JP6528359B2 - Toroidal type continuously variable transmission - Google Patents

Description

  The present invention relates to a toroidal continuously variable transmission that can be used as a transmission for automobiles and various industrial machines.

For example, a double cavity type toroidal continuously variable transmission used as a transmission for an automobile is configured as shown in FIG. 5 and FIG. As shown in FIG. 5, the input shaft 1 is rotatably supported inside the casing 50, and on the outer periphery of the input shaft 1, two input side disks 2, 2 and two output side disks 3, 3 and is attached. Further, an output gear (transmission gear) 4 is rotatably supported on the outer periphery of the middle portion of the input shaft 1. The output side disks 3 and 3 are connected to the cylindrical flanges 4a and 4a provided at the center of the output gear 4 by spline connection.
The input shaft 1 is rotationally driven by the drive shaft 22 via a loading cam type pressing device 12 provided between the input side disk 2 positioned on the left side in FIG. 5 and the cam plate (loading cam) 7. It is supposed to be. In addition, the output gear 4 is supported in the casing 50 via a partition wall 13 configured by coupling of two members, and thereby, can rotate around the axis O of the input shaft 1, while the axis O Directional displacement is blocked.

  The output side disks 3, 3 are rotatably supported centering on the axis O of the input shaft 1 by needle bearings 5, 5 interposed between the output side disks 3 and 3. Further, the input side disc 2 on the left side in FIG. 5 is supported by the input shaft 1 via a ball spline 6, and the input side disc 2 on the right side in FIG. 5 is splined to the input shaft 1 The disk 2 is adapted to rotate with the input shaft 1. In addition, a power roller is provided between the inner side surfaces (concave; also referred to as traction surface) 2a, 2a of the input side disks 2, 2 and the inner side surfaces (concave; also referred to as traction surfaces) 3a, 3a of the output disks 3, 3. 11 (see FIG. 6) are rotatably held.

  A stepped portion 2b is provided on the inner peripheral surface 2c of the input side disk 2 positioned on the right side in FIG. 5, and the stepped portion 1b provided on the outer peripheral surface 1a of the input shaft 1 abuts on the stepped portion 2b. At the same time, the rear surface (right surface in FIG. 5) of the input side disk 2 is abutted against a loading nut 9 screwed on a screw formed on the outer peripheral surface of the input shaft 1. Thereby, the displacement of the input disk 2 in the direction of the axis O with respect to the input shaft 1 is substantially prevented. Further, a disc spring 8 is provided between the cam plate 7 and the flange portion 1 d of the input shaft 1, and the disc spring 8 has concave surfaces 2 a, 2 a, 3 a of the respective disks 2, 2, 3, 3. , 3a and a contact portion between the peripheral surfaces 11a and 11a of the power rollers 11 and 11, a pressing force (preload) is applied.

  6 is a cross-sectional view taken along the line A-A of FIG. As shown in FIG. 6, inside the casing 50, a pair of trunnions 15, 15 swinging around a pair of pivots 14, 14 in a twisted position relative to the input shaft 1 are provided. In FIG. 6, the illustration of the input shaft 1 is omitted. Each of the trunnions 15, 15 is a pair of bent wall portions 20, 20 formed at both end portions in the longitudinal direction (vertical direction in FIG. 6) of the support plate portion 16 so as to be bent toward the inner side surface of the support plate portion 16. have. A concave pocket portion P for accommodating the power roller 11 is formed in each of the trunnions 15, 15 by the bent wall portions 20, 20. The pivots 14 and 14 are provided concentrically with each other on the outer surface of each of the bent wall portions 20 and 20.

  A circular hole 21 is formed in the central portion of the support plate portion 16, and a base end 23 a of the displacement shaft 23 is supported by the circular hole 21. The tilt angles of the displacement shafts 23 supported at the central portions of the trunnions 15, 15 can be adjusted by swinging the trunnions 15, 15 about the pivots 14, 14, respectively. In addition, each power roller 11 is rotatably supported around the tip 23 b of the displacement shaft 23 protruding from the inner side surface of each trunnion 15, 15, and each power roller 11 is a disk on each input side 2, 2 and each output side disc 3, 3 are held. The proximal end 23a and the distal end 23b of each displacement shaft 23, 23 are eccentric to each other.

  The pivot shafts 14 and 14 of the trunnions 15 and 15 are respectively swingably supported on the pair of yokes 23A and 23B and displaceable in the axial direction (vertical direction in FIG. 6). The horizontal movement of trunnions 15, 15 is restricted by 23B. Each yoke 23A, 23B is formed in a rectangular shape by pressing or forging a metal such as steel. Four circular support holes 18 are provided at the four corners of each of the yokes 23A and 23B, and pivot shafts 14 provided at both ends of the trunnion 15 are respectively pivoted through the radial needle bearings 30 in these support holes 18 It is freely supported. Further, a circular locking hole 19 is provided at the central portion in the width direction (left and right direction in FIG. 6) of the yokes 23A and 23B, and the inner peripheral surface of the locking hole 19 is a cylindrical surface. 64, 68 are fitted inside. That is, the upper yoke 23A is swingably supported by the spherical post 64 supported by the casing 50 via the fixing member 52, and the lower yoke 23B is a spherical post 68 and a drive for supporting the same. It is pivotally supported by the upper cylinder body 61 of the cylinder 31.

  The displacement shafts 23 and 23 provided in the trunnions 15 and 15 are provided at positions 180 degrees opposite to each other with respect to the input shaft 1. Further, the direction in which the distal end portion 23b of each displacement shaft 23, 23 is eccentric with respect to the base end portion 23a is the same direction with respect to the rotational direction of both the disks 2, 2, 3 and 3 (in FIG. In the opposite direction). In addition, the eccentric direction is a direction substantially orthogonal to the arrangement direction of the input shaft 1. Therefore, each power roller 11 is supported so as to be slightly displaceable in the longitudinal direction of the input shaft 1. As a result, even if each power roller 11, 11 tends to be displaced in the axial direction of the input shaft 1 due to elastic deformation or the like of each component based on the thrust load generated by the pressing device 12, each configuration This displacement is absorbed without applying an excessive force to the member.

  Further, between the outer surface of the power roller 11 and the inner surface of the support plate portion 16 of the trunnion 15, a thrust ball bearing (thrust bearing) 24 and a thrust rolling bearing are sequentially arranged from the outer surface side of the power roller 11. And thrust needle bearings 25 are provided. Among these, the thrust ball bearings 24 allow the rotation of each power roller 11 while supporting the load in the thrust direction applied to each power roller 11. Each of such thrust ball bearings 24 has a plurality of balls (hereinafter referred to as rolling elements) 26, 26 and an annular cage 27 for rollingly holding the rolling elements 26, 26, and a circle. It comprises an annular outer ring 28. Further, the inner ring raceway of each thrust ball bearing 24 is formed on the outer side surface (large end face) of each power roller 11, and the outer ring raceway is formed on the inner side surface of each outer ring 28.

  Further, the thrust needle bearing 25 is sandwiched between the inner side surface of the support plate portion 16 of the trunnion 15 and the outer side surface of the outer ring 28. The thrust needle bearing 25 supports the thrust load applied from the power roller 11 to the outer rings 28 and causes the power roller 11 and the outer ring 28 to swing around the proximal end 23 a of each displacement shaft 23. Tolerate.

  Furthermore, drive rods (trunnion shafts) 29, 29 are provided at one end (lower end in FIG. 6) of each trunnion 15, 15, and a drive piston (an outer peripheral surface between the drive rods 29, 29) is provided. Hydraulic pistons 33, 33 are fixed. Each of the drive pistons 33, 33 is oil-tightly fitted in a drive cylinder 31 formed of an upper cylinder body 61 and a lower cylinder body 62. The drive pistons 33, 33 and the drive cylinder 31 constitute a drive device 32 for displacing the trunnions 15, 15 in the axial direction of the pivot shafts 14, 14 of the trunnions 15, 15.

  In the case of the toroidal type continuously variable transmission configured as described above, the rotation of the input shaft 1 is transmitted to the input side disks 2 via the pressing device 12. Then, the rotation of the input side disks 2 and 2 is transmitted to the output side disks 3 and 3 via the pair of power rollers 11 and 11, and the rotation of the output side disks 3 and 3 is output to the output gear 4. It is taken out.

When changing the rotational speed ratio between the input shaft 1 and the output gear 4, the drive pistons 33, 33 are displaced in opposite directions. With the displacement of the drive pistons 33, the pair of trunnions 15, 15 are displaced in opposite directions. For example, the power roller 11 on the left side of FIG. 6 is displaced downward, and the power roller 11 on the right side of FIG. 6 is displaced upward.
As a result, it acts on the contact portions between the circumferential surfaces 11a and 11a of the power rollers 11 and the inner side surfaces 2a 2a 3a and 3a of the input side disks 2 and 2 and the output side disks 3 and 3, respectively. The direction of the tangential force changes. Then, with the change in the direction of the force, the trunnions 15, 15 swing (tilt) in opposite directions with respect to the pivots 14, 14 pivotally supported by the yokes 23A, 23B.

  As a result, the contact positions of the circumferential surfaces 11a, 11a of the power rollers 11, 11 and the inner side surfaces 2a, 3a change, and the rotational speed ratio between the input shaft 1 and the output gear 4 changes. In addition, when the torque transmitted between the input shaft 1 and the output gear 4 fluctuates and the amount of elastic deformation of each component changes, the power rollers 11, 11 and the outer rings attached to the power rollers 11, 11 28, 28 slightly pivot about the proximal ends 23a, 23a of the respective displacement axes 23, 23. Since the thrust needle bearings 25 and 25 exist between the outer surface of each of the outer rings 28 and 28 and the inner surface of the support plate portion 16 constituting each of the trunnions 15 and 15, respectively, the rotation smoothly proceeds. It will be. Therefore, as described above, the force for changing the inclination angle of each displacement shaft 23, 23 may be small.

In the above-described toroidal type continuously variable transmission, power is transmitted by an output gear (transmission gear) 4 separate from the output-side disc 3. For example, as shown in Patent Document 1 and FIG. In some cases, a gear for transmitting power (peripheral gear) 4A may be provided on the outer peripheral surface of the integrated output side disk 3A in which the output side disks 3 and 3 are integrally formed.
In the toroidal continuously variable transmission shown in FIG. 7, the same components as those of the toroidal continuously variable transmission shown in FIG.

  Such a toroidal type continuously variable transmission is, for example, at the stage before being accommodated in the casing, the aforementioned input shaft 1, input side disks 2, 2, output side disk 3A, outer peripheral gear 4A, upper and lower yokes 23A, 23B. , The trunnion, the power roller 11, the driving device 32, the hydraulic pressing device 80, the fixing member 52 (upper plate) and the like are integrally assembled into a variator module 43, and the variator module 43 is housed and attached in a casing It is supposed to be.

  In such a variator module 43, the lower spherical post 68 fixed to the upper cylinder body 61 and the lower cylinder body 62 constituting the drive cylinder 31 of the drive device 32, and the upper one fixed to the upper plate 52. The spherical post 64 is a columnar post 69 integrally joined to the upper and lower sides, and in the variator module 43, a pair of columnar posts 69 corresponds to the upper plate 52 and the cylinder body of the drive cylinder 31 (upper cylinder body 61 and lower cylinder body 62 ) Is connected.

Further, the input shaft 1 is in a state in which the upper and lower central portions of the columnar posts 69 pass through. The input shaft 1 supports a pair of input side disks 2 and 2, an output side disk 3A, a pressing device 80 and the like.
The output side disk 3A is rotatably supported by the input shaft 1 via a radial needle bearing (radial bearing) 35.
In addition, an output side disk 3A is disposed between the pair of columnar posts 69, and the output side disk 3A is axially positioned at both ends in the axial direction of the output side disk 3A and is thrust rotatably supported about the axis. A bearing 60 is provided. That is, the thrust ball bearing (thrust bearing) 60 is disposed between the columnar post 69 and the small diameter end of the output side disk 3A, and the position of the output side disk 3A in the axial direction of the input shaft 1 is restricted. And allows rotation about the axis of the output side disk 3A.

Unexamined-Japanese-Patent No. 2004-257533

Thus, the rotational support of the output side disk (inner disk) 3A is performed by the radial bearing 35 and the thrust bearing 60.
On the other hand, a counter gear (not shown) is engaged with the power transmission gear (outer peripheral gear) 4A, but since the meshing position of this gear is on the outer peripheral portion of the output side disk 3A, torque (power) When being transmitted, a moment load acts on the output side disk 3A, and the output side disk 3A may be inclined with respect to the input shaft 1. In this case, an excessive load may be input to the thrust bearing 60 and the life may be reduced. That is, when the output side disk 3A is inclined, as shown in FIG. 8, the output side disk 3A moves so as to turn around the input shaft 1, so that the load is concentrated on the thrust bearing 60 at a portion shown by the arrow A. The durability of the thrust bearing 60 may be reduced.

  The present invention has been made in view of the above circumstances, and is a toroidal type capable of improving the durability of thrust bearings provided on both axial ends of an inner disk provided with an outer peripheral gear for transmitting power on the outer peripheral surface. An object of the present invention is to provide a continuously variable transmission.

In order to achieve the above object, the toroidal type continuously variable transmission according to the present invention comprises a shaft, a pair of outer disks supported by the shaft, and a shaft rotatably supported by the shaft via a radial bearing. A toroidal continuously variable transmission comprising: an inner disk having an outer peripheral gear for transmitting power on a surface thereof; and a power roller interposed between the outer disk and the inner disk.
At both axial ends of the inner disc, there are provided thrust bearings having two races for axially positioning and rotatably supporting the inner disc.
The one bearing ring on the side of the inner disk of the thrust bearing or the other bearing ring on the side of the supporting member supporting the thrust bearing has a surface in contact with the inner disk or the supporting member It is characterized in that a spherical seat is provided which allows inclination with respect to the axis.

In the present invention, the inner disk or support member at the back of the bearing ring of the thrust bearing, that is, one bearing ring on the inner disk side of the thrust bearing or the other bearing ring on the bearing member supporting the thrust bearing Since the spherical seat which allows the inclination with respect to the axis of the inner disc is provided on the surface in contact with the shaft, the inclination is spherical even if the inner disc is inclined with respect to the axis when torque (power) is transmitted. Since the seat permits, there is no local concentration of load on the thrust bearing as in the prior art. Therefore, the durability of the thrust bearing can be improved, and the life of the thrust bearing can be improved.

  In the above-mentioned composition of the present invention, surface treatment which controls sliding resistance may be given to the above-mentioned spherical seat.

  According to such a configuration, since the sliding resistance can be suppressed by the surface treatment of the spherical seat, the spherical seat of the bearing ring of the thrust bearing slides smoothly against the spherical portion that receives it, thus further The durability of the thrust bearing can be improved to improve the life.

  Further, in the configuration of the present invention, an elastic member may be provided between an outer diameter surface of the bearing ring provided with the spherical seat and a support member for supporting the bearing ring.

  According to such a configuration, since the elastic member is provided between the outer peripheral surface of the bearing ring and the support member, the bearing ring of the thrust bearing follows the spherical seat due to the inclination of the inner disk with respect to the axis. When it moves, the elastic member is elastically contracted along with it, but the elastic return force also restores the bearing ring to its original position. Therefore, the alignment of the thrust bearing can be improved.

  According to the present invention, since the spherical seat allowing the inclination of the inner disc with respect to the axis of the inner disk is provided on the rear surface of the bearing ring of the thrust bearing, the durability of the thrust bearing can be improved. Can be improved.

FIG. 1 is a cross-sectional view of a toroidal continuously variable transmission according to an embodiment of the present invention. FIG. 7 is an enlarged cross-sectional view of a central portion of the output side disk. It is an expanded sectional view showing a thrust bearing and its neighborhood equally. It is an expanded sectional view showing the thrust bearing which provided the elastic member equally, and its neighborhood. It is sectional drawing which shows an example of the conventional toroidal type continuously variable transmission. It is sectional drawing which follows the AA in FIG. It is a sectional view showing another example of the conventional toroidal type continuously variable transmission. It is sectional drawing of the principal part which shows the state which the output side disc inclined similarly.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
The feature of the toroidal-type continuously variable transmission of the present embodiment lies in the configuration of the thrust bearing 60 supporting the output side disk (inner disk) 3A, and the other configuration and operation are the conventional toroidal shown in FIG. Since the configuration and operation of the continuously variable transmission are substantially the same, in the following, only the characterizing portion of the present embodiment will be referred to, and the other portions will be briefly described with the same reference numerals as in FIG. I will just explain.

  The toroidal type continuously variable transmission of this embodiment shown in FIG. 1 is similar to the conventional toroidal type continuously variable transmission shown in FIG. 7 in the input shaft (shaft) 1, the input side disks (outer side disks) 2, 2 , An output side disk (inner side disk) 3A, an outer peripheral gear 4A provided on the outer peripheral surface of the output side disk 3A, upper and lower yokes 23A and 23B, a trunnion, a power roller 11, a drive device 32, a hydraulic pressing device 80, A fixing member 52 (upper plate) or the like is integrally assembled to form a variator module 43, and the variator module 43 is accommodated and attached in a casing (not shown).

  The pressing device 80 includes a first cylinder 81 connected to the right end of the input shaft 1, a second cylinder 82 provided on the input disc 2, and an annular first piston (hydraulic piston). 83 and an annular second piston portion (hydraulic piston) 84.

A space surrounded by the inner surface of the first cylinder portion 81, the first piston portion 83, and a part of the outer peripheral surface of the input shaft 1 constitutes a first hydraulic chamber 85.
In addition, a space surrounded by the inner peripheral surface of the second cylinder portion 82, the second piston portion 84, the back surface 2d of the input side disk 2 and a part of the outer peripheral surface of the input shaft 1 is the second The hydraulic chamber (oil chamber) 90 of the

  In addition, a disc spring 94 for applying a preload is interposed between the first piston portion 83 and the first cylinder portion 81 by partially using the first hydraulic chamber 85, The first piston portion 83 movable along the input shaft 1 is biased toward the input-side disc 2 with respect to the cylinder portion 81 of FIG.

In such a pressing device 80, pressure oil of a predetermined pressure is sent to the first hydraulic chamber 85 and the second hydraulic chamber 90. Then, a force in the direction in which the axial dimension of the hydraulic pressure chambers 85 and 90 increases is caused in the hydraulic pressure chambers 85 and 90.
When pressure oil is fed into the first hydraulic chamber 85, the first piston portion 83 is pressed to the left (in the side of the input side disc 2) in FIG. 1, thereby being integrally formed on the back side of the input side disc 2 The input side disc 2 is pressed to the left through the second cylinder portion 82.

On the other hand, when pressure oil is fed into the second hydraulic chamber 90, the movement of the second piston portion 84 to the right in FIG. 1 is restricted, so the input side disc 2 is pressed to the left.
As described above, the forces generated in both the hydraulic pressure chambers 85 and 90 both press the input side disc 2 toward the output side disc 3A.

The output side disk (inner disk) 3A is supported by the input shaft (shaft) 1 via a radial needle bearing (radial bearing) 35. Therefore, the output side disk (inner disk) 3A is provided on the outer peripheral surface of the output side disk 3A. The gear reaction force (radial force) applied to the outer peripheral gear 4A is basically received by the input shaft (shaft) 1 through the radial needle bearing 35.
However, as described above, when torque (power) is transmitted, a moment load acts on the output side disk 3A, and the output side disk 3A may be inclined with respect to the input shaft 1. In this case, a load is also input to the thrust bearing 60.

Therefore, in the present embodiment, as shown in FIG. 2, a part of a spherical surface (shown by a broken line) of radius R centering on the center O of the output side disk 3A is shown by two races 60a of the thrust bearing 60, Of the 60b, by providing it on the back of the axially outer race 60a, three-dimensional freedom is given to the movement of the race 60a and local pressure increase is suppressed.
That is, as shown in FIG. 3, a convex spherical seat 60c which is a part of the spherical surface of the radius R is provided on the back surface of the bearing ring 60a. The spherical seat 60c is provided over substantially the entire area of the outer surface of the bearing ring 60a.
On the other hand, the concave spherical portion 69a forms a spherical couple with the spherical seat 60c on the outer peripheral side of the hole through which the input shaft 1 penetrates in the substantially central portion of the columnar post 69 supporting the bearing ring 60a. Is provided.
The outer diameter surface 60d of the bearing ring 60a is not restrained, and the bearing ring 60a is provided between the outer diameter surface 60d and the cylindrical inner wall surface 69b provided substantially at the center of the columnar post 69 in the axial direction. A gap S is provided which is movable along the spherical portion 69a.

Therefore, according to the present embodiment, when the output side disk 3A receives a moment due to the gear reaction force applied to the outer peripheral gear 4A of the outer peripheral surface of the output side disk 3A, the gear reaction force is , Radial needle bearing 35 and thrust bearing 60.
In this case, since the spherical seat 60c allowing the inclination of the output side disk 3A with respect to the input shaft 1 is provided on the back surface of the bearing ring 60a of the thrust bearing 60, when torque (power) is transmitted, the output side Even if the disc 3A is inclined with respect to the input shaft 1, this inclination is allowed by the spherical seat 60c. That is, with the inclination of the output side disk 3A, the thrust bearings 60 provided at both axial ends of the output side disk 3A move centering on the center O of the output side disk 3A, but the bearing ring 60a has its spherical surface Since the seat 60c and the spherical portion 69a can move by a spherical couple, inclination of the output side disk 3A is allowed.
Therefore, since the load does not locally concentrate on the thrust bearing 60 as in the conventional case, the durability of the thrust bearing 60 can be improved, and the life of the thrust bearing 60 can be improved.

  Further, in the present embodiment, the spherical seat 60c provided on the back surface of the bearing ring 60a may be subjected to surface treatment for reducing the sliding resistance. Examples of this surface treatment include, but are not limited to, DLC (diamond-like carbon) coating.

As described above, since the sliding resistance can be suppressed by applying the surface treatment to the spherical seat 60c, the spherical seat 60c of the bearing ring 60a smoothly slides with respect to the spherical portion 69a which receives the same. Furthermore, the durability of the thrust bearing 60 can be improved, and the life can be improved.
The same effect can be obtained by applying the same surface treatment to the surface of the spherical portion 69a.

  Further, as shown in FIG. 4, in the present embodiment, between the outer diameter surface 60d of the bearing ring 60a provided with the spherical seat 60c and the cylindrical inner wall surface 69b of the columnar post 69 supporting the bearing ring 60a. Alternatively, an elastic member 70 such as an annular web washer may be provided.

  In this way, when the bearing ring 60a of the thrust bearing 60 moves along the spherical seat 60c due to the inclination of the output side disk 3A with respect to the input shaft 1 as described above, the elastic member 70 is elastically moved accordingly However, due to its elastic return force, the bearing ring 60a is also returned to its original position. Therefore, the alignment of the thrust bearing 60 can be enhanced.

Further, in the present embodiment, of the races 60a and 60b of the thrust bearing 60, the spherical seat 60c is provided on the back of the race 60a, but instead, the back of the race 60b on the output side disc 3A side May have a concave spherical seat. In this case, the spherical surface portion and the spherical surface portion constituting the spherical surface pair may be provided on the small diameter side end surface of the output side disk 3A.
According to such a configuration, even if the output side disk 3A is inclined with respect to the input shaft 1 when torque (power) is transmitted, the inclination is allowed by the spherical seat, so that a thrust bearing as in the prior art There is no concentration of load locally. Therefore, the durability of the thrust bearing can be improved, and the life of the thrust bearing can be improved.

  In the present embodiment, the output side disk (inner disk) 3A provided with the outer peripheral gear 4A for power transmission is described as an example supported by the input shaft 1, but in the toroidal type continuously variable transmission, The input / output relationship between the input disk and the output disk may be reversed. Therefore, the present invention can be applied to the case where the input side disk 2 and the output side disk 3A are interchanged. The present invention can also be applied to a full toroidal continuously variable transmission.

1 Input axis (axis)
2 Input disc (outer disc)
3A output disc (inner disc)
4A Outer peripheral gear 11 Power roller 35 Radial bearing 60 Thrust bearing 60a, 60b Bearing ring 60c Spherical seat 70 Elastic member

Claims (2)

A shaft, a pair of outer disks supported by the shaft, an inner disk rotatably supported on the shaft via a radial bearing and having an outer peripheral gear for transmitting power on an outer peripheral surface, the outer disk, and the outer disk In a toroidal type continuously variable transmission provided with a power roller nipped between the inner disc and
At both axial ends of the inner disc, there are provided thrust bearings having two races for axially positioning and rotatably supporting the inner disc.
The one bearing ring on the side of the inner disk of the thrust bearing or the other bearing ring on the side of the supporting member supporting the thrust bearing has a surface in contact with the inner disk or the supporting member A toroidal continuously variable transmission characterized in that a spherical seat for allowing inclination with respect to the shaft is provided. The toroidal type continuously variable transmission according to claim 1, wherein an elastic member is provided between an outer diameter surface of a bearing ring provided with the spherical seat and the support member.

Images