary cylinder and the other of the respective cam plates; A pair of elastic members provided between the input side and the input disk, and swinging about a pivot which is twisted with respect to the input shaft and the output shaft; A plurality of trunnions and a peripheral surface are made into spherical convex surfaces, and each Is rotatably supported by the supporting displacement shaft trunnion includes input, output, and a plurality of power rollers interposed between each disk.

[0029]

In the case of the toroidal type continuously variable transmission of the present invention configured as described above, when the input shaft is rotated, the outer rotating cylinder and both ends of the outer rotating cylinder are driven via the driving gear and the driven gear. Is rotated by the pair of cam plates supported by the pair. The rotation of the cam plate is transmitted to a pair of input disks supported at both ends of the inner rotating cylinder via a plurality of rollers.

Since the pair of input disks is supported at both ends of the inner rotating cylinder so as to be freely displaceable only in the axial direction, the two input disks rotate in synchronization with each other.
Also, the radial load and the thrust load applied to the outer rotating cylinder are supported by the partition wall through the rolling bearing,
The position of the outer rotating cylinder does not shift not only in the diameter direction but also in the axial direction.

Based on the operation of the pressing device including the above rollers, the pair of input disks are pressed by a plurality of power rollers, and together with the inner rotating cylinder,
Rotates around the output shaft. As a result, the plurality of power rollers rotate around the displacement axis while pressing the respective peripheral surfaces against the inner surfaces of the input disk and the output disk, and rotate the pair of input disks to the outer periphery of the output shaft. Transmit to a pair of output disks fixed to the surface. As a result,
The output shaft rotates.

The output disks do not move while being fixed at predetermined positions on the outer peripheral surface of the output shaft. Therefore, even when the pair of input disks is pressed against each output disk via a plurality of power rollers, the axial position of each input disk does not deviate from a desired position. Therefore, the torque transmission between each input disk and each output disk can always be efficiently performed.

When changing the gear ratio between the input shaft and the output shaft, the inclination angle of the displacement shaft is changed by swinging the trunnion about the pivot shaft, as in the case of the above-described conventional device.

In the case of the toroidal type continuously variable transmission of the present invention configured as described above, the main components such as the input and output, both disks, trunnions, and power rollers can be arranged around the output shaft. Therefore, the front end of the propeller shaft can be directly connected to the rear end of the output shaft without passing through the gear transmission mechanism. Therefore, the weight of the rear end of the toroidal type continuously variable transmission does not increase, and when the toroidal type continuously variable transmission is incorporated in a vehicle, the weight of the rear end which is a free end can be reduced. As a result, noise and vibration generated during operation can be suppressed low.

[0035]

FIG. 1 shows an embodiment of the present invention. A fixed partition wall 28 is provided inside a casing (not shown) that houses components of the toroidal-type continuously variable transmission. In the case of the illustrated embodiment, the partition wall 28 is a double wall. A circular through hole 29 is provided in a part of the partition wall 28.

On the other hand, an input shaft 1 is provided in the casing.
A rolling bearing (not shown) is supported so as to be rotatable only (displaceable in the axial direction), and a drive gear 30 is fixed to an intermediate portion of the input shaft 1. In the casing, an output shaft 31 is supported by a rolling bearing (not shown) so that the output shaft 31 can rotate only in a direction parallel to the input shaft 1 and independently of the input shaft 1 (no displacement in the axial direction). I have. The intermediate portion of the output shaft 31 passes through the center of the through hole 29.

At the intermediate portion of the output shaft 31, the partition 28
A pair of output discs 4, 4 each having an inner surface 4a, 4a having an arc-shaped concave surface at two positions sandwiching the
Are fixed with a space between each other and with the inner side surfaces 4a, 4a facing each other.

The outer peripheral surface of the intermediate portion of the output shaft 31
The portion between the pair of output disks 4 and 4 and the through hole 29
The inner rotating cylinder 32 is rotatably supported on the inner part of the inner cylinder via a pair of needle bearings 33, 33. A pair of input disks 2, 2 are supported at both ends of the inner rotary cylinder 32 so that only the displacement in the axial direction (left-right direction in FIG. 1) with respect to the inner rotary cylinder 32 is free.

That is, male spline grooves 35 are formed on the outer peripheral surfaces of both ends of the inner rotary cylinder 32, respectively. On the other hand, in the annular concave portions 36, 36 formed at the outer peripheral inner end of each of the input disks 2, 2, female spline grooves 37, 37 are formed on the respective inner peripheral surfaces.
8, 38 are fixed inside. Then, steel balls 39, 39 are interposed between the male spline grooves 35, 35 and the female spline grooves 37, 37, so that both ends of the inner rotary cylinder 32 and the input disks 2, 2 are interposed. Are provided with ball splines 40, 40. Accordingly, the input disks 2 are smoothly displaced in the axial direction of the inner rotary cylinder 32, but do not rotate relative to the inner rotary cylinder 32. That is, the pair of input disks 2, 2 rotates synchronously via the inner rotary cylinder 32.

Needle bearings 34 are provided between the inner peripheral surfaces of the input disks 2 and 2 and the outer peripheral surface of the output shaft 31, respectively. And relative rotation is free.

An outer rotating cylinder 41 is rotatably supported around the inner rotating cylinder 32 via needle bearings 42, 42. The outer rotating cylinder 41 is located inside the through hole 29 between the pair of input disks 2 and 2.

On the outer peripheral surface of the intermediate portion of the outer rotary cylinder 41,
A driven gear 43 meshing with the driving gear 30 is provided integrally, and the driven gear 43 is rotatable inside the double wall as the partition wall 28. On the outer peripheral surface of the outer rotating cylinder 41, the inner ring 4 constituting the angular type ball bearings 44, 44 is located at a position sandwiching the driven gear 43.
5, 45 are externally fitted and fixed. Also, each ball bearing 44, 44
The outer races 46, 46 are fixedly fitted in locking step portions 47, 47 formed on the inner peripheral edge of the through hole 29, respectively. As a result, the radial load and the thrust load applied to the outer rotating cylinder 41 are reduced by the pair of ball bearings 44, 44.
Supported by

A pair of cam plates 9 and 9 are supported at both ends of the outer rotary cylinder 41 so as to be freely displaceable in the axial direction of the outer rotary cylinder 41, respectively. That is, the male spline grooves 4 formed on the outer peripheral surfaces of both ends of the outer rotary cylinder 41
8 and 48 are engaged with female spline grooves 49 and 49 formed on the inner peripheral surface of each of the cam plates 9 and 9. Therefore,
The cam plates 9 and 9 are displaced in the axial direction of the outer rotating cylinder 41 but do not rotate relative to the outer rotating cylinder 41. That is, the pair of cam plates 9, 9 rotate synchronously via the outer rotary cylinder 41.

Also, one side surface of each of the cam plates 9, 9 and the one
On the outer surfaces of the pair of input disks 2, 2, cam surfaces 12, 13 which are uneven in the circumferential direction are formed, and a plurality of rollers 1 are provided between the two cam surfaces 12, 13.
The pressurizing device 8 is configured by arranging 1, 1 in the radial direction. An inner ring 45 externally fitted and fixed to the outer rotary cylinder 41;
A pair of disc springs 50, 50 and thrust needle bearings 51, 51, which are elastic members, are provided between the cam plate 9 and the other side surfaces of the cam plates 9, 9, respectively. , 9 are pressed against the outer surfaces of the input disks 2, 2.

Further, around the output shaft 31, between the pair of input disks 2, 2 and the output disks 4, 4, a portion twisted with respect to the input shaft 1 and the output shaft 31 is provided. A plurality of trunnions 5, 5 are provided that oscillate about a pivot (not shown). That is, each of these trani
At the center of both ends of the ON and 5, 5 axial directions (front and back directions in FIG. 1)
Protruding the pivots concentrically with each other, with this pivot as the center
Each of the trunnions 5, 5 is swingably displaceable. A plurality of power rollers 7, 7 having a peripheral surface 7a having a spherical convex surface are rotatably supported on displacement shafts 6, 6, which are supported by the trunnions 5, 5, respectively. 7 is sandwiched between the input and output disks 2 and 4.

In the case of the toroidal type continuously variable transmission of the present invention configured as described above, when the input shaft 1 is rotated, the outer rotary cylinder 41 and the driven rotary gear 43 are driven via the drive gear 30 and the driven gear 43. The pair of cam plates 9 and 9 supported at both ends of the outer rotary cylinder 41 are rotated. The rotation of the cam plates 9, 9 is performed by a plurality of rollers 11,
The power is transmitted to a pair of input disks 2, 2 supported at both ends of the inner rotary cylinder 32 through the input disk 11. Since the pair of input disks 2 and 2 are supported at both ends of the inner rotary cylinder 32 so as to be freely displaceable only in the axial direction, the input disks 2 and 2 rotate in synchronization with each other. .

The outer rotary cylinder 41 is supported on the partition wall 28 by the pair of ball bearings 44, 44.
Even when a helical gear is used as the drive gear 30 and the driven gear 43 and the axial force is applied to the outer rotary cylinder 41, the outer rotary cylinder 41 is shifted in the axial direction. Nothing. Therefore, the pair of cam plates 9, 9
Is transmitted to the pair of input disks 2 and 2 under the same conditions, and a large torsional stress is applied to the inner rotary cylinder 32 based on the difference between the rotational forces transmitted to the input disks 2 and 2. I will not join.

As described above, the plurality of rollers 11, 1
Each of the input disks 2, 2 is pressed by a plurality of power rollers 7, 7 together with the inner rotating cylinder 32 around the output shaft 31 based on the action of the pressure devices 8, 8 including As a result, the plurality of power rollers 7, 7 press against the respective peripheral surfaces 7a, 7a and the inner surfaces 2a, 4a of the input disks 2, 2, and the output disks 4, 4, while the respective displacement shafts Rotate around 6,6.
As a result, the rotation of the pair of input disks 2, 2 causes the pair of output disks 4, 4
And the output shaft 31 rotates.

Since each of the output disks 4, 4 does not move while being fixed at a predetermined position on the outer peripheral surface of the output shaft 31, the pair of input disks 2, 2 are connected to a plurality of power rollers 7, 7, respectively. , The axial position of each input disk 2, 2 is
There is no deviation from the desired position. Therefore, the rotational force transmission between each input disk 2, 2 and each output disk 4, 4,
It can always be done efficiently.

When the gear ratio is changed between the input shaft 1 and the output shaft 31, the trunnions 5, 5 are swung about a pivot, as in the case of the above-described conventional device, so that the displacement is changed. The inclination angles of the shafts 6, 6 are changed, and the peripheral surfaces 7a, 7a of the power rollers 7, 7, which are pivotally supported by the respective displacement shafts 6, 6, and the inner surfaces 2 of the input disks 2, 2, and the output disks 4, 4,
a, 4a.

In the case of the toroidal-type continuously variable transmission of the present invention configured as described above, the input, output,
Main parts such as the two disks 2 and 4, the trunnions 5 and 5, and the power rollers 7 and 7 can be arranged. Therefore, as in the conventional structure shown in FIG. 5, the front end of the propeller shaft can be directly connected to the rear end of the output shaft 26 without using a gear transmission mechanism. Therefore, the weight of the rear end of the toroidal-type continuously variable transmission does not increase, and when the toroidal-type continuously variable transmission is incorporated in a vehicle, the weight of the rear end, which is the free end, can be reduced. As a result, noise and vibration generated during operation can be suppressed low.

That is, when an automobile transmission is constructed using the toroidal type continuously variable transmission of the present invention, the output shaft 31 is arranged on a line connecting the crankshaft of the engine and the propeller shaft constituting the drive system. . As a result, the input shaft 1 is shifted laterally from an extension of the crankshaft, so that a gear transmission mechanism or the like provided near the front end of the toroidal-type continuously variable transmission, that is, near the joint between the engine and the transmission,
The torque of the crankshaft is transmitted to the input shaft 1.

Even if the weight of the front end near the joint between the engine and the transmission is slightly increased, the transmission will not vibrate or generate noise during operation of the engine.

[0054]

The toroidal-type continuously variable transmission according to the present invention is constructed and operates as described above, so that a practical automotive transmission with reduced vibration and noise during operation can be obtained. Can be

[Brief description of the drawings]

FIG. 1 is a sectional view showing an embodiment of the present invention.

FIG. 2 is a side view showing a basic structure of the toroidal-type continuously variable transmission in a state of maximum deceleration.

FIG. 3 is a side view similarly showing a state at the time of maximum acceleration.

FIG. 4 is a sectional view showing a first example of a conventional structure.

FIG. 5 is a sectional view showing a second example.

[Explanation of symbols]

 Reference Signs List 1 input shaft 2 input disk 2a inner surface 3 output shaft 4 output disk 4a inner surface 5 trunnion 6 displacement shaft 7 power roller 7a peripheral surface 8 pressing device 9 cam plate 10 retainer 11 roller 12 cam surface 13 cam surface 14 torque transmission Shaft 14a Outer peripheral surface 15 Ball spline 16 Thrust ball bearing 17 Flange plate 18 Output gear 19 Sleeve 20 Stopper 21 Disc spring 22 Needle bearing 23 Take-out shaft 24, 25 Gear 26 Output shaft 27 Gear 28 Partition wall 29 Through hole 30 Drive gear 31 Output Shaft 32 Inner rotating cylinder 33, 34 Needle bearing 35 Male spline groove 36 Annular recess 37 Female spline groove 38 Ring body 39 Steel ball 40 Ball spline 41 Outer rotating cylinder 42 Needle bearing 43 Follower gear 44 Ball bearing 45 Inner ring 46 Outer ring 47 Engagement Step 48 male Line groove 49 female spline grooves 50 servings plate springs 51 thrust needle bearing

Claims (1)

(57) [Scope of request for utility model registration] 1. A casing, a fixed partition provided inside the casing, a through hole provided in a part of the partition, an input shaft rotatably supported in the casing, and an input shaft. A drive gear fixed to a shaft, and an output shaft which is arranged in parallel with the input shaft and is rotatable independently with respect to the input shaft, in the casing with the center portion of the through hole inserted therethrough; A pair of output disks fixed at intervals around the output shaft, a portion between the pair of output disks, and an inner portion of the through hole; An inner rotating cylinder rotatably supported around the output shaft; and a pair of input disks supported at both ends of the inner rotating cylinder so as to be freely displaceable in an axial direction with respect to the inner rotating cylinder. A portion between the pair of input disks, and An outer rotating cylinder rotatably supported around the inner rotating cylinder at an inner portion of the through-hole; and a radial load and thrust provided between the outer rotating cylinder and the partition wall, the radial load being applied to the outer rotating cylinder. A rolling bearing for supporting a load, a driven gear fixed to an outer peripheral surface of an intermediate portion of the outer rotary cylinder and meshing with the drive gear, and extending at both ends of the outer rotary cylinder in an axial direction of the outer rotary cylinder. A pair of cam plates, one side of which is opposed to the outer surface of the pair of input disks, and one side of each cam plate and the outer surface of the pair of input disks. A plurality of radially extending cam surfaces formed on at least one side surface of the cam surface, the concave and convex portions extending in the circumferential direction, between one side surface of each of the cam plates and the outer side surfaces of the pair of input disks. And the outer rotation A pair of elastic members provided between a portion fixed to the cylinder and the other side surface of each of the cam plates and pressing each of the cam plates toward each of the input disks; A plurality of trunnions swinging about a pivot at the torsion position, and a spherical convex surface on the circumferential surface, rotatably supported by a displacement shaft supported by each trunnion, between input, output, and each disk A toroidal-type continuously variable transmission including a plurality of power rollers sandwiched between.