JP2000346159A - Toroidal continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To facilitate the working of an oil feeding passage by forming the mutually opposed inside surfaces of both discs to circular sectional recessed surfaces, forming the circumferential surface of each power roller into a spherical protruding surface, and providing an oil feeding means on a control valve side relative to the radial direction of both the discs. SOLUTION: In a toroidal continuously variable transmission for performing the transmission of a rotating force between input and output discs whose mutually opposed inside surfaces are formed into circular sectional recessed surfaces through power rollers 8 having spherically protruding circumferential surfaces, and also changing the gear ratio between both the discs, the lubricating oil sent to a separating space 49 through an oil feed port 48 is supplied to the bearing around each power roller 8, 8 through oil passage 38, 38 provided within each trunnion 6, 6 in operation. The lubricating oil in the separating space 49 is also injected from a nozzle port 41a provided at the tip of a support post 22a'. Oil feeding means are provided on the control valve side in this way, whereby the working of the oil feeding passage can be facilitated.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement in a toroidal-type continuously variable transmission used as a transmission unit of a transmission for an automobile, for example, and realizes a structure which can be easily processed.

[0002]

2. Description of the Related Art The use of a toroidal-type continuously variable transmission as schematically shown in FIGS. This toroidal type continuously variable transmission is called a half toroidal type.
As disclosed in Japanese Patent Application Publication No. 65-65, an input disk 2 is supported concentrically with an input shaft 1, and an output disk 4 is fixed to an end of an output shaft 3 arranged concentrically with the input shaft 1. .
Trunnions 6, 6 are provided inside the casing containing the toroidal-type continuously variable transmission, at the axially intermediate positions of the input side and output side disks 2, 4. Each of the trunnions 6 is twisted so as not to intersect with the center axis in a direction perpendicular to the direction of the input shaft 1 and the output shaft 3 (the left-right direction in FIGS. 2 and 3). Swings about the pivots 5 at the position of.

That is, each of the trunnions 6, 6 has the pivots 5, 5 concentrically provided on the outer surfaces of both ends. In addition, a base end of the displacement shafts 7, 7 is supported at an intermediate portion between the trunnions 6, 6, and the trunnions 6, 6 are pivoted about the pivots 5, 5, whereby
The tilt angles of the displacement shafts 7, 7 can be adjusted freely. Power rollers 8 are rotatably supported around the displacement shafts 7 supported by the trunnions 6 respectively. And each of these power rollers 8, 8 is
The input side and output side disks 2 and 4 are sandwiched between inner surfaces 2a and 4a facing each other. Each of the inner side surfaces 2a, 4a has a concave section obtained by rotating an arc around the pivot 5 as described above.
Each of the power rollers 8, 8 formed on a spherical convex surface
Are brought into contact with the inner side surfaces 2a, 4a.

A loading device 9 of a loading cam type is provided between the input shaft 1 and the input disk 2, and the input device 2 is elastically pressed toward the output disk 4 by the pressing device 9. It is free. The pressing device 9 includes a cam plate 10 that rotates together with the input shaft 1 and a retainer 1.
1 and a plurality (for example, four) of rollers 12 and 12 held rotatably. On one side surface (the right side surface in FIGS. 2 and 3) of the cam plate 10, a cam surface 13 which is uneven in the circumferential direction is formed, and the outer side surface of the input side disk 2 (the left side surface in FIGS. 2 and 3). 3), a cam surface 14 having a similar shape is formed. The plurality of rollers 12 are rotatably supported about a radial axis with respect to the center of the input shaft 1.

When the cam plate 10 rotates with the rotation of the input shaft 1 when the toroidal type continuously variable transmission having the above-described configuration is used, the cam surface 13 causes the plurality of rollers 12, 12 to move to the input side disk. 2 against the cam surface 14 formed on the outer surface. As a result, the input side disk 2 is pressed by the plurality of power rollers 8, and at the same time, the input disk 2 is pressed based on the pressing of the cam surfaces 13, 14 and the plurality of rollers 12, 12. The side disk 2 rotates. Then, the rotation of the input side disk 2 is transmitted to the output side disk 4 via the plurality of power rollers 8, and the output shaft 3 fixed to the output side disk 4 rotates.

When the rotational speed ratio (speed change ratio) between the input shaft 1 and the output shaft 3 is changed, and when deceleration is first performed between the input shaft 1 and the output shaft 3, each of the pivots 5 The trunnions 6, 6 are swung in a predetermined direction as a center. The peripheral surfaces 8a, 8a of the power rollers 8, 8 are shown in FIG.
As shown in FIG. 5, the displacement shafts 7, 7 are inclined so as to abut against the central portion of the inner surface 2a of the input disk 2 and the outer peripheral portion of the inner surface 4a of the output disk 4, respectively. Conversely, when increasing the speed,
, Each of the trunnions 6 is swung in the opposite direction. The peripheral surface 8 of each of the power rollers 8
As shown in FIG. 3, each of the displacement shafts 7a and 8a comes into contact with a portion of the inner surface 2a of the input disk 2 near the outer periphery and a portion of the inner surface 4a of the output disk 4 near the center. , 7 are tilted. If the inclination angles of the displacement shafts 7, 7 are set between those in FIGS. 2 and 3, an intermediate speed ratio can be obtained between the input shaft 1 and the output shaft 3.

FIGS. 4 and 5 show Japanese Utility Model Application No. 63-69293.
FIG. 1 shows an example of a more specific toroidal type continuously variable transmission described in the microfilm of Japanese Utility Model Application Publication No. Hei 1-173552. The input-side disk 2 and the output-side disk 4 are rotatably supported around a cylindrical input shaft 15 via needle bearings 16 and 16, respectively.
Further, the cam plate 10 is spline-engaged with the outer peripheral surface of the end portion (the left end portion in FIG. 4) of the input shaft 15, and is prevented from moving away from the input side disk 2 by the flange portion 17. The cam plate 10 and the rollers 12, 12 constitute a pressing device 9 for rotating the input disk 2 while pressing the input disk 2 toward the output disk 4 based on the rotation of the input shaft 15. . The output side disk 4
The output gear 18 is connected by keys 19, 19 so that the output disk 4 and the output gear 18 rotate synchronously.

The pivots 5, 5 provided at both ends of the pair of trunnions 6, 6 respectively swing on the pair of support plates 20, 20 in the axial direction (the front-back direction in FIG. 4, the left-right direction in FIG. 5). It is supported so as to be freely displaceable. That is, the pair of support plates 20, 20 are housed in a housing 21 in which a main body of the toroidal-type continuously variable transmission is housed, and both the input-side and output-side disks 2,
4 are arranged substantially parallel to each other with the support posts 22a and 22b being slightly displaceable about the support posts 22a and 22b, respectively. Then, inside the circular holes 23, 23 formed in the portions where the support plates 20, 20 are aligned with each other,
Axis 5,5 provided at both ends of each trunnion 6,6
Are supported by the radial needle bearings 24, 24 so as to be swingable and displaceable in the axial direction. Each of the above circular holes 2
3, 23 and the respective pivots 5, 5 are connected to the two discs 2,
4 center axis direction (left-right direction in FIG. 4, front-back direction in FIG. 5)
And in the direction perpendicular to (the front and back direction in FIG. 4 and the left and right direction in FIG. 5).

In this manner, circular holes 25, 25 are formed in the middle portions of the trunnions 6, 6 whose both ends are supported by the support plates 20, 20, respectively.
The displacement shafts 7, 7 are provided in these circular holes 25, 25, respectively.
I support. Each of these displacement shafts 7, 7 is parallel and eccentric to the support shafts 26, 26 and the pivot shafts 27, 2,
7 respectively. Each of the support shafts 26,
26 is rotatably supported inside the circular holes 25, 25 via radial needle bearings 28, 28.
In addition, the power rollers 8, 8 are provided around the respective pivot shaft portions 27, 27 via separate radial needle bearings 29, 29 corresponding to the radial rolling bearings described in the claims.
It is rotatably supported.

Note that the pair of displacement shafts 7 are provided at positions 180 ° opposite to the input shaft 15. or,
The direction in which the respective pivot shaft portions 27, 27 of the respective displacement shafts 7, 7 are eccentric with respect to the respective support shaft portions 26, 26 is the same as the rotation direction of the input side and output side disks 2, 4. (In FIG. 5, the left and right directions are reversed). The eccentric direction is a direction substantially orthogonal to the direction in which the input shaft 15 is provided. Therefore, the power rollers 8 are supported so as to be slightly displaceable in the axial direction of the input shaft 15 (the left and right direction in FIG. 4 and the front and back directions in FIG. 5). As a result, the power rollers 8, 8 tend to be displaced in the axial direction of the input shaft 15 due to elastic deformation of the constituent members based on a large load applied to the constituent members in the state of transmission of the rotational force. In this case, the displacement can be absorbed without applying excessive force to the components.

Further, between the outer surfaces of the power rollers 8, 8 and the inner surfaces of the intermediate portions of the trunnions 6, 6, the power rollers 8, 8 are arranged in order from the outer surface. Thrust ball bearing 3 equivalent to thrust rolling bearing
0, 30 and thrust needle bearings 31, 31 are provided. Of these, the thrust ball bearings 30, 30 allow rotation of the power rollers 8, 8, while supporting the load in the thrust direction applied to the power rollers 8, 8. Further, each of the thrust needle bearings 31,
The support shafts 27, 27 and the outer races 32, 32 support the thrust load applied from the power rollers 8, 8 to the outer races 32, 32 constituting the thrust ball bearings 30, 30, respectively. However, it is possible to swing about the support shafts 26, 26.

Driving rods 33, 33 are connected to one end (the left end in FIG. 5) of each of the trunnions 6, 6, and a driving piston 34, 34 are fixed. Then, these drive pistons 34, 34 are respectively
5, 35 are fitted in an oil-tight manner. In a valve body 37 provided adjacent to a cylinder body 36 provided with both drive cylinders 35, 35, there is provided a control valve (shown in the figure) for controlling the supply and discharge of pressure oil into each of the drive cylinders 35, 35. (Omitted).

Further, oil passages 38, 38 are provided inside the trunnions 6, 6, and these oil passages 38, 38 are provided.
Through an upstream oil passage 39 provided in each of the drive rods 33, 33 to a lubricating oil supply unit, not shown, such as an oil supply pump. The first oil supply means including the respective oil passages 38, 38 includes the thrust ball bearings 30, 30 and the radial needle bearings 29, 29 during operation of the toroidal-type continuously variable transmission. Lubricating oil is supplied to the bearings around the power rollers 8. Then, even when the power rollers 8 rotate at high speed, the durability of the bearings around the power rollers 8 can be sufficiently ensured.

On the other hand, of the pair of support plates 20, 20, a support post 22b for supporting the support plate 20 on the side opposite to the valve body 37 (right side in FIG. 5, upper side in FIG. 6 described later). , A fueling nozzle 40 constituting a second fueling means is supported and fixed. This refueling nozzle 40 has
As shown in FIG. 6 showing a more specific structure, a plurality of nozzle holes 41 are provided. These nozzle holes 41, 41
Are the inner surfaces 2 of the input side and output side disks 2 and 4 respectively.
a, 4a or the peripheral surface 8a of each of the power rollers 8, 8;
8a. During operation of the toroidal-type continuously variable transmission, lubricating oil (traction oil) is fed into the oil supply nozzle 40 from the lubricating oil supply unit, and the lubricating oil is supplied from the nozzle holes 41, 41 to the surfaces 2a, 4a.
a, 8a, the two disks 2, 4
The lubricating oil is supplied to a contact portion (traction portion) between the inner side surfaces 2a, 4a and the peripheral surfaces 8a, 8a of the power rollers 8, 8, respectively. The rolling fatigue life of each of the surfaces 2a, 4a and 8a can be sufficiently ensured.

In the case of the toroidal type continuously variable transmission configured as described above, the rotation of the input shaft 15 is transmitted to the input side disk 2 via the pressing device 9. The rotation of the input disk 2 is transmitted to the output disk 4 via the pair of power rollers 8, 8, and the rotation of the output disk 4 is extracted from the output gear 18. When changing the rotation speed ratio between the input shaft 15 and the output gear 18, the pair of drive pistons 34, 34 are displaced in opposite directions. The pair of trunnions 6, 6 are displaced in opposite directions with the displacement of the driving pistons 34, 34. For example, the lower power roller 8 in FIG. Are displaced to the left in FIG. As a result, these power rollers 8, 8
The direction of the tangential force acting on the contact portions between the peripheral surfaces 8a, 8a and the inner surfaces 2a, 4a of the input side disk 2 and the output side disk 4 changes. Then, with the change in the direction of this force, each of the trunnions 6, 6
Swing in opposite directions about pivots 5, 5 pivotally supported by 20. As a result, as shown in FIGS. 2 and 3 described above, the contact positions between the peripheral surfaces 8a, 8a of the power rollers 8, 8 and the inner surfaces 2a, 4a change, and the input shaft 15 The rotation speed ratio with the output gear 18 changes.

The input shaft 15 and the output gear 1 are
When transmitting the rotational force to the power rollers 8, the power rollers 8, 8 are displaced in the axial direction of the input shaft 15 based on the elastic deformation of the constituent members. Each of the displacement shafts 7, 7 pivotally supporting 8 rotates slightly about each of the support shafts 26, 26. As a result of this rotation, the outer ring 3 of each of the thrust ball bearings 30,
The outer surfaces of the trunnions 6, 32 and the inner surfaces of the trunnions 6, 6 are relatively displaced. Since the thrust needle bearings 31, 31 exist between the outer surface and the inner surface, the force required for the relative displacement is small. Therefore, the force for changing the inclination angle of each of the displacement shafts 7 can be small as described above.

[0017]

In the case of the conventional structure shown in FIGS. 5 and 6, first lubricating means for supplying lubricating oil to each of the power rollers 8 and 8 and a lubricating oil for the traction portion are provided. And a second oil supply means for supplying the oil on the input side and the output side disks 2 and 4 on the opposite sides in the diametrical direction. Therefore, an oil supply passage for supplying lubricating oil to the first and second oil supply means is required independently of each other, and a large space is required for a supply pipe.
In particular, the second lubricating means for supplying lubricating oil to the traction portion includes the cylinder body 36 and the valve body 3.
7, the provision of an oil supply passage for supplying lubricating oil to the second oil supply means is troublesome, and causes an increase in cost. The toroidal-type continuously variable transmission of the present invention has been invented in view of such circumstances.

[0018]

The toroidal-type continuously variable transmission according to the present invention, like the above-mentioned conventional toroidal-type continuously variable transmission, has an input side rotatably supported concentrically and independently of each other. A plurality of trunnions oscillating about a pair of concentric pivots in a twisted position perpendicular to the direction of the central axes of the output side disks and perpendicular to the direction of the central axes of the two disks. And a displacement shaft supported for each of these trunnions, and rotatably supported around each of the displacement shafts via radial rolling bearings,
A power roller sandwiched between the inner surfaces of the input and output disks; a thrust rolling bearing provided between an outer surface of each of the power rollers and an inner surface of each of the trunnions; A drive rod having a base end connected to one of the pivots provided for each pair, a hydraulic actuator for displacing each of the drive rods in the axial direction, and each of these actuators. And a control valve provided adjacent to each of the actuators and an oil passage provided inside each of the trunnions to switch between the supply and discharge states of the pressure oil. First lubricating means for supplying lubricating oil to the rolling bearing and the thrust rolling bearing, and a contact portion between an inner surface of each of the disks and a peripheral surface of each of the power rollers. And a second oil supply means for supplying a lubricating oil. The inner surfaces of the two disks facing each other are concave surfaces having a circular cross section, and the peripheral surfaces of the power rollers are spherical convex surfaces. It is made to contact the side. In particular, in the toroidal-type continuously variable transmission according to the present invention, the second oil supply means is provided on the control valve side with respect to the diameter direction of the two disks.

[0019]

With the toroidal-type continuously variable transmission of the present invention constructed as described above, the function of transmitting the torque between the input side disk and the output side disk, and the speed ratio between these two disks. Is the same as that of the conventionally known toroidal-type continuously variable transmission as described above. In particular, in the case of the toroidal-type continuously variable transmission of the present invention, the second oil supply for supplying lubricating oil to the contact portion between the inner surfaces of both the input and output disks and the peripheral surface of each power roller. Since the means is provided on the control valve side, machining of the oil supply passage for supplying the lubricating oil to the second oil supply means is facilitated. Further, the space for the supply pipe can be reduced.

[0020]

FIG. 1 shows a first embodiment of the present invention.
An example is shown. The features of the present invention are the inner surfaces 2a and 4a of the input and output disks 2 and 4 (see FIGS. 2 to 4).
And a contact portion between the power roller 8 and the peripheral surface 8a of each power roller 8;
That is, it is located in the second oil supply means for supplying lubricating oil, that is, traction oil, to the traction section. Since the structure and operation of the other parts are the same as those of the above-described conventional structure, the illustration and description of the equivalent parts are omitted or simplified, and will not be described below with the characteristic part of the present invention and the above-described prior art part. The description will focus on the parts.

On a lower surface of a cylinder body 36 fixed in the housing 21, a valve body 37 having a built-in control valve for controlling pressure oil supplied to and discharged from drive cylinders 35 provided in the cylinder body 36 is provided. It is fixed. A support hole 42 having a circular cross section is provided at the center of the cylinder body 36, and a portion having a larger diameter than the support hole 42 is provided at a portion of one side (the upper surface in FIG. 1) of the valve body 37 which is aligned with the support hole 42. Recesses 43 are respectively formed. Then, inside the support holes 42 and the concave portions 43,
The support post 22a 'is supported and fixed.

In the support post 22a ', the cross-sectional shape of the distal end portion 44 is oval, the cross-sectional shape of the outer peripheral surface of the proximal end portion 46 is circular, and a mounting flange 45 is fixed to the proximal end surface. The outer diameter of the base end 46 is substantially equal to the inner diameter of the support hole 42, and the base end 46 is connected to the support hole 42.
In addition, the inside can be freely fitted without play. To support and fix the support post 22a 'to the cylinder body 36, the base end 46 is fitted in the support hole 42, and the mounting flange 45 is pushed to one side (the lower surface in FIG. 1) of the cylinder body 36. In this state, the mounting flange 45 is screwed and fixed to the cylinder body 36. Further, in this state, the mounting flange 45 enters the concave portion 43 to prevent interference with the valve body 37.

The intermediate portion of one (lower in FIG. 1) support plate 20 is attached to the tip end 44 of the support post 22a 'fixed in the casing 5 as described above in one direction (FIG. 1).
(Clockwise and counterclockwise directions). That is, the distal end portion 44 is loosely fitted in the rectangular locking hole 47 formed in the middle portion of the support plate 20 in the length direction (the left-right direction in FIG. 1) of the support plate 20 and in the width direction (FIG. 1). (Front and back direction) are fitted without play.

Then, through the support posts 22a ', the inner surfaces 2 of the input side and output side disks 2, 4 are formed.
The lubricating oil (traction oil) can be freely supplied to the traction portion, which is the contact portion between the power rollers a and 4a and the peripheral surfaces 8a of the power rollers 8,8. For this reason, in the case of this example, lubricating oil can be freely fed into the concave portion 43 from an oil supply pump (not shown). That is, the oil supply port 48 provided on the lower surface of the valve body 37 communicates with the concave portion 43 via the branch flow space 49 and the throttle channels 50, 50. Also, an oil supply passage 51 is provided in the support post 22a '.
The above-described surfaces 2a, 4a
Nozzle holes 41a, 41a facing a, 8a are formed, respectively.

The branch space 49 is connected to the oil passages 38, 38 provided inside the trunnions 6, 6, by the branch passages 52, 52 provided in the valve body 37, and the drive rods 33, It communicates with the upstream oil passages 39, 39 provided in the inside 33. Each of these upstream oil passages 3
A well-known communication means is provided between the upstream and downstream oil passages 39, 39, regardless of the axial displacement of the drive rods 33, 33. The communication between the flow path 39 and each of the branch passages 52 is not interrupted.

In the illustrated example, the upper support post 22
A stopper plate 53 for preventing the swing angle of each of the trunnions 6, 6 from becoming excessive is provided at the tip of b '. Further, a cable 54 is crossed between the trunnions 6, 6 to cross each other, so that the swing angles of the trunnions 6, 6 are mechanically synchronized. Note that the cable 54 and the stopper plate 53 are conventionally known, and have nothing to do with the gist of the present invention. The outer peripheral surface of the distal end of the upper support post 22b 'is a spherical convex surface, and this distal end is fitted in a circular locking hole 47a formed in an intermediate portion of the upper support plate 20. . Therefore, the upper support plate 20 is connected to the upper support post 22b '.
Are supported so as to be freely displaceable in each direction.

The toroidal-type continuously variable transmission of the present invention configured as described above has a structure similar to that of the conventional structure described above.
Rotational force is transmitted between the input-side disk 2 and the output-side disk 4, and the speed ratio between the disks 2 and 4 is changed. In operation, the lubricating oil sent from the oil supply port 48 into the diversion space 49 is supplied from the oil passages 38, 38 provided inside the trunnions 6, 6 to the bearings around the power rollers 8, 8. To supply.
At the same time, the lubricating oil in the diversion space 49 is supplied from the nozzle holes 41a, 41a provided at the tip of the support post 22a 'to the respective surfaces 2a, 4a constituting the traction portion.
a, 8a.

In the case of the toroidal type continuously variable transmission of the present invention, which is constructed as described above and operates as described above, the inner side surfaces 2a, 4a of the input side and output side disks 2, 4 and the respective Since the second oil supply means for supplying the lubricating oil to the traction part which is the contact part of the power rollers 8, 8 with the peripheral surfaces 8a, 8a is provided on the control valve side, the second oil supply means is provided with the second oil supply means. Processing of an oil supply passage for supplying lubricating oil is facilitated. or,
The installation space for the refueling passage can be reduced.
The amount of lubricating oil supplied to each part can be arbitrarily adjusted by changing the area of a throttle provided in the middle of each lubricating means.

[0029]

Since the present invention is constructed and operates as described above, it is possible to realize a low-cost toroidal type continuously variable transmission which is easy to process.

[Brief description of the drawings]

FIG. 1 shows an example of an embodiment of the present invention,
The figure corresponding to A section.

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

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

FIG. 4 is a sectional view showing an example of a specific structure of the toroidal-type continuously variable transmission.

FIG. 5 is a sectional view taken along line AA of FIG. 4;

FIG. 6 is a view similar to FIG. 5, showing a more specific structure.

[Explanation of symbols]

 Reference Signs List 1 input shaft 2 input side disk 2a inner surface 3 output shaft 4 output side disk 4a inner surface 5 pivot 6 trunnion 7 displacement shaft 8 power roller 8a peripheral surface 9 pressing device 10 cam plate 11 retainer 12 roller 13, 14 cam surface 15 Input shaft 16 Needle bearing 17 Flange 18 Output gear 19 Key 20 Support plate 21 Housing 22a, 22b, 22a ', 22b' Support post 23 Circular hole 24 Radial needle bearing 25 Circular hole 26 Support shaft 27 Rotation shaft 28 Radial Needle bearing 29 Radial needle bearing 30 Thrust ball bearing 31 Thrust needle bearing 32 Outer ring 33 Drive rod 34 Drive piston 35 Drive cylinder 36 Cylinder body 37 Valve body 38 Oil passage 39 Upstream oil passage 40 Oil supply nozzle 41, 41a Nozzle hole 42 support 43 recess 44 tip 45 mounting flange 46 proximal end 47,47a locking hole 48 fuel supply port 49 diversion space 50 throttle channel 51 the oil supply passage 52 split passageway 53 stopper plate 54 Cable

Claims (1)

[Claims] An input-side and an output-side disk, which are rotatably supported concentrically and independently of each other, and have a twist that is perpendicular to the direction of the center axis of these two disks and does not intersect the center axis. A plurality of trunnions swinging about a pair of concentric pivots at a position, displacement shafts supported for each of the trunnions, and rotatable around the respective displacement shafts via radial rolling bearings And a power roller sandwiched between the inner surfaces of the input and output disks, and a thrust rolling bearing provided between the outer surface of each of the power rollers and the inner surface of each of the trunnions. A drive rod having a base end connected to one of the pivots provided for each trunnion, and an oil for displacing each of the drive rods in the axial direction. A pressure-type actuator and a control valve provided adjacent to each of these actuators for switching the supply / discharge state of the pressure oil to and from each of the actuators, and an oil passage provided inside each of the trunnions, First oil supply means for supplying lubricating oil to the radial rolling bearing and the thrust rolling bearing for supporting the power rollers, and a contact portion between the inner surfaces of both disks and the peripheral surfaces of the power rollers. Second lubricating means for supplying lubricating oil to the inner surfaces of the two disks, each of which has an arc-shaped concave surface in cross section, and a peripheral convex surface of each of the power rollers. In the toroidal-type continuously variable transmission in which the peripheral surface of each of the power rollers and the inner surface of each of the disks are brought into contact with each other, the second oiling means is disposed in the diameter direction of both of the disks. To, toroidal type continuously variable transmission, characterized in that provided on the control valve side.