JP2015090159A - Toroidal type continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a toroidal type continuously variable transmission which can lower a stress generated at an integrated output-side disc.SOLUTION: An integrated output-side disc 34 is arranged between paired input-side discs 2. A radial needle bearing 72 for rotatably supporting the integrated output-side disc 34 with respect to a cylindrical shaft is arranged between the cylinder shaft 71 and the integrated output-side disc 34. A step 81 for regulating a position along an axial direction of the radial needle bearing 72 is arranged at an outer peripheral face of the cylindrical shaft 71. Furthermore, a snap ring 82 for regulating a position along the axial direction of the radial needle bearing 72 is attached to a snap ring groove 83 of the cylindrical shaft 71.

Description

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

  For example, a double cavity toroidal continuously variable transmission used as a transmission for an automobile is configured as shown in FIGS. 3 and 4, for example. An input shaft 1 is rotatably supported inside the casing 50, and two input side disks 2, 2 and two output side disks 3, 3 are attached to the outer periphery of the input shaft 1. . An output gear 4 is rotatably supported on the outer periphery of the intermediate portion of the input shaft 1. Output side disks 3 and 3 are connected to cylindrical flange portions 4a and 4a provided at the center of the output gear 4 by spline coupling.

  The input shaft 1 is rotationally driven by a drive shaft 22 via a loading cam type pressing device 12 provided between an input side disk 2 and a cam plate 7 located on the left side in the drawing. . The output gear 4 is supported in the casing 50 via a partition wall 13 formed by coupling two members, so that the output gear 4 can rotate around the axis O of the input shaft 1 while the axis O. Directional displacement is prevented.

  The output side disks 3 and 3 are supported by needle bearings 5 and 5 interposed between the input shaft 1 so as to be rotatable about the axis O of the input shaft 1. Further, the left input side disk 2 in the figure is supported on the input shaft 1 via a ball spline 6, and the right side input disk 2 in the figure is splined to the input shaft 1. Rotates with the input shaft 1. Further, the power roller 11 is rotatably held between the inner side surfaces (concave surfaces) 2a, 2a of the input side discs 2, 2 and the inner side surfaces (concave surfaces) 3a, 3a of the output side discs 3, 3. .

  A step portion 2b is provided on the inner peripheral surface 2c of the input side disk 2 located on the right side in FIG. 3, and the step portion 1b provided on the outer peripheral surface 1a of the input shaft 1 is abutted against the step portion 2b. At the same time, the back surface (right surface in FIG. 3) of the input side disk 2 is abutted against the loading nut 9. Thereby, the displacement of the input side 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 1d of the input shaft 1, and this disc spring 8 is a concave surface 2a, 2a, 3a of each disk 2, 2, 3, 3. , 3a and the contact surface between the peripheral surfaces 11a and 11a of the power rollers 11 and 11 are applied with a pressing force.

  4 is a cross-sectional view taken along line AA in FIG. As shown in FIG. 4, a pair of trunnions 15, 15 that swing about a pair of pivots 14, 14 that are twisted with respect to the input shaft 1 are provided inside the casing 50. In FIG. 4, the input shaft 1 is not shown. Each trunnion 15, 15 is a pair of bent wall portions 20, 20 formed at both ends in the longitudinal direction (vertical direction in FIG. 4) of the support plate portion 16 so as to be bent toward the inner surface side of the support plate portion 16. have. The bent wall portions 20 and 20 form concave pocket portions P for accommodating the power rollers 11 in the trunnions 15 and 15. Further, the pivot shafts 14 and 14 are concentrically provided on the outer side surfaces of the bent wall portions 20 and 20, respectively.

  A circular hole 21 is formed in the central portion of the support plate portion 16, and the base end portion 23 a of the displacement shaft 23 is supported in the circular hole 21. Then, by swinging each trunnion 15, 15 about each pivot 14, 14, the inclination angle of the displacement shaft 23 supported at the center of each trunnion 15, 15 can be adjusted. Each power roller 11 is rotatably supported via a radial needle bearing 35 around the tip 23b of the displacement shaft 23 protruding from the inner surface of each trunnion 15, 15. 11 is sandwiched between the input disks 2 and 2 and the output disks 3 and 3. In addition, the base end part 23a and the front-end | tip part 23b of each displacement shaft 23 and 23 are mutually eccentric.

  The pivot shafts 14 and 14 of the trunnions 15 and 15 are supported so as to be swingable and axially displaceable with respect to the pair of yokes 23A and 23B, respectively. The horizontal movement of the trunnions 15 and 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 23 </ b> A and 23 </ b> B, and the pivot shafts 14 provided at both ends of the trunnion 15 swing through the radial needle bearings 30. It is supported freely. In addition, a circular locking hole 19 is provided in the central portion of the yokes 23A and 23B in the width direction (left and right direction in FIG. 4). The inner peripheral surface of the locking hole 19 is a cylindrical surface, and is a spherical post. 64 and 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 cylinder for supporting the same. The upper cylinder body 61 of the body 31 is supported so as to be swingable.

  The displacement shafts 23 and 23 provided in the trunnions 15 and 15 are provided at positions 180 degrees opposite to the input shaft 1. Further, the direction in which the distal end portion 23b of each of the displacement shafts 23, 23 is eccentric with respect to the base end portion 23a is the same direction as the rotational direction of both the disks 2, 2, 3, 3 (in FIG. (Reverse direction). Further, the eccentric direction is a direction substantially orthogonal to the direction in which the input shaft 1 is disposed. Accordingly, the power rollers 11 and 11 are supported so that they can be slightly displaced 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 of each component member based on the thrust load generated by the pressing device 12, each component 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 that is a thrust rolling bearing is sequentially formed from the outer surface side of the power roller 11. A thrust needle bearing 25 is provided. Among these, the thrust ball bearing 24 supports 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 includes a plurality of balls (hereinafter referred to as rolling elements) 26, 26, an annular retainer 27 that holds the rolling elements 26, 26 in a freely rolling manner, And 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 surface) of each power roller 11, and the outer ring raceway is formed on the inner side surface of each outer ring 28.

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

  Further, drive rods (trunnion shafts) 29 and 29 are provided at one end portions (lower end portions in FIG. 4) of the trunnions 15 and 15 respectively, and a drive piston ( Hydraulic pistons) 33, 33 are fixed. Each of the drive pistons 33 and 33 is oil-tightly fitted in a cylinder body 31 constituted by an upper cylinder body 61 and a lower cylinder body 62. The drive pistons 33 and 33 and the cylinder body 31 constitute a drive device 32 that displaces the trunnions 15 and 15 in the axial direction of the pivots 14 and 14 of the trunnions 15 and 15.

  In the case of the toroidal continuously variable transmission configured as described above, the rotation of the input shaft 1 is transmitted to the input side disks 2 and 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 further transmitted to the output gear 4. It is taken out more.

  When changing the rotational speed ratio between the input shaft 1 and the output gear 4, the pair of drive pistons 33, 33 are displaced in opposite directions. As the drive pistons 33 and 33 are displaced, the pair of trunnions 15 and 15 are displaced in directions opposite to each other. For example, the power roller 11 on the left side in FIG. 4 is displaced to the lower side in the figure, and the power roller 11 on the right side in the figure is displaced to the upper side in the figure.

  As a result, the peripheral surfaces 11a and 11a of the power rollers 11 and 11 act on contact portions of the input side disks 2 and 2 and the inner side surfaces 2a, 2a, 3a and 3a of the output side disks 3 and 3, respectively. The direction of the tangential force changes. As the force changes, the trunnions 15 and 15 swing in opposite directions around the pivots 14 and 14 pivotally supported by the yokes 23A and 23B.

  As a result, the contact position between the peripheral surfaces 11a and 11a of the power rollers 11 and 11 and the inner surfaces 2a and 3a changes, and the rotational speed ratio between the input shaft 1 and the output gear 4 changes. Further, 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 and 11 and the outer rings attached to the power rollers 11 and 11 will be described. 28 and 28 slightly rotate around the base end portions 23a and 23a of the displacement shafts 23 and 23, respectively. Since the thrust needle bearings 25 and 25 exist between the outer side surfaces of the outer rings 28 and 28 and the inner side surfaces of the support plate portions 16 constituting the trunnions 15 and 15, respectively, the rotation is performed smoothly. Is called. Therefore, as described above, the force for changing the inclination angle of each displacement shaft 23, 23 can be small.

  By the way, in the double cavity type toroidal continuously variable transmission, as shown in FIG. 5, the back surfaces of the pair of output side disks 3, 3 arranged between the pair of input side disks 2, 2 are joined to each other. A pair of output side disks 3 and 3 is integrated, and an integrated output side disk 34 is used as an output gear 4 provided with teeth 41 on the outer peripheral surface of the integrated output side disks 3 and 3. (For example, refer to Patent Document 1).

  For example, as shown in FIG. 5, such an integrated output side disk 34 is supported by a cylindrical shaft (hollow shaft) 71 through which the input shaft 1 (shown in FIG. 3) passes through a radial needle bearing 72. There is a case. That is, the integrated output side disk 34 is rotatably supported on the cylindrical shaft 71 via the radial needle bearing 72.

  Both ends of the cylindrical shaft 71 are fixed to the casing 50 via positioning members, for example. The positioning member is, for example, a pair of columnar posts 69 that are formed by connecting the above-described pair of upper and lower spherical posts 64 and 68 together. The columnar post 69 has its lower end fixed to the casing 50 via the cylinder body 31 and its upper end fixed to the casing 50 via the fixing member 52.

  Further, the input shaft 1 passes through the central portion of the columnar post 69. In addition, the integrated output side disk 34 is disposed between the pair of columnar posts 69, and the thrust bearing 67 is disposed between each columnar post 69 and the integrated output side disk 34, and the integrated output side The position of the disk 34 along the axial direction is restricted.

  The radial needle bearing 72 is disposed between the inner peripheral surface of the through hole 76 of the integrated output side disk 34 and the outer peripheral surface of the cylindrical shaft 71, and both ends along the axial direction of the integrated output side disk 34. Corresponding to the two places that are the parts, they are arranged with a space therebetween.

  The radial needle bearings 72 are regulated in the axially central position of the integrated output side disk 34 by a pair of steps 73 formed on the inner peripheral surface of the through hole 76 of the integrated output side disk 34. . The step 73 is formed by making the inner diameter of the central portion of the inner peripheral surface of the through hole 76 of the integrated output side disk 34 smaller than the inner diameter of the end portion outside the central portion.

  Further, the position of the axial end side of the integrated output side disk 34 of the radial needle bearing 72 is restricted by the retaining ring 74. The retaining ring 74 is attached to a retaining ring groove 75 provided on the inner peripheral surface of the through hole 76 of the integrated output side disk 34.

Japanese Patent Laid-Open No. 2001-116097

  By the way, a large contact load is applied to the contact portion with the power roller 11 by the pressing force of the pressing device 12 and the gear reaction force is applied to the output gear 5 provided on the outer peripheral portion of the integrated output side disk 34. Become. In this case, the step 73 and the retaining ring groove 75 are provided on the inner peripheral surface of the through hole 76 of the integrated output side disk 34, that is, the shape changes greatly on the inner peripheral surface of the through hole 76. Since there is a portion, stress concentrates and increases at the portion where the shape changes, that is, at the corner of the step or the bottom corner of the retaining ring groove. Therefore, in the design of the integrated output side disk 34, the portion where the stress increases becomes a problem, and a structure capable of reducing the stress is required.

  The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a toroidal continuously variable transmission that can reduce the stress generated in the integrated output side disk.

  In order to achieve the above object, the toroidal continuously variable transmission according to the present invention includes an input-side disk and an output-side disk that are supported concentrically and rotatably with their inner surfaces facing each other. And a power roller sandwiched between the input-side disk and the output-side disk, and the pair of the output-side disks are integrated between the pair of the input-side disks and the outer peripheral portion is an output gear. A shaft that supports the input side disk and penetrates the integrated output side disk, the input side disk, the integrated output side disk, a power roller, and a shaft. A casing to be accommodated and supported by the casing and rotatably supported by the integrated output-side disk in a state where the shaft penetrates. A toroidal-type continuously variable transmission including an empty shaft, provided between the hollow shaft and the integrated output side disk, and rotatably supporting the integrated output disk with respect to the hollow shaft A bearing is provided, and a step is provided on an outer peripheral surface of the hollow shaft to regulate a position along the axial direction of the radial bearing.

  In the present invention, the positioning (movement restriction) of the radial bearing that rotatably supports the integrated output side disk with respect to the hollow shaft (cylindrical shaft) is performed by the step provided on the hollow shaft. There is no need to provide a step for determining the position of the radial bearing on the inner peripheral surface of the through hole of the output side disk.

  Therefore, since there is no step where the shape changes greatly on the inner peripheral surface of the integrated output side disk, a large contact load acts on the contact portion with the power roller, and even if a gear reaction force acts on the output gear, The stress does not increase at the corner of the step on the inner peripheral surface of the integrated output side disk. That is, it is possible to prevent the stress from increasing on the inner peripheral surface of the integrated output side disk.

  Further, since the contact load described above does not act on the cylindrical shaft, and only the gear reaction force acts, the force on the cylindrical shaft is small compared to the integrated output side disk, and the shape of the cylindrical shaft changes greatly. Even if the step is formed, the stress generated at the corner of the step does not become too high. In the structure in which the integrated output side disk is supported by the shaft (input shaft) via the radial bearing, if a step for restricting the position of the radial bearing is provided on the shaft side, the stress on the shaft becomes high. Further, in such a structure, since a gear reaction force acts on the shaft and a large axial force acts on the shaft, if there is a portion where the shape of the above-described step or the retaining ring groove described later greatly changes, the shaft The stress generated in the process becomes too high, resulting in a structure that is difficult to design.

  The said structure of this invention WHEREIN: It is preferable that the said hollow shaft is provided with the retaining ring groove | channel in which the retaining ring which regulates the position along the axial direction of the said radial bearing with the said level | step difference is attached.

  According to such a configuration, the position (movement) along the axial direction of the radial bearing that rotatably supports the integrated output-side disk with respect to the hollow shaft has a step provided on the hollow shaft and the hollow shaft. It is regulated by a retaining ring attached to a retaining ring groove provided. Therefore, there is no need to provide a step or a retaining ring groove whose shape changes greatly on the inner peripheral surface of the integrated weekly power disk. Thereby, it is possible to prevent a large stress from being generated on the inner peripheral surface of the integrated output side disk. Further, even if the retaining ring is provided on the hollow shaft, since the hollow shaft does not rotate, the retaining ring can be prevented from coming off due to centrifugal force.

  In the configuration of the present invention, both ends of the hollow shaft are supported by the casing, and a thrust bearing is provided between each end of the integrated output side disk in the axial direction. A position restricting portion for restricting a position along the axial direction of the radial bearing together with the step between the thrust bearing and the radial bearing. Is preferably provided.

  According to such a configuration, the position (movement) along the axial direction of the radial bearing is such that the step provided on the hollow shaft, the thrust bearing disposed between the positioning member and the integrated output side disk, and the above-described configuration. It is regulated by a position regulation part provided between the radial bearings. Therefore, there is no need to provide a structure whose shape changes greatly, such as a step or a retaining ring groove, on the inner peripheral surface of the integrated output side disk. Thereby, it is possible to prevent a large stress from being generated on the inner peripheral surface of the integrated output side disk. Further, since there is no need to provide a retaining ring groove on the hollow shaft, stress concentration on the hollow shaft can be prevented.

  According to the present invention, it is possible to prevent an increase in stress in the integrated output side disk.

It is principal part sectional drawing which shows the toroidal type continuously variable transmission in the 1st Embodiment of this invention. It is principal part sectional drawing which shows the toroidal type continuously variable transmission in the 2nd Embodiment of this invention. It is sectional drawing which shows an example of the conventional toroidal type continuously variable transmission. It is sectional drawing which follows the AA line in FIG. It is sectional drawing which shows the integral-type output side disk and cylindrical shaft of the conventional toroidal type continuously variable transmission.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
The toroidal-type continuously variable transmission according to the present embodiment is characterized in that an integrated output side disk can be rotated via a radial needle bearing (radial bearing) with respect to a cylindrical shaft (hollow shaft) through which the input shaft passes. In the supporting structure, the structure that regulates the position along the axial direction of the radial needle bearing is to be provided in a member other than the integrated output side disk such as a cylindrical shaft, so this point will be described in detail below. Other parts are denoted by the same reference numerals as those in the prior art, and description thereof is omitted or simplified.

(First embodiment)
As shown in FIG. 1, in the toroidal-type continuously variable transmission according to the first embodiment, a pair of radials are mounted on a cylindrical shaft 71 supported by a casing 50 via a columnar post 69 as a positioning member as in the conventional case. The integrated output side disk 34 is rotatably supported via the needle bearing 72.

  A position along the axial direction of the pair of radial needle bearings 72, that is, a position along the axial direction of the input shaft 1, the cylindrical shaft 71, and the integrated output side disk 34, and a step 81 formed on the cylindrical shaft 71, It is determined by a retaining ring 82 attached to a retaining ring groove 83 provided on the cylindrical shaft 71. Thereby, the movement along the axial direction of the pair of radial needle bearings 72 is restricted by the pair of steps 81 and the pair of retaining rings 82.

  In other words, the radial needle bearings 72 arranged at both ends in the axial direction of the integrated output side disk 34 are positioned at the central end of the integrated output side disk 34 by the step 81, and the integrated output side The position of the end portion on the end side of the disk 34 is regulated by a retaining ring 82.

  The pair of steps 81 of the cylindrical shaft 71 is provided on the cylindrical shaft 71 by making the outer diameter of the central portion of the cylindrical shaft 71 larger than the outer diameter of the end portion. Further, since the inner peripheral surface of the through hole 76 of the integrated output side disk 34 is not provided with a structure for determining the position of the radial needle bearing 72, the inner peripheral surface of the through hole 76 is a cylinder having a constant inner diameter. It is in the shape.

  In such a toroidal-type continuously variable transmission, as described above, the inner peripheral surface of the through hole 76 of the integrated output side disk 34 has a cylindrical shape with a constant inner diameter, and there is no portion in which the shape greatly changes. Since the structure is such that the stress is difficult to concentrate, in the integrated output side disk 34, based on the force such as the contact load at the contact portion with the power roller 11 or the gear reaction force generated at the output gear 4 at the outer peripheral portion. The generated stress can be reduced.

  Further, the cylindrical shaft 71 is formed with a step 81, a retaining ring groove 83, and the like on the outer peripheral surface thereof, and stress is easily concentrated due to a portion whose shape changes greatly. However, although the gear reaction force described above acts on the cylindrical shaft 71, the contact load of the power roller 11 does not act on the cylindrical shaft 71, and the stress generated in the large shape change portion does not become too high. Further, since the cylindrical shaft 71 does not rotate, the retaining ring 82 does not come off the cylindrical shaft 71 due to centrifugal force.

(Second Embodiment)
As shown in FIG. 2, the toroidal type continuously variable transmission according to the second embodiment has a pair of radials on a cylindrical shaft 71 supported by a casing 50 via a columnar post 69 as a positioning member, as in the conventional case. The integrated output side disk 34 is rotatably supported via the needle bearing 72.

  A position along the axial direction of the pair of radial needle bearings 72, that is, a position along the axial direction of the input shaft 1, the cylindrical shaft 71, and the integrated output side disk 34 is regulated by a step 81 formed on the cylindrical shaft 71. At the same time, it is restricted by a position restricting portion 86 provided between a thrust bearing 85 disposed between the columnar post 69 and the integrated output side disk 34 and the radial needle bearing 72. Thereby, the movement along the axial direction of the radial needle bearing 72 is restricted.

  In other words, the radial needle bearings 72 arranged at both ends in the axial direction of the integrated output side disk 34 are positioned at the central end of the integrated output side disk 34 by the step 81, and the integrated output side The position of the end on the end side of the disk 34 is regulated by the position regulating unit 86.

  The pair of steps 81 of the cylindrical shaft 71 has the same structure as that of the first embodiment. The position restricting portion 86 is an annular protruding portion that protrudes from the outer ring or inner ring of the thrust bearing 85 between the outer peripheral surface of the cylindrical shaft 71 and the inner peripheral surface of the through hole 76 of the integrated output side disk 34. The ends on the axial direction end side of the integrated output side disk 34 of the radial needle bearing 72 disposed at both ends of the inner peripheral surface of the through hole 76 of the output side disk 34 are positioned.

  Further, the inner peripheral surface of the through hole 76 of the integrated output side disk 34 has a cylindrical shape with a constant inner diameter, as in the first embodiment. In the second embodiment, only the step 81 is provided on the outer peripheral surface of the cylindrical shaft 71, but the retaining ring groove 83 is not provided because the retaining ring 82 is not used.

  In such a toroidal-type continuously variable transmission, as described above, the inner peripheral surface of the through hole 76 of the integrated output side disk 34 has a cylindrical shape with a constant inner diameter, which is the same as in the case of the first embodiment. Similarly, the stress generated in the integrated output side disk 34 can be reduced.

  Further, since the cylindrical shaft 71 has a step 81 formed on the outer peripheral surface thereof but does not have a retaining ring groove 83, the generated stress can be made lower than in the case of the first embodiment. In the second embodiment, the position restricting portion 86 is a protruding portion that protrudes from the thrust bearing 85. However, the position restricting portion 86 is disposed between the thrust bearing 67 and the radial needle bearing 72 in the first embodiment. An annular spacer may be used.

  The present invention can be applied to full-toroidal continuously variable transmissions without trunnions in addition to various double cavity type half toroidal continuously variable transmissions.

1 Input shaft (axis)
2 Input side disk 3 Output side disk 4 Output gear 11 Power roller 34 Integrated output side disk (a pair of output side disk and output gear)
69 Columnar post (positioning member)
71 Cylindrical shaft (hollow shaft)
72 Radial needle bearings (radial bearings)
81 Step 82 Retaining ring 83 Retaining ring groove 85 Thrust bearing 86 Position restricting portion

Claims (3)

Power held between the input side disk and the output side disk, and the input side disk and the output side disk supported concentrically and rotatably with the respective inner surfaces facing each other. With rollers,
A pair of the output side disks are integrated between the pair of the input side disks, and an integrated output side disk having an outer peripheral portion as an output gear is disposed,
A shaft that supports the input-side disk and penetrates the integrated output-side disk, a casing that accommodates the input-side disk, the integrated output-side disk, a power roller, and a shaft, and is supported by the casing. And a toroidal continuously variable transmission comprising a hollow shaft that rotatably supports the integrated output side disk with the shaft penetrating therethrough,
A radial bearing provided between the hollow shaft and the integrated output disk, and rotatably supporting the integrated output disk with respect to the hollow shaft;
A toroidal continuously variable transmission characterized in that a step is provided on the outer peripheral surface of the hollow shaft to regulate a position along the axial direction of the radial bearing.   The toroidal-type continuously variable step according to claim 1, wherein the hollow shaft is provided with a retaining ring groove to which a retaining ring for restricting a position along the axial direction of the radial bearing is mounted together with the step. transmission. Both end portions of the hollow shaft are supported by the casing, and a thrust bearing is provided between each end portion in the axial direction of the integrated output side disk, and extends along the axial direction of the integrated output side disk. A positioning member for regulating the position;
2. The toroidal type according to claim 1, wherein a position restricting portion is provided between the thrust bearing and the radial bearing for restricting a position along the axial direction of the radial bearing together with the step. Continuously variable transmission.

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