JP2003090403A - Toroidal continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a toroidal continuously variable transmission capable of constantly upgrading the lubricating performance of a ball bearing equipped on a power roller, miniaturizing the power roller by shortening the shaft part that supports the power roller, and reducing the fabrication cost. SOLUTION: In the toroidal continuously variable transmission, an oil groove for lubrication from inner circumference side to outer circumference side is provided only on the power roller's inner ring side of a holder that holds rotatably the ball bearing of the power roller bearing.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention belongs to the technical field of a toroidal type continuously variable transmission applied to vehicles and the like.

[0002]

2. Description of the Related Art A continuously variable transmission for an automobile has a smoothness,
In recent years, research and development have been promoted in view of ease of driving and improvement of fuel efficiency. Of these, power is transmitted by shearing an oil film formed between the input / output disk and the power roller, and has a larger capacity and responsiveness than the V-belt type continuously variable transmission that has been practically used previously. A good toroidal type continuously variable transmission (hereinafter referred to as toroidal type CVT) has already been put to practical use.

The toroidal CVT is an input disc and an output disc that are coaxially opposed to each other, a power roller that is sandwiched between the input and output discs so that power can be transmitted between them, and a transmission case that is tiltably mounted. A trunnion that rotatably supports the roller is provided, and a gear shifting operation that obtains a gear ratio according to the magnitude of the tilt angle of the power roller is performed by slightly shifting the trunnion in the tilt axis direction orthogonal to the power roller rotation axis. The power roller is offset from the disk rotation center position by displacing the power roller, and the offset causes the power roller to tilt due to the side slip force generated at the contact portion between the power roller and the input disk, resulting in a predetermined tilt angle. At that time, the displacement given to the trunnion is returned to the original disc rotation center position, and the tilting operation of the power roller is stopped. It is made in the.

During this shifting operation, in order to always maintain the contact state between the power roller and the input / output disk regardless of the tilt of the power roller, the spacing between the input / output disks is changed by the loading cam device. At this time, only the input disc is moved in the disc axial direction by the loading cam device with respect to the fixed output disc, whereas the trunnion tilting shaft is a fixed shaft whose axial position does not change. In order to keep the disk contact of the power roller by following the change in the interval between the input and output disks, it is necessary to move the power roller in the direction (horizontal direction) perpendicular to the power roller rotation axis and the trunnion tilt axis. Also, when the input / output disk is deformed during power transmission or misalignment that may occur during assembly occurs, a relative positional deviation between the power roller and the input / output disk occurs, and this relative positional deviation is absorbed. In order to do so, it is necessary to move the power roller in the left-right direction.

As a power roller support structure for ensuring the movement of the power roller in the left-right direction, for example, in Japanese Patent Laid-Open No. 11-159590, the shaft center position is eccentric between the power roller support side and the trunnion support side. A power roller support structure has been proposed which uses a pivot shaft and allows the power roller to move in the left-right direction by swinging motion (swing motion) of the power roller.

Further, for example, in Japanese Unexamined Patent Publication No. 1978014/1989, a power roller accommodating portion arranged in the rotation axis direction of the input / output disk is formed in the trunnion, and the power roller and the trunnion power roller accommodating portion are provided between the power roller and the trunnion. A power roller support structure has been proposed in which a linear roller bearing is interposed and a power roller is supported so as to be movable in parallel in the left-right direction. Note that the power roller is configured to have a power roller inner ring, a power roller bearing, and an outer ring integral type shaft, and there is an idea of ensuring smooth horizontal translation of the power roller.

Regarding the above-mentioned lubrication structure of the power roller, for example, the techniques described in Japanese Patent Application Laid-Open No. 2000-310308 (Prior Art 1) and Japanese Patent Application Laid-Open No. 2001-124164 (Prior Art 2) are known. In these publications, a ball bearing that rotatably receives the thrust force applied to the power roller is provided, and a retainer that holds the ball bearing is provided with an oil groove from the inner peripheral side toward the outer peripheral side.
The oil grooves are formed on both sides of the power roller inner ring side and the power roller outer ring side of the cage, and lubricate the ball bearings from both sides.

[0008]

However, the above-described lubrication structure of the power roller has the following problems. That is, since the inner ring of the power roller has both a surface for transmitting power to and from the input / output disk and a ball bearing surface for rolling under a thrust force, the environment is thermally severe. However, in the prior art 1, since the lubricating oil is supplied from the oil holes of the outer ring of the power roller to the oil grooves provided on both sides of the cage, in reality, most of the supplied lubricating oil is retained. There is a problem that the durability of the ball bearing is deteriorated because it flows into the gap between the container and the outer ring.

Further, as described in the prior art 2, when the radial oil passage for supplying the lubricating oil to the ball bearing is provided on the pivot shaft so as to face the oil groove on the inner ring side of the power roller,
Sufficient lubricating oil will be supplied to the oil groove on the inner ring side of the power roller, but the radial oil passage will be processed unless it is axially separated from the end surface of the large-diameter shaft part on the inner ring side of the power roller. Therefore, it is necessary to set the large-diameter shaft part more than necessary, and if the axial length of the small-diameter shaft part is set to secure the axial length of the bearing that rotatably supports the power roller. There is a problem that the roller becomes large.

Further, since the oil groove is provided on both sides of the cage, the wall thickness t1 of the oil groove portion with respect to the wall thickness T of the cage is thin, and the oil groove must be formed by shaving. In this shaving, it is necessary to shave one surface and then the other surface, which causes a problem that processing time and cost are required.

The present invention has been made in view of the above problems, and an object of the present invention is to improve the lubrication of a ball bearing provided on a power roller to improve the durability and to improve the durability of a pivot shaft. An object of the present invention is to provide a toroidal type continuously variable transmission that can reduce the size of the power roller by shortening the large diameter shaft portion and further reduce the processing cost.

[0012]

In order to achieve the above object, in the invention according to claim 1, the input and output disks coaxially opposed to each other and the input and output disks are pinched so that power can be transmitted. And a trunnion that rotatably supports the power roller,
The power roller includes a power roller inner ring that makes frictional contact with the input / output disc, a power roller outer ring that receives an axial load that is input from the input / output disc to the power roller inner ring, and between the power roller inner ring and the power roller outer ring. In a toroidal type continuously variable transmission including a power roller bearing that is interposed and a shaft that receives an inner circumferential load that is input from an input / output disk to a power roller inner ring, a ball bearing of the power roller bearing An oil groove for lubrication extending from the inner peripheral side to the outer peripheral side is provided only on the inner side of the power roller of the retainer that holds the roller.

According to a second aspect of the present invention, in the toroidal type continuously variable transmission according to the first aspect, the oil groove provided in the cage is formed by forging, casting or resin integral molding. To do.

According to a third aspect of the present invention, in the toroidal type continuously variable transmission according to the first or second aspect, the shaft includes a small diameter shaft portion that rotatably supports the power roller inner ring via a bearing. A stepped shaft shape is formed by a large-diameter shaft portion that is integrated with the outer ring of the power roller, has an axial oil passage in the shaft axis, and communicates with the axial oil passage at one end side, The radial shaft portion has an outer end opening on the outer periphery and a radial oil passage for supplying lubricating oil to the power roller bearing, and the opening on the other end side of the radial oil passage is in an axial direction with respect to the oil groove. It is characterized in that it is provided on the outer ring side of the power roller.

[0015]

In the toroidal type continuously variable transmission according to the first aspect of the present invention, the cage for holding the ball bearing of the power roller bearing in a rollable manner is lubricated from the inner peripheral side to the outer peripheral side. The oil groove for use is provided only on the inner ring side of the power roller. That is, since the inner ring of the power roller has both a surface for transmitting power to and from the input / output disk and a ball bearing surface for rolling under a thrust force, the environment is thermally severe. However, by incorporating the oil groove of the cage toward the inner ring side, most of the lubricating oil supplied from the lubricating oil passage will flow through the gap between the cage and the inner ring, so the inner ring of the power roller will be cooled efficiently. The durability can be improved by mitigating a thermally severe environment. Further, since the oil groove is provided only on one side, it is possible to shorten the molding time of the groove and reduce the cost.

In the toroidal type continuously variable transmission according to the second aspect, the oil groove provided in the cage is formed by forging, casting or resin integral molding. That is, when the oil groove is provided on both sides, the axial groove thickness of the cage is insufficient, so the oil groove could only be provided by shaving, but the oil groove should be provided only on the inner ring side of the power roller. Thus, the axial thickness of the cage is secured, and the oil groove of the cage can be formed by an inexpensive manufacturing method such as forging, casting, or resin integral molding.

In the toroidal type continuously variable transmission according to the present invention, a radial oil passage communicating with an axial oil passage in the shaft shaft having a stepped shaft shape and supplying lubricating oil to the outer circumference of the large diameter shaft portion. Supplies the lubricating oil. At this time,
Since the radial oil passage is provided on the outer side of the power roller in the axial direction with respect to the oil groove, the lubricating oil is supplied to the outer side of the power roller of the cage, while a large amount of oil is supplied to the inner side of the power roller provided with the oil groove. It is possible to supply the above lubricating oil, and it is possible to further improve durability by efficiently mitigating a thermally severe environment. Also, the radial oil passage can be processed only at a position axially separated from the end surface of the large diameter shaft portion on the inner side of the power roller to some extent, but the opening of the radial oil passage is provided near the outer ring of the power roller. By that,
The large-diameter shaft portion can be shortened, and the power roller can be downsized.

[0018]

BEST MODE FOR CARRYING OUT THE INVENTION An embodiment for realizing a toroidal type continuously variable transmission according to the present invention will be described below.

[Overall Configuration] FIG. 1 is an overall configuration diagram showing a toroidal type continuously variable transmission according to a first embodiment. Reference numeral 10 denotes a toroidal type continuously variable transmission, in which a rotational driving force from an engine (not shown) is applied. It is input via the torque converter 12.
The torque converter 12 includes a pump impeller 12a, a turbine runner 12b, a stator 12c, a lockup clutch 12d, an apply-side oil chamber 12e, a release-side oil chamber 12f, and the like, and an input shaft 14 penetrates through a central portion thereof.

The input shaft 14 is connected to a forward / reverse switching mechanism 36, and the mechanism 36 includes a planetary gear mechanism 4
2. A forward clutch 44 and a reverse brake 46 are provided. The planetary gear mechanism 42 includes a pinion carrier 42a that supports a double pinion, a ring gear 42b that meshes with each of the double pinions, and a sun gear 42c.

The pinion carrier 42a of the planetary gear mechanism 42 is connected to the torque transmission shaft 16, and the torque transmission shaft 16 includes a first continuously variable transmission mechanism 18 and a second continuously variable transmission mechanism 20 in a transmission case 22. It is located in tandem on the downstream side. A control valve system body is arranged on the base indicated by reference numeral 64.

The first continuously variable transmission mechanism 18 has a pair of input disks 18a and output disks 18b whose opposing surfaces are formed as toroidal curved surfaces, and these input / output disks 18a,
A pair of power rollers 18c, which are arranged between the opposed surfaces of 18b and are symmetrically arranged with respect to the torque transmission shaft 16;
18d and trunnions 17a and 17b (FIG. 2) that rotatably support these power rollers 18c and 18d, respectively. Similarly, in the second continuously variable transmission mechanism 20, a pair of input disks 20a and output disks 20b whose opposing surfaces are formed toroidal curved surfaces, and a pair of power rollers 20c,
20d and trunnions 27a and 27b (FIG. 2) that rotatably support these power rollers 20c and 20d, respectively.

On the torque transmission shaft 16, the continuously variable transmission mechanisms 18 and 20 are arranged in opposite directions so that the output disks 18b and 20b face each other, and the first continuously variable transmission mechanism 1 is provided.
The input disk 18a of No. 8 is pressed rightward in the axial direction in the drawing by the loading cam device 34 that generates a pressing force according to the input torque that has passed through the torque converter 12.

The loading cam device 34 has a loading cam 34a and is supported by the shaft 16 via a slide bearing 38. The input disk 20a of the second continuously variable transmission mechanism 20 is biased by the disc spring 40 toward the left side in the axial direction in the drawing.

The input disks 18a and 20a are supported by the transmission shaft 16 via ball splines 24 and 26 so as to be rotatable and axially movable.

In the above mechanism, each power roller 18
c, 18d, 20c and 20d are respectively tilted by an operation described later so that a tilt angle according to the gear ratio is obtained,
The input rotation of the input disks 18a and 20a is continuously and continuously changed and transmitted to the output disks 18b and 20b.

The output disks 18b and 20b are spline-coupled to an output gear 28 which is fitted on the torque transmission shaft 16 so as to be relatively rotatable, and the transmission torque is transmitted to the output shaft (counter shaft) 30 via the output gear 28. Gear 3 combined
0a, and these gears 28, 30a form a torque transmission mechanism 32. Further, a transmission mechanism 48 including gears 52 and 56 provided on the output shafts 30 and 50 and an idler gear 54 meshing with the gears 52 and 56 is provided, and the output shaft 50 connects the propeller shaft 60 with the transmission mechanism 48.

[Structure of Shift Control System] FIG. 2 is a schematic diagram showing a shift control system in which the power rollers 18c, 18d, 20c and 20d are respectively tilted so as to obtain tilt angles according to the gear ratio. Will be described.

First, each power roller 18c, 18d, 2
0c and 20d are trunnions 17a, 17b, 27a,
The power roller rotating shaft 1 is supported by one end of 27b.
It is rotatable around 5a, 15b, 25a and 25b. This trunnion 17a, 17b, 27a, 27b
The other end of the trunnion 17a, 17b, 27a, 2
7b is moved in the axial direction to move the power rollers 18c, 18
Servo pistons 70a, 70b, 72a, 72b are provided as hydraulic actuators for tilting d, 20c, 20d.

The servo pistons 70a, 70b, 72
As a hydraulic control system for controlling the operation of a and 72b, a high side oil passage 74 connected to the high side oil chamber, a low side oil passage 76 connected to the low side oil chamber, and a high side oil passage 74 are connected. A shift control valve 78 having a port 78b connecting the port 78a and the low oil passage 76 is provided. An oil pump 80 is attached to the line pressure port 78c of the shift control valve 78.
And line pressure from a hydraulic source having a relief valve 82. Shift spool 78d of the shift control valve 78
Detects the axial direction and tilt direction of the trunnion 17a,
It is interlocked with a lever 84 and a recess cam 86 which feed back to the shift control valve 78. The shift sleeve 78e of the shift control valve 78 is driven by a step motor 88 so as to be displaced in the axial direction.

A CVT controller 110 is provided as an electronic control system for driving and controlling the step motor 88. The CVT controller 110 has a throttle opening sensor 112, an engine rotation sensor 114, an input shaft rotation sensor 116, and an output shaft rotation. Sensor (vehicle speed sensor) 11
Input information from 8 etc. is taken in.

[Power roller support structure] With respect to the support structure of the power roller 18c selected from the above power rollers 18c, 18d, 20c, 20d as a representative,
The configuration will be described with reference to FIG. The same structure is adopted for the other power rollers 18d, 20c, 20d.

The trunnion 17a is a transmission case 2
2, the power roller 18c is supported by a power roller accommodating portion 90 which is mounted so as to be tiltable around a trunnion tilting shaft 19a orthogonal to the power roller rotating shaft 15a, and which is formed at an upper position of the trunnion 17a. Has been done.

As shown in FIG. 3, the power roller 18c includes a power roller inner ring 91 frictionally contacting the input / output disks 18a and 18b, and the input / output disks 18a and 18b.
From the power roller inner ring 91 to the axial load applied to the power roller inner ring 91, and the power roller inner ring 9
1 and the power roller outer ring 92, a ball bearing (power roller bearing) 93 interposed between the input and output disks 18a,
18b, a first shaft portion 94 that receives a radial load input to the power roller inner ring 91, and a second shaft that is rotatably supported by the trunnion 17a and is connected to a position eccentric to the central axis of the first shaft portion 94. It is configured to have a pivot shaft 100 including a portion 100a.

The ball bearing 93 is shown in FIG. 4 (a) front view and FIG.
(B) As shown in the sectional view, the main body 99a and the ball bearing 93
And a lubricating oil passage 99 for holding the pocket 99b for rolling freely.
It is provided from c. The lubricating oil passage 99c is provided only on the power roller inner ring 91 side.

The power roller housing portion 90 of the trunnion 17a and the rear surface of the power roller outer ring 92 are vertically spaced apart by sandwiching the power roller rotating shaft 15a.
8c to the trunnion 17a, the trunnion tilting shaft 19
a so as to swing about the second shaft portion 100a along the left-right direction orthogonal to the a and the power roller rotation shaft 15a.
Thrust bearings 95, 95 are arranged.

The first shaft portion 94 is the inner ring 9 of the power roller.
1 is formed in a stepped shaft shape by a small diameter shaft portion 94a that rotatably supports the roller 1 through a roller bearing 96 and a large diameter shaft portion 94b that is fitted to the power roller outer ring 92 after processing. Further, a second lubricating oil passage 98 extending in the axial direction is formed in the first shaft portion 94, and one end of the radial lubricating oil passage 94 communicates with the second lubricating oil passage 98.
c and 94d are formed. And the radial oil passage 94c
The other end of is open to the outer circumference of the small-diameter shaft portion 94a,
The other end of the radial oil passage 94d is the outer circumference of the large-diameter shaft portion 94b, and the axial power roller outer ring 9 is larger than the oil groove 99c.
It opens to the 2 side.

The power roller outer ring 92 is a ball bearing 93.
Has a rolling element race surface 92a on the front side, a rolling element race surface 92b with the thrust bearing 95 on the back side, and an inner diameter hole 92c inserted into the large diameter shaft portion 94b of the first shaft portion 94. It is a member provided in the central portion.

The power roller outer ring 92 having the rolling element race surface 92a of the ball bearing 93 and the first shaft portion 94 are separately processed, and when assembled to the trunnion 17a, the inner diameter of the power roller outer ring 92 is set. The hole 92c and the large-diameter shaft portion 94b of the first shaft portion 94 are integrated by press fitting, bonding, shrink fitting, or the like.

In FIG. 3, 97 is a trunnion 1.
7a is a first lubricating oil passage, and 99 is a first lubricating oil passage 9
7 is a lubricating pipe for delivering the lubricating oil of No. 7 to the second lubricating oil passage 98.

Next, the operation will be described.

[Lubricating action] The lubricating oil cooled by an oil cooler (not shown) passes through the first lubricating oil passage 97 and the axial oil passage 98, and then the radial oil passage 94c and the radial oil passage 94d.
Emitted from and. At this time, since the radial oil passage 94d is provided closer to the power roller outer ring 92 in the axial direction than the oil groove 99c, part of the lubricating oil discharged from the radial oil passage 94d is the power roller outer ring of the retainer 99. Is supplied to the ball bearing 9 and flows through the gap between the retainer 99 and the power roller outer ring 92.
Lubricate the power roller outer ring 93, which is the rolling surface of the No. 3 roller. Further, most of the lubricating oil discharged from the radial oil passage 94d is supplied to the power roller inner ring 91 side provided with the oil groove, flows through the gap between the retainer 99 and the power roller inner ring and the oil groove 99c, and the power roller Lubricate the inner ring. As a result, durability can be further improved by efficiently mitigating a thermally severe environment.

The radial oil passage 94d can be machined only at a position axially separated from the end surface of the large diameter shaft portion 94b on the power roller inner ring 91 side, but the radial oil passage 94d cannot be processed. Since the large diameter shaft portion 94b is provided by being provided on the outer ring 92 side, the power roller can be downsized.

Further, since the power roller inner ring 91 has both a surface for transmitting power to and from the input / output disk and a ball bearing surface for rolling under the thrust force, it becomes a thermally severe environment. There is. However, by incorporating the oil groove 99c of the retainer 99 toward the inner ring side, the lubricating oil passage 94d
While a part of the lubricating oil supplied from flows through the gap between the cage 99 and the power roller outer ring, most of the lubricating oil flows through the gap between the cage 99 and the power roller inner ring 91. Durability can be improved by cooling and mitigating a thermally severe environment. Further, since the oil groove is provided only on one side, it is possible to shorten the molding time of the groove and reduce the cost.

Further, the oil groove 99c may be formed by forging, casting or resin integral molding. That is, the oil groove 99
When c is provided on both sides, because the axial thickness of the cage is insufficient, the oil groove could only be provided by shaving, but by providing the oil groove only on the power roller inner ring 91 side, The axial thickness t of the cage 99 is secured, and the oil groove of the cage can be formed by an inexpensive manufacturing method such as forging, casting, or resin integral molding.

(Other Embodiments) The toroidal type continuously variable transmission according to the present invention has been described above based on the embodiment. However, the specific configuration is not limited to this embodiment. Modifications and additions of the design are allowed without departing from the gist of the invention according to each claim of the claims.

For example, in the embodiment, the power roller supporting structure having a pivot shaft (eccentric shaft), which secures the lateral movement of the power roller by a so-called conventional swing mechanism, is shown. It can also be applied to a power roller support structure that ensures parallel movement in the left-right direction.

Further, in the embodiment, the example in which the ball bearing is used as the power roller bearing is shown, but the invention can be applied to the one using the tapered roller bearing and the like.

[Brief description of drawings]

FIG. 1 is an overall system diagram showing a toroidal type continuously variable transmission according to a first embodiment.

FIG. 2 is a shift control system system diagram showing the toroidal type continuously variable transmission according to the first embodiment.

FIG. 3 is a longitudinal sectional view showing a power roller support structure in the toroidal type continuously variable transmission according to the embodiment.

FIG. 4 is a view showing a front surface and a cross section of a ball bearing in the toroidal type continuously variable transmission according to the embodiment.

[Explanation of symbols]

12 torque converter 12a pump impeller 12b turbine runner 12c stator 12d lockup clutch 12e apply side oil chamber 12f release side oil chamber 14 input shafts 15a, 15b, 25a, 25b power roller rotating shaft 16 torque transmission shafts 17a, 17b, 27a, 27b Trunnion 18c, 18d, 20c, 20d Power rollers 18a, 18b, 20a, 20b Input / output disk 18 First continuously variable transmission mechanism 19a Trunnion tilting shaft 20 Second continuously variable transmission mechanism 22 Transmission case 24 Ball spline 26 Ball spline 27a , 27b trunnion 28 output gear 30 output shaft 30a gear 32 torque transmission mechanism 34 loading cam device 34a loading cam 36 forward / reverse switching mechanism 38 slide bearing 42 planetary gear mechanism 2a Pinion carrier 42b Ring gear 42c Sun gear 44 Forward clutch 46 Reverse brake 48 Transmission mechanism 50 Output shaft 52, 56 Gear 54 Idler gear 60 Propeller shaft 64 Control valve body 70a, 70b Servo piston 72a, 72b Servo piston 74 High side oil passage 76 Low side oil passage 78 Shift control valve 78a Port 78b Port 78c Line pressure port 78d Shift spool 78e Shift sleeve 80 Oil pump 82 Relief valve 84 Lever 86 Precess cam 88 Step motor 90 Power roller housing 91 Power roller inner ring 91a Rolling element race surface 91b Inner diameter hole 92 Power roller outer ring 92a Rolling element race surface 92b Rolling element race surface 92c Inner diameter hole 93 Ball bearing 94 First shaft portion 94a Small diameter shaft portion 94b Large diameter shaft DOO portion 95 thrust bearing 96 roller bearing 97 lubricating oil passage 98 lubricating oil passage 100 pivot shaft 100a second shaft portion 110 CVT controller 112 throttle opening degree sensor 114 engine rotation sensor 116 input shaft rotation sensor

Claims (3)

[Claims] 1. An input disk and an output disk, which are coaxially opposed to each other, a power roller sandwiched between the input and output disks so as to be capable of transmitting power, and a trunnion rotatably supporting the power roller, The power roller includes a power roller inner ring that makes frictional contact with the input / output disc, a power roller outer ring that receives an axial load that is input from the input / output disc to the power roller inner ring, and between the power roller inner ring and the power roller outer ring. In a toroidal type continuously variable transmission including a power roller bearing that is interposed and a shaft that receives an inner peripheral load that is input from an input / output disk to a power roller inner ring, a ball bearing of the power roller bearing An oil groove for lubrication extending from the inner circumference side to the outer circumference side is provided only on the inner ring side of the power roller of the cage that holds the roller Toroidal type continuously variable transmission, wherein the door. 2. The toroidal type continuously variable transmission according to claim 1, wherein the oil groove provided in the retainer is formed by forging, casting or resin integral molding. . 3. The toroidal type continuously variable transmission according to claim 1, wherein the shaft is integrally formed with a small-diameter shaft portion that rotatably supports the power roller inner ring via a bearing, and the power roller outer ring. And a large-diameter shaft portion that is formed into a stepped shaft shape, has an axial oil passage in the shaft axis, communicates the axial oil passage with one end side, and has the other end on the outer circumference of the large-diameter shaft portion. And a radial oil passage for supplying lubricating oil to the power roller bearing, and an opening on the other end side of the radial oil passage is provided on the outer ring side of the power roller in the axial direction with respect to the oil groove. A toroidal type continuously variable transmission characterized in that