JP2001012574A - Toroidal type continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress a sliding from occurring at a contact part of an input/ output disc with a power roller and also reduce a variation in transmission ratio due to an increase of surface pressure or deformation by eccentric load by assuring a smooth parallel movement motion of the power roller even if a vertical power transmitting force acts on the power roller, while a power roller supporting structure supporting the power roller rotatably and movably in lateral direction is adopted. SOLUTION: First roller bearings 96a, 96a supporting a pressing force 100 acting on a power roller in rotating axis direction and a pair of second roller bearings 96b, 96b supporting a power transmitting force acting on a power roller in a swing axis direction (vertical direction) crossed perpendicular to the rotating axis are disposed between an outer ring 94 and a power roller storing part 91 along the lateral direction of the power roller 18c.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention belongs to the technical field of a toroidal type continuously variable transmission applied to a vehicle or 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 consideration of ease of driving and improvement of fuel efficiency. The V-belt type has already been put to practical use. On the other hand, there is a demand for a CVT having a larger capacity and a higher responsiveness than a V-belt. To achieve this possibility, a traction drive type toroidal type continuously variable transmission (hereinafter, toroidal type CVT) that transmits power by shearing an oil film is known. Toroidal type CVTs can be classified into full toroidal types and half toroidal types based on their shapes. Of the two types, in the full toroidal type CVT, no thrust force is applied to the power roller. On the other hand, in the half toroidal type CVT, a thrust force is applied to the power roller, and a bearing is required to receive this force. This bearing performance has a significant effect on efficiency. However, in the half toroidal type CVT, the tangent drawn at the two contact points between the disk and the power roller has an intersection, and the locus of the intersection is near the rotation axis in the entire speed change range, so that the spin loss is full toroidal. The half toroidal type CVT is selected in consideration of these advantages and disadvantages compared to the type CVT, and research and development are proceeding.

The shifting operation of the half toroidal type CVT is performed by a power roller supporting member (hereinafter referred to as a trunnion).
In this mechanism, a slight displacement is applied in a direction perpendicular to the axis of rotation of the power roller and the axis of rotation of the disk to generate a side slip force, thereby obtaining a tilting force.

[0004] As described above, the power roller pressed between the input and output disks of the toroidal type CVT so as to be able to transmit power is, for example, via a pivot shaft as described in Japanese Patent Application Laid-Open No. 6-129509. Supported by trunnions.

[0005] However, this pivot shaft is
It has eccentric both ends, rotatably supports the power roller at one end, and rotatably supports the trunnion at the other end, and is eccentric to allow the power roller to swing around the other end. Because it is a shaped shaft member, when the power roller moves in the left and right direction due to swinging motion, it also displaces in the up and down direction, it is difficult to process, the problem is that the component cost is high, and to secure the support strength There is a problem that the trunnion becomes large and heavy.

In order to solve this problem, for example, in Japanese Unexamined Patent Publication No. 7-198014, as shown in FIG. 18, a power roller accommodating portion 91 arranged in the rotation direction of the input / output disk is formed in the trunnion 38. A power roller supporting structure in which the pivot shaft is omitted by supporting the power roller 35 so as to be able to move in parallel in the power roller storage portion 91 of the trunnion 38 has been proposed.

[0007]

However, in the power roller supporting structure of the conventional toroidal type continuously variable transmission, the power transmission force acting on the power roller 35 in the vertical direction due to the power transmission is reduced by the power of the trunnion. When the power transmission force in the vertical direction acts, the power roller 35 and the power roller housing inner wall 91a of the trunnion 38 are pressed against each other and slid when the above-described vertical power transmission force acts, and the sliding resistance is reduced. Large and smooth power roller 35
There is a problem that hinders the parallel movement.

[0008] The problem to be solved by the present invention is light weight,
Even though the power roller support structure without a pivot shaft is compact, it ensures smooth translation of the power roller even when power transmission force is applied to the power roller in the vertical direction. An object of the present invention is to provide a toroidal-type continuously variable transmission that can suppress occurrence of slippage or the like at a contact portion, and can reduce an increase in surface pressure due to an unbalanced load and a change in a gear ratio due to deformation.

[0009]

According to the first aspect of the present invention, 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 transmit power, and the power roller A power roller supporting member that is rotatable with respect to the power roller storage portion, and that is capable of tilting about a swing axis orthogonal to the power roller rotation axis while supporting the parallel movement in the left and right direction. An inner ring that frictionally contacts the input / output disk with the power roller, and an outer ring that rotatably supports the inner ring,
A toroidal configured to have a ball bearing interposed between the inner ring and the outer ring, and to receive a contact load input to the inner ring from the input / output disk due to the pinching pressure by the outer ring via the ball bearing. In the type of continuously variable transmission, a first roller bearing for supporting a pressing force acting in the front-rear direction between the outer ring and the power roller housing portion, and a pair of second rollers for supporting a power transmission force acting in a vertical direction. The bearings are arranged along the left and right directions of the power roller.

According to a second aspect of the present invention, in the toroidal type continuously variable transmission according to the first aspect, the shape of the outer ring is
The upper and lower portions of the outer peripheral surface have a flat portion extending in the left-right direction, and the power roller storage portion has a flat portion extending in the left-right direction at a portion of the power roller storage portion facing the flat portion. And the second roller bearing is disposed between two sets of opposed flat portions.

According to the third aspect of the present invention, there are provided an input disk and an output disk coaxially opposed to each other, a power roller pressed between the input and output disks to transmit power.
A power roller capable of tilting around a swing axis orthogonal to the power roller rotation axis while supporting the power roller rotatably with respect to the power roller storage portion and in such a manner as to be able to move in parallel in the left-right direction. A supporting member, the power roller having an inner ring that frictionally contacts an input / output disk, an outer ring that rotatably supports the inner ring, and a ball bearing interposed between the inner ring and the outer ring. In a toroidal-type continuously variable transmission that receives a contact load input from the input / output disk to the inner ring due to the squeezing pressure by an outer ring via a ball bearing, between the outer ring and the power roller housing portion A pair of common roller bearings that support both the pressing force acting in the front-rear direction and the power transmission force acting in the up-down direction are provided at the upper and lower positions distant from the power roller rotation shaft. And wherein the inclined arranged along.

According to a fourth aspect of the present invention, in the toroidal type continuously variable transmission according to the third aspect, the shape of the outer ring is
A shape having an inclined plane portion extending in the left-right direction at an up-down position away from the power roller rotation axis, and the shape of the power roller storage portion is changed to a portion of the power roller storage portion facing the inclined flat portion in the left-right direction. The common roller bearing is disposed between two sets of opposed inclined plane portions.

According to a fifth aspect of the present invention, there is provided an input disk and an output disk coaxially opposed to each other, and a power roller pressed between the input and output disks to transmit power.
A power roller capable of tilting around a swing axis orthogonal to the power roller rotation axis while supporting the power roller rotatably with respect to the power roller storage portion and in such a manner as to be able to move in parallel in the left-right direction. A supporting member, the power roller having an inner ring that frictionally contacts an input / output disk, an outer ring that rotatably supports the inner ring, and a ball bearing interposed between the inner ring and the outer ring. In a toroidal-type continuously variable transmission that receives a contact load input from the input / output disk to the inner ring due to the squeezing pressure by an outer ring via a ball bearing, between the outer ring and the power roller housing portion A pair of common roller bearings that support both the pressing force acting in the front-rear direction and the power transmission force acting in the vertical direction are provided in the vertical position close to the power roller rotating shaft in the left-right direction of the power roller. And wherein the inclined arrangement I.

According to a sixth aspect of the invention, in the toroidal type continuously variable transmission according to the third to fifth aspects, a contact line connecting a contact point of the ball bearing with an inner raceway and a contact point of an outer raceway. The inclination is shifted from the front-rear direction so that the ball bearing bears the radial load acting on the inner ring of the power roller, and the inner ring of the power roller is a solid inner ring having no shaft through hole. And

According to a seventh aspect of the present invention, in the toroidal type continuously variable transmission according to the sixth aspect, the thickness of the solid inner ring in the front-rear direction is increased, and the area of the spherical portion that contacts the input / output disk is increased. It has a dome shape.

According to an eighth aspect of the present invention, in the toroidal type continuously variable transmission according to the sixth or seventh aspect, a lubricating oil reservoir is provided between the solid inner ring and the outer ring, and the lubricating oil reservoir is provided from the power roller supporting member. The lubricating structure is characterized in that the lubricating oil supplied through the first lubricating oil supply pipe and the outer ring shaft oil passage is guided to the ball bearing via the lubricating oil reservoir.

According to a ninth aspect of the present invention, in the toroidal-type continuously variable transmission according to the eighth aspect, the space between the oil sump recess formed on the solid inner ring and the oil sump convex formed on the outer ring is formed. And a lubricating oil reservoir.

According to a tenth aspect of the present invention, in the toroidal type continuously variable transmission according to the eighth or ninth aspect, the outer ring shaft oil passage has an inclination angle with respect to the front-rear direction. Road.

According to the eleventh aspect of the present invention, in the toroidal type continuously variable transmission according to the eighth to tenth aspects,
The lubricating oil reservoir is provided with a lubricating oil guide structure for guiding lubricating oil to an area where the load of the ball bearing is large.

According to a twelfth aspect of the present invention, in the toroidal-type continuously variable transmission according to the eighth aspect, the outer ring shaft oil passage for guiding lubricating oil to a lubricating oil reservoir having an oil reservoir recess formed in the solid inner ring. , The opening end of which is close to the oil reservoir recess.
A lubricating oil supply pipe is provided.

[0021]

According to the first aspect of the present invention, at the time of power transmission, a contact load input from the input / output disk to the inner race of the power roller due to the squeezing force is received by the outer race via a ball bearing. The first roller bearing disposed between the outer ring and the power roller housing supports the pressing force acting in the front-rear direction of the power roller. further,
The pair of second roller bearings disposed between the outer ring and the power roller storage section support the power transmission force acting in the vertical direction of the power roller. Therefore, even if the power transmission force in the vertical direction acts on the power roller, this load is supported by the second roller bearing. The power roller moves left and right due to the low rolling resistance while rolling. That is, even if the power transmission force in the vertical direction acts on the power roller, a smooth parallel movement of the power roller in the left and right direction is ensured. As a result, when the input / output disk is deformed or misalignment that can occur during assembly occurs, it is possible to smoothly perform the horizontal translation of the power roller in order to absorb these positional deviations, The pressing force applied from the input disk side to the power roller and the pressing force applied from the output disk side are uniformly maintained, and it is possible to suppress the occurrence of slippage at the contact portion between the input / output disk and the power roller. . Also, since there is no need to provide a structure for holding a pivot shaft for supporting the power roller on the power roller support member,
An increase in stress of the power roller support member can be prevented, the rigidity can be improved, and deformation can be suppressed. Therefore, the contact position between the input / output disk and the power roller does not largely deviate from the design value, and the effect of increasing the surface pressure due to the unbalanced load and reducing the change in the gear ratio due to deformation can be obtained.

According to the second aspect of the present invention, a power roller having a shape having a flat portion extending in the left-right direction at upper and lower portions of the outer peripheral surface and a flat portion extending in the left-right direction at a portion opposed to the flat portion. The storage portion forms two sets of opposed flat portions, and the second roller bearing is disposed between the two sets of opposed flat portions. Therefore, in addition to the effect of the invention described in claim 1, the length of the opposed flat portion in the left-right direction is extended,
It is possible to increase the number of second roller bearings, and by increasing the number of second roller bearings, it is possible to obtain the effect of increasing the capacity for power transmission force (vertical load).

According to the third aspect of the present invention, at the time of power transmission, a contact load input from the input / output disk to the inner race of the power roller due to the squeezing pressure is received by the outer race via the ball bearing. A pair of common roller bearings disposed between the outer ring and the power roller storage portion and inclined vertically at a distance from the power roller rotation axis, the pressing force acting in the front-rear direction of the power roller, and the power roller The power transmission force acting in the vertical direction is supported together. Therefore, even if a load in the left-right direction is applied while the power transmission force in the vertical direction is acting on the power roller, the power roller moves in the left-right direction due to the low rolling resistance of the common roller bearing while rolling, so The parallel movement of the power roller is ensured, and the same effect as the first aspect of the invention can be obtained. In addition, there is no need to manage the clearance of the second roller bearing that supports the power transmission force in the vertical direction, and the number of parts is reduced. Furthermore, since the point of application of the load acting on the power roller support member is not at the flat portion of the power roller storage portion but at both ends, it is possible to reduce the deformation of the power roller support member. .

According to the fourth aspect of the present invention, an outer ring having an inclined plane portion extending in the left-right direction at a vertical position distant from the power roller rotation shaft, and an inclined plane portion extending in the left-right direction at a portion opposed to the inclined plane portion. The power roller accommodating portion has two sets of opposed inclined flat portions, and a common roller bearing is arranged between the two sets of opposed inclined flat portions. Therefore, in addition to the effect of the third aspect of the present invention, the number of common roller bearings can be increased by increasing the length of the opposed inclined flat portions in the left-right direction, and the number of common roller bearings can be increased. Thus, the effect of increasing the supporting capacity for the pressing force and the power transmission force is obtained.

According to the fifth aspect of the present invention, at the time of power transmission, the contact load input from the input / output disk to the inner race of the power roller due to the squeezing pressure is received by the outer race via the ball bearing. A pair of common roller bearings disposed between the outer ring and the power roller storage portion and inclined vertically at a position close to the power roller rotation axis, the pressing force acting in the front-rear direction of the power roller, The power transmission force acting in the vertical direction is supported together. Therefore, even if a load in the left-right direction is applied while the power transmission force in the vertical direction is acting on the power roller, the power roller moves in the left-right direction due to the low rolling resistance while the common roller bearing rolls, and the power roller moves smoothly in the left-right direction. Parallel movement of the power roller is secured,
The same effect as that of the first aspect can be obtained. in addition,
Similarly to the invention according to the third aspect, it is not necessary to manage the clearance of the second roller bearing that supports the power transmission force in the vertical direction, and the number of parts is reduced. Furthermore, the thickness of the ball bearing disposed between the inner ring and the outer ring of the power roller can be secured on the back surface of the groove on the outer ring side, thereby improving the durability of the ball bearing of the power roller. Is obtained.

According to the sixth aspect of the invention, the same effects as those of the third to fifth aspects can be obtained by employing a pair of common roller bearings. In addition, the contact line connecting the contact point of the ball bearing with the inner ring raceway and the contact point of the outer ring raceway has a tilt setting shifted from the front-rear direction so that the ball bearing bears the radial load acting on the inner ring of the power roller. By doing so, the power roller inner ring is a solid inner ring having no shaft portion through-hole. For this reason, the strength durability of the inner ring is greatly improved, and the deformation of the inner ring is suppressed by making the power roller inner ring a solid inner ring, so that the power roller is disposed between the solid inner ring and the outer ring. The durability of the ball bearing is improved.

According to the seventh aspect of the present invention, since there is no need to secure a flat portion for providing a washer and a snap ring, the thickness of the solid inner ring in the front-rear direction is increased, and the solid inner ring is attached to the input / output disk. It has a dome shape in which the area of the contacting spherical portion is enlarged. Therefore, the strength and durability of the inner ring alone are improved, and the deformation of the power roller due to the narrow pressure with the input / output disk is suppressed to be small. Therefore, the ball bearing disposed between the solid inner ring and the outer ring of the power roller. Can be improved in durability.

According to the present invention, when lubricating the ball bearing, the lubricating oil supplied from the power roller supporting member through the first lubricating oil supply pipe and the outer ring shaft oil passage is supplied to the solid inner ring and the outer ring. It is guided to a ball bearing via a lubricating oil reservoir provided between them. Therefore, since the lubricating oil is effectively guided to the ball bearing while securing a sufficient oil amount, the durability of the ball bearing disposed between the solid inner ring and the outer ring of the power roller can be improved. .

According to the ninth aspect of the present invention, the space between the oil reservoir concave portion formed on the solid inner ring and the oil reservoir convex portion formed on the outer ring is a lubricating oil reservoir. Accordingly, since the deformation of the power roller is suppressed to be small by improving the rigidity of the power roller outer ring, the durability of the ball bearing disposed between the solid inner ring and the outer ring of the power roller can be improved.

According to the tenth aspect of the present invention, even when the supply pressure (supply flow rate) of the lubricating oil is not sufficient, the inclination direction of the outer ring inclined oil passage is directed to the lower side of the unit to supply the lubricating oil using gravity. Is possible. Therefore, even when the supply pressure of the lubricating oil is insufficient or the viscosity of the lubricating oil is high depending on the temperature, the lubricating oil can be reliably supplied to the ball bearing.

According to the eleventh aspect of the present invention, the lubricating oil from the power roller supporting member is supplied to the ball bearing in a region where the load of the ball bearing is large (up and down receiving power transmission force) via the lubricating oil guide structure provided in the lubricating oil reservoir. Direction and left / right direction receiving the pressing force)
The lubricating oil is guided to. Therefore, the durability of the ball bearing disposed between the solid inner ring and the outer ring of the power roller can be further improved by distributing the lubricating oil according to the required oil amount.

According to the twelfth aspect of the invention, when lubricating the ball bearing, the power roller support member approaches the opening end of the second lubricating oil supply pipe via the first lubricating oil supply pipe and the second lubricating oil supply pipe. Lubricating oil is supplied toward the oil reservoir recess of the solid inner race, and the lubricating oil is reliably supplied to the solid inner race of the power roller along the inner surface of the oil reservoir recess. Therefore, with the rotation of the solid inner ring, lubricating oil can be reliably supplied to the entire ball bearing disposed between the solid inner ring and the outer ring of the power roller.

[0033]

(Embodiment 1) Embodiment 1 is a toroidal-type continuously variable transmission corresponding to the first aspect of the present invention.

[Overall Configuration] FIG. 2 shows the first embodiment.
1 is an overall configuration diagram showing a toroidal-type continuously variable transmission. Reference numeral 10 denotes a toroidal-type continuously variable transmission, and a rotational driving force from an engine (not shown) is input via a torque converter 12. The torque converter 12 includes a pump impeller 12a,
The turbine shaft includes a turbine runner 12b, a stator 12c, a lock-up clutch 12d, an apply-side oil chamber 12e, a release-side oil chamber 12f, and the like.

The input shaft 14 is connected to a forward / reverse switching mechanism 36, which is connected to the planetary gear mechanism 4
2, a forward clutch 44 and a reverse brake 46 are provided. The planetary gear mechanism 42 has 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 first continuously variable transmission mechanism 18 and the second continuously variable transmission mechanism 20 are connected to the torque transmission shaft 16 in the transmission case 22. Is arranged in tandem on the downstream side (dual cavity type). A control valve system body is disposed on a base indicated by reference numeral 64.

The first continuously variable transmission mechanism 18 includes a pair of input disk 18a and output disk 18b whose opposing surfaces are formed as toroidal curved surfaces, and these input / output disks 18a,
A pair of power rollers 18 c, which are arranged between the opposing surfaces of the power rollers 18 b and symmetrically with respect to the torque transmission shaft 16,
18d, a support member for tiltably supporting the power rollers 18c and 18d, and a servo piston (FIG. 3) as a hydraulic actuator. Similarly, the second continuously variable transmission mechanism 20 includes a pair of input disk 20a and output disk 20b whose opposing surfaces are formed as toroidal curved surfaces,
It includes a pair of power rollers 20c and 20d, a supporting member thereof, and a servo piston (FIG. 3).

The two continuously variable transmission mechanisms 18 and 20 are arranged on the torque transmission shaft 16 in opposite directions so that the output disks 18b and 20b face each other.
The input disks 18a, 20a of No. 8 are pressed toward the right in the axial direction in the figure by a loading cam device 34 that generates a pressing force according to the input torque passing 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 18a of the first continuously variable transmission mechanism 18 and the input disk 20a of the second continuously variable transmission mechanism 20 are urged by a disc spring 40 toward the left in the axial direction in the figure.

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

In the above mechanism, each power roller 20
c and 20d are tilted by an operation described later so that a tilt angle corresponding to the gear ratio is obtained.
The input rotations of the motors a and 20a are changed in a stepless (continuous) manner 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 rotatably fitted on the torque transmission shaft 16, and the transmission torque is transmitted to the output shaft (counter shaft) 30 via the output gear 28. Combined gear 3
0a, and these gears 28, 30a constitute a torque transmission mechanism 32. Further, a transmission mechanism 48 including a gear 52 provided on the output shaft 30 and an idler gear 54 meshing with the gear 52 is provided, and the output shaft 50 is connected to a propeller shaft 60.

FIG. 3 is a schematic diagram showing a shift control system for tilting each of the power rollers 18c, 18d, 20c, and 20d so as to obtain a tilt angle corresponding to the speed ratio. This will be described below.

First, each of the power rollers 18c, 18d, 2
0c and 20d are trunnions 17a, 17b, 27a,
27b, it is rotatable around the power roller rotation axes 15a, 15b, 25a, 25b, and is supported so as to be able to move in parallel in the left and right direction, which is the disk rotation axis direction. That is, the power roller support structure without the pivot shaft is employed. This trunnion 1
Servo pistons 70 are provided at the other ends of the servo pistons 7a, 17b, 27a, 27b as hydraulic actuators for moving the trunnions 17a, 17b, 27a, 27b in the axial direction to tilt the respective power rollers 18c, 18d, 20c, 20d.
a, 70b, 72a, and 72b are provided.

The servo pistons 70a, 70b, 72
As a hydraulic control system for controlling the operation of a and 72b, a high-side oil path 74 connected to the high-side oil chamber, a low-side oil path 76 connected to the low-side oil chamber, and a high-side oil path 74 are connected. A shift control valve 78 having a port 78b connecting the port 78a and the low-side oil passage 76 is provided. An oil pump 80 is connected to a line pressure port 78c of the shift control valve 78.
And a line pressure from a hydraulic source having a relief valve 82. Transmission spool 78d of the transmission control valve 78
Detects the axial direction and tilt direction of the trunnion 17a,
The lever 84 and the precess cam 86 that feed back to the shift control valve 78 are interlocked. The speed change sleeve 78e of the speed change 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 controlling the drive of the step motor 88. The CVT controller 110 includes a throttle opening sensor 112, an engine rotation sensor 114, an input shaft rotation sensor 116, 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 as a representative from the power rollers 18c, 18d, 20c and 20d,
The configuration will be described with reference to FIG. The same structure is adopted for the other power rollers 18d, 20c and 20d.

The trunnion 17a is provided with a power roller housing 91 at one end thereof,
1, the input / output disks 18a,
The power roller 18c supports the power roller 18c so as to be able to move in parallel along the left-right direction which is the rotation axis direction of the power roller 18b, and is capable of tilting around a swing axis 19a orthogonal to the power roller rotation axis 15a. A lubricating oil supply oil passage 98 is provided in the trunnion 17a, and an open end thereof is arranged so as to communicate with an axial oil passage 99 formed in an outer ring 94 of the power roller 18c. A bearing support plate 95 is fixed to a flat portion of the power roller housing 91. Further, the movement range of the power roller 18c in the left-right direction is defined by the contact between the power roller storage portion 91 and the outer ring 94 at both left and right ends.

The power roller 18c has an inner ring 93 that comes into frictional contact with the input / output disks 18a and 18b,
3 and a ball bearing 92 interposed between the inner ring 93 and the outer ring 94. The inner ring 93 is moved from the input / output disks 18a and 18b with the pressing force. Is received by the outer ring 94 via the ball bearing 92.

The outer ring 94 and the power roller housing 9
1 and a pair of upper and lower first roller bearings 96a, 96a supporting a pressing force 100 acting in the front-rear direction, and a power transmission force 10 acting in the vertical direction, which is the oscillating axis 19a.
1 and a pair of upper and lower second roller bearings 96b, (96b)
Are arranged along the left and right directions of the power roller 18c. Incidentally, 97 is a second roller bearing 96b, 96b.
This is an adjustment shim for managing the gap between the two.

Next, the function and effect will be described.

[Gear ratio control action] Toroidal type CVT
Changes the gear ratio by tilting the power rollers 18c, 18d, 20c, 20d. That is, when the step motor 88 is rotated, the speed change sleeve 78 is rotated.
When e is displaced, the servo pistons 70a, 70b, 72
Hydraulic oil is guided to one of the servo piston chambers a and 72b, and the hydraulic oil is discharged from the other servo piston chamber. The rotation centers of the power rollers 18c, 18d, 20c and 20d are arranged on the disks 18a, 18b, 20a and 20b. Offset to the center of rotation. Due to this offset, a tilting force is generated in the power rollers 18c, 18d, 20c, 20d, and the tilt angle changes. The tilting motion and the offset are transmitted to the speed change spool 78d via the precess cam 86 and the lever 84, and stop at a position where the speed change sleeve 78e is displaced by the step motor 88. The step motor 88 is connected to the CVT controller 9.
The shift sleeve 78e is displaced by a drive command to obtain a target gear ratio from 0.

[Load Support Function and Sliding Function of Power Roller] During power transmission, the input / output disks 18a,
The contact load input to the inner ring 93 of the power roller 18c from 18b is received by the outer ring 94 via the ball bearing 92. Then, the outer ring 94 and the power roller storage portion 91
Pressing force 1 acting in the front-rear direction of the power roller 18c by the first roller bearings 96a, 96a disposed between
00 is supported. Further, a pair of upper and lower second roller bearings 9 disposed between the outer ring 94 and the power roller storage portion 91.
The power transmission force 101 acting in the vertical direction of the power roller 18c is supported by 6b and 96b.

Therefore, even if the power transmission force 101 in the vertical direction acts on the power roller 18c, the second roller bearings 96b, 9
6b supports this load, and even if a vertical load acts on the power roller 18c simultaneously with the vertical load,
The power roller 18c moves in the left-right direction due to low rolling resistance while the second roller bearings 96b, 96b roll. That is, even if the power transmission force 101 in the vertical direction acts on the power roller 18c, a smooth parallel movement of the power roller 18c in the horizontal direction is secured.

[Effect] As described above, the power roller 18
Even if a vertical load is applied to c, smooth translation movement of the power roller 18c in the left and right direction is ensured, so that the input / output disks 18a and 18b are deformed and misalignment that can occur during assembly occurs. In this case, the horizontal translation of the power roller 18c for absorbing these positional deviations can be smoothly performed.
8c, the pressing force applied from the input disk 18a side and the pressing force applied from the output disk 18b side can be kept uniform. Therefore, the pressing force from the input disk 18a and the pressing force from the output disk 18b become unbalanced, and it is possible to suppress the occurrence of slippage or the like at the contact portion between the input / output disks 18a, 18b and the power roller 18c. .

The power roller 1 is attached to the trunnion 17a.
Since there is no need to provide a structure for holding the pivot shaft for supporting the 8n, the increase in the stress of the trunnion 17a can be prevented, the rigidity can be improved, and the deformation can be suppressed. Therefore, the contact position between the input / output disks 18a, 18b and the power roller 18c does not largely deviate from the design value, and it is possible to reduce the increase in the surface pressure due to the unbalanced load and the change in the gear ratio due to the deformation.

(Embodiment 2) Embodiment 2 is the second embodiment.
Is a toroidal-type continuously variable transmission corresponding to the invention described in (1).

First, the structure will be described. In the second embodiment, as shown in FIG. 4, the outer ring 94 is formed in a polygonal shape having flat portions 94a, 94a extending in the left-right direction at the upper and lower portions of the outer peripheral surface. The flat portion 9 is provided in the roller storage portion 91.
By forming a shape having flat portions 91a, 91a extending in the left-right direction at a portion opposed to 4a, 94a, two sets of opposed flat portions 91a, 94a are formed, and the two sets of opposed flat portions 91a, 94a are formed. This is an example in which second roller bearings 96b, 96b are arranged together with adjustment shims 97 therebetween. The other configuration is the same as that of the first embodiment, and the description is omitted.

In the second embodiment, in addition to the functions and effects of the first embodiment, the second roller bearings 96b, 96b are extended by the length of the opposing flat portions 91a, 94a in the left-right direction.
Of the second roller bearing 96 can be increased.
By increasing the number of b and 96b, the capacity for power transmission force (vertical load) increases.

(Embodiment 3) Embodiment 3 is the third embodiment.
Is a toroidal-type continuously variable transmission corresponding to the invention described in (1).

First, the structure will be described. In the third embodiment, as shown in FIG. 5, a vertical position is provided between the outer ring 94 and the power roller storage portion 91 and away from the power roller rotating shaft 15a. A pair of common roller bearings 96c, 96c supporting both the pressing force 100 acting in the front-rear direction and the power transmission force 101 acting in the up-down direction,
This is an example in which the components are inclined and arranged along the left-right direction of FIG. The other configuration is the same as that of the first embodiment, and the description is omitted.

In the third embodiment, when power is transmitted, the contact load input from the input / output disks 18a and 18b to the inner ring 93 of the power roller 18c due to the squeezing force is applied to the outer ring 94 via the ball bearing 92. Received by A pair of common roller bearings 96c, 96c, which are arranged between the outer ring 94 and the power roller storage portion 91 and are vertically inclined away from the power roller rotation shaft 15a, act in the front-rear direction of the power roller 18c. Pressing force 1
00 and a power transmission force 101 acting in the vertical direction of the power roller 18c.

Therefore, even if a load in the left-right direction is applied while the power transmission force 101 in the up-down direction is acting on the power roller 18c, the power roller 18c is driven by the low rolling resistance due to the low rolling resistance while rolling. 18c moves in the left-right direction, and a smooth parallel movement of the power roller 18c is ensured, and the same effect as the invention of the first embodiment can be obtained.

In addition, as in the first embodiment, the adjustment shim 97 for controlling the clearance between the second roller bearings 96b, 96b for supporting the power transmission force in the vertical direction is not required, and the number of parts including the bearing parts is reduced. Be reduced. Furthermore, since the point of application of the load acting on the trunnion 17a is not the flat portion of the power roller housing portion 91 but both ends, the deformation of the trunnion 17a can be reduced.

(Embodiment 4) Embodiment 4 is the fourth embodiment.
Is a toroidal-type continuously variable transmission corresponding to the invention described in (1).

First, the structure will be described. In the fourth embodiment, as shown in FIG. 6, an outer ring 94 is formed by a polygon having an inclined plane portion 94b extending in the left-right direction at a vertical position distant from the power roller rotation shaft 15a. By forming the power roller storage portion 91 in a polygonal shape having an inclined flat portion 91b extending in the left-right direction at a portion facing the inclined flat portion 94b, two sets of opposed inclined flat portions 91b and 94b are formed. The two sets of opposed inclined plane portions 91b and 94b
This is an example in which common roller bearings 96c, 96c are arranged therebetween.
The other configuration is the same as that of the third embodiment, and the description is omitted.

In the fourth embodiment, in addition to the functions and effects of the third embodiment, the opposing inclined plane portions 91b, 94
b, the common roller bearings 96c, 9
6c can be increased, and by increasing the number of common roller bearings 96c, 96c, the supporting capacity for the pressing force and the power transmission force is increased.

(Embodiment 5) Embodiment 5 is a toroidal-type continuously variable transmission corresponding to the third and fourth aspects of the present invention.

First, the structure will be described.
In FIG. 4, as shown in FIG. 7, the first roller bearings 96a, 96a found in the first and second embodiments are eliminated, and it is not necessary to supply lubricating oil to this portion. Therefore, in the fifth embodiment, the lubricating oil is supplied directly from the lubricating oil supply oil passage 98 provided in the trunnion 17a to the bearing of the power roller 18c via the lubricating oil supply pipe 102. is there.

Thus, in addition to the effects of the third and fourth embodiments, it is possible to effectively supply a limited amount of lubricating oil to the power roller 18c without leaking, thereby suppressing damage due to oil film breakage, and The durability of the roller 18c is greatly improved.

(Embodiment 6) Embodiment 6 is the fifth embodiment.
Is a toroidal-type continuously variable transmission corresponding to the invention described in (1).

First, the structure will be described. In the sixth embodiment, as shown in FIG. 8, the vertical position between the outer ring 94 and the power roller storage portion 91 and close to the power roller rotating shaft 15a is This is an example in which a pair of common roller bearings 96d, 96d that support both a pressing force 100 acting in the front-rear direction and a power transmission force 101 acting in the up-down direction are arranged obliquely along the left-right direction of the power roller 18c. The other configuration is the same as that of the first embodiment, and the description is omitted.

In the sixth embodiment, at the time of power transmission, the contact load input from the input / output disks 18a and 18b to the inner ring 93 of the power roller 18c due to the squeezing force is applied to the outer ring 94 via the ball bearing 92. Received by A pair of common roller bearings 96d, 96d, which are arranged between the outer ring 94 and the power roller storage portion 91 and vertically inclined near the power roller rotating shaft 15a, act in the front-rear direction of the power roller 18c. Pressing force 100
And the power transmission force 101 acting in the vertical direction of the power roller 18c.

Further, the inclined common roller bearings 96d,
96d is symmetrically arranged at a vertical position close to the power roller rotating shaft 15a, so that the groove rear surface 94a of the ball bearing 92 disposed between the inner ring 93 and the outer ring 94 of the power roller 18c is located on the outer ring 94 side. Can be made thicker, and the durability of the ball bearing 92 is improved.

(Embodiment 7) The embodiment 7 is a fifth embodiment.
Is a toroidal-type continuously variable transmission corresponding to the invention described in (1).

First, the structure will be described. In the fifth embodiment, as shown in FIG. 9, the first roller bearings 96a and 96a found in the first and second embodiments are eliminated, and the lubricating oil is supplied to the portion. You don't have to. Therefore, Embodiment 7
Then, the lubricating oil supply oil passage 9 provided in the trunnion 17a
8 through the lubricating oil supply pipe 102 to the power roller 1
This is an example in which lubricating oil is supplied directly to the bearing portion 8c.

As a result, in addition to the effects of the fifth embodiment,
A limited amount of lubricating oil can be effectively supplied to the power roller 18c without leaking, the damage due to the oil film shortage is suppressed, and the durability of the power roller 18c is greatly improved.

(Eighth Embodiment) An eighth embodiment is a sixth embodiment.
Is a toroidal-type continuously variable transmission corresponding to the invention described in (1).

First, the structure will be described. As shown in FIG. 10, an upper and lower part which is located between a non-axial outer ring 94 'described later and the power roller storage part 91 of the trunnion 17a and is separated from the power roller rotating shaft 15a. Position, a pressing force 100 acting in the front-rear direction and a power transmitting force 101 acting in the vertical direction.
A pair of common roller bearings 96c, 96c supporting both
The power rollers 18c are arranged obliquely along the left-right direction (similar to the third embodiment in FIG. 5).

A contact line C connecting the contact point of the ball bearing 92 'with the inner raceway and the contact point of the outer raceway forms a radial load (radial load) acting on the inner race of the power roller by the ball bearing 92'. The power roller outer ring is a non-axial outer ring 94 'in which a shaft portion for supporting a radial load acting on the inner ring is eliminated, and the power roller inner ring Is a solid inner ring 93 'having no shaft through-hole. Here, as a specific configuration for shifting the contact line C, as described in Japanese Patent Application Laid-Open No. HEI 9-125288, the grooves of the inner raceway and the outer raceway are shifted so that the contact points of the ball bearing 92 'with respect to both raceways are shifted. This is done by determining the shape. Further, the inclination direction of the contact line C is not limited to the setting shifted outward from the front-rear direction, but may be set inward, such as the setting shifted radially from the front-rear direction as long as the ball bearing 92 ′ bears the radial load. The shift direction is not limited.

In FIG. 10, reference numeral 98 denotes a lubricating oil supply passage, 102 denotes a lubricating oil supply pipe, and 103 denotes an outer ring shaft oil passage.

Next, the function and effect will be described. Non-axial outer ring 9
Between the power roller housing 4 'and the power roller storage portion 91, and at a vertical position away from the power roller rotating shaft 15a, a pair of support members for supporting both the pressing force 100 acting in the front-rear direction and the power transmitting force 101 acting in the vertical direction. Common roller bearings 96c, 96
c is inclined along the left-right direction of the power roller 18c, so that a pair of inclined common roller bearings 96c,
96c supports both the pressing force 100 acting in the front-rear direction of the power roller 18c and the power transmission force 101 acting in the vertical direction of the power roller 18c, and the vertical power transmission force 101 acts on the power roller 18c. Even if a load in the left-right direction acts when the
The power roller 18c moves in the left-right direction due to the low rolling resistance while the 6c and 96c are rolling, and a smooth parallel movement of the power roller 18c is ensured.

Further, a pair of common roller bearings 96c, 96c
As in the third embodiment, the adjustment shim 97 for managing the clearance between the second roller bearings 96b, 96b that supports the power transmission force in the vertical direction is not required as in the third embodiment. The number of parts including parts is reduced. Furthermore, since the point of application of the load acting on the trunnion 17a is not the flat portion of the power roller housing portion 91 but both ends, the deformation of the trunnion 17a can be reduced.

In addition, the contact line C is set to be inclined so that the ball bearing 92 'bears the radial load acting on the inner race of the power roller.
4 'and the power roller inner ring is a solid inner ring 93'
It is said. For this reason, in power roller outer ring processing,
Difficult machining for simultaneously machining the raceway surface of the ball bearing 92 'and the shaft portion through hole can be eliminated. Further, since the power roller inner ring is a solid inner ring 93 ', the strength and durability of the inner ring are greatly improved, and the power roller inner ring is formed as a solid inner ring 9'.
Since the deformation of the inner ring is suppressed by setting it to 3 ′, the durability of the ball bearing 92 ′ disposed between the solid inner ring 93 ′ and the non-axial outer ring 94 ′ of the power roller 18c is improved. Also,
Because the outer race of the power roller is a non-axial outer race 94 ', FIGS.
A roller bearing disposed between a shaft portion of the outer ring 94 and a shaft portion through hole of the inner ring 93 as in the embodiment shown in FIG.
The washer and snap ring provided on the distal end side of the shaft portion of the outer ring 94 are eliminated, and the cost of the power roller 18c can be reduced by reducing the number of parts and the number of processing steps.

(Embodiment 9) The ninth embodiment is the seventh embodiment.
Is a toroidal-type continuously variable transmission corresponding to the invention described in (1).

First, the structure will be described. In the ninth embodiment, as shown in FIG. 11, a solid structure according to the eighth embodiment is obtained by eliminating the shaft through hole of the inner ring 93 in the first to seventh embodiments. Since there is no need to secure a flat portion for providing a washer and a snap ring instead of the inner ring 93 ', the thickness in the front-rear direction is increased, and the input / output disks 18a, 1
This is an example of a dome-shaped solid inner ring 93 ″ having an enlarged area of the spherical portion in contact with 8 b. The other configuration is the same as that of the eighth embodiment, and a description thereof will be omitted.

Thus, in addition to the effects of the eighth embodiment,
The strength and durability of the inner ring alone are improved, and the power roller 1 is formed by a narrow pressure with the input / output disks 18a and 18b.
8c is kept small, the power roller 18
The durability of the ball bearing 92 ′ disposed between the solid inner ring 93 ″ c and the non-axial outer ring 94 ′ can be improved.

(Embodiment 10) Embodiment 10 is a toroidal-type continuously variable transmission corresponding to the eighth aspect of the present invention.

First, the structure will be described. In the tenth embodiment, as shown in FIG. 12, a lubricating oil is provided between an oil reservoir recess formed in a solid inner ring 93 "and a plane portion of a non-axial outer ring 94 '. A lubrication structure is provided in which a reservoir 104 is provided to guide lubricating oil supplied from the trunnion 17a through the lubricating oil supply pipe 102 and the outer ring shaft oil passage 103 to the ball bearing 92 'via the lubricating oil reservoir 104. The other configuration is the same as that of the ninth embodiment, and the description is omitted.

Thus, in addition to the effects of the ninth embodiment,
Since the lubricating oil is effectively guided to the ball bearing 92 'while ensuring a sufficient oil amount by the lubricating oil reservoir 104, the lubricating oil is disposed between the solid inner ring 93 "and the non-axial outer ring 94' of the power roller 18c. The durability of the ball bearing 92 ′ can be improved.

Embodiment 11 Embodiment 11 is a toroidal-type continuously variable transmission according to the ninth aspect of the present invention.

First, the structure will be described. In the eleventh embodiment, as shown in FIG. 13, an oil sump concave portion formed on a solid inner ring 93 "and an oil sump convex portion formed on a non-axial outer ring 94 'are formed. The space between them is a lubricating oil reservoir 104 '. Except for the fact that the outer ring shaft center oil passage 103 is lengthened by the oil reservoir convex portion, the other configuration is the same as that of the ninth embodiment and will be described. Is omitted.

As a result, in addition to the effects of the ninth embodiment,
Since the rigidity of the non-axial outer ring 94 'of the power roller 18c is improved, the deformation of the power roller 18c is suppressed to be small. Therefore, the power roller 18c is disposed between the solid inner ring 93 "and the non-axial outer ring 94'. The durability of the ball bearing 92 'can be improved.

(Twelfth Embodiment) A twelfth embodiment is a toroidal type continuously variable transmission according to the tenth aspect of the present invention.

First, the configuration will be described. In the twelfth embodiment, as shown in FIG. 14, the outer ring shaft center oil passage is an outer ring inclined oil passage 103 'having an inclination angle with respect to the front-rear direction. Things. Note that the other configuration is the same as that of the eleventh embodiment, and the description is omitted.

Therefore, the supply pressure (supply flow rate) of the lubricating oil
Even if is not enough, the inclination direction of the outer ring inclined oil passage 103 'is directed to the lower side of the unit, so that lubricating oil can be supplied using gravity.

Thus, in addition to the effects of the eleventh embodiment, even when the supply pressure of the lubricating oil is insufficient or the viscosity of the lubricating oil is high due to the temperature, the lubricating oil can be reliably supplied to the ball bearing 92 '. Can be.

(Thirteenth Embodiment) A thirteenth embodiment is a toroidal-type continuously variable transmission according to the eleventh aspect of the present invention.

First, the structure will be described. In the thirteenth embodiment, as shown in FIGS.
A lubricating oil guide groove 105 (lubricating oil guiding structure) for guiding lubricating oil to the vertical region and the lateral direction region where the load of the ball bearing 92 'is large on the oil reservoir convex portion formed on the non-axial outer ring 94' constituting the shaft 04 '. Is provided. Note that the other configuration is the same as that of the eleventh embodiment, and the description is omitted.

Therefore, the lubricating oil from the lubricating oil supply passage 98 of the trunnion 17a passes through the lubricating oil supply pipe 102 and the outer ring shaft oil passage 103, and flows through the lubricating oil guide groove 105 provided in the lubricating oil reservoir 104 '. Thus, the lubricating oil is guided to a region where the load of the ball bearing 92 'is large, that is, a vertical region where the power transmission force is received and a horizontal region where the pressing force is received.

As a result, in addition to the effect of the eleventh embodiment, the lubricating oil is distributed by the lubricating oil guide groove 105, so that the power roller 18c is disposed between the solid inner ring 93 ″ and the non-axial outer ring 94 ′. The durability of the ball bearing 92 'can be further improved.

(Embodiment 14) Embodiment 14 is a toroidal type continuously variable transmission according to the twelfth aspect of the present invention.

First, the structure will be described. In the fourteenth embodiment, as shown in FIG. 17, outer ring shaft oil for guiding lubricating oil to a lubricating oil reservoir 104 having an oil reservoir recess formed in a solid inner ring 93 ″. A lubricating oil supply pipe 106 (second lubricating oil supply pipe) whose opening end is close to the oil reservoir recess is provided in the passage 103. Other configurations are the same as those of the tenth embodiment shown in FIG. Description is omitted.

Therefore, when lubricating the ball bearing 92 ′, the lubricating oil supplied from the lubricating oil supply passage 98 of the trunnion is supplied to the lubricating oil supply pipe 102 (first lubricating oil supply pipe), the outer ring shaft oil path 103, and the lubricating oil. Lubricating oil supply pipe 1 via oil supply pipe 106
The lubricating oil is supplied to the solid inner ring 93 "of the solid inner ring 93" adjacent to the opening end of the oil roller 06, and the lubricating oil is reliably supplied to the solid inner ring 93 "of the power roller 18c along the inner surface of the oil sump concave.

As a result, in addition to the effects of the tenth embodiment, the lubricating oil is disposed between the solid inner ring 93 "and the non-axial outer ring 94 'with the rotation of the solid inner ring 93". Can be reliably supplied to the entirety of the ball bearing 92 '.

[Brief description of the drawings]

FIG. 1 is a sectional view showing a power roller support structure in a toroidal type continuously variable transmission according to a first embodiment.

FIG. 2 is an overall system diagram showing a toroidal-type continuously variable transmission according to the first embodiment.

FIG. 3 is a transmission control system diagram illustrating the toroidal-type continuously variable transmission according to the first embodiment;

FIG. 4 is a sectional view showing a power roller support structure in a toroidal type continuously variable transmission according to a second embodiment;

FIG. 5 is a sectional view showing a power roller support structure in a toroidal type continuously variable transmission according to a third embodiment.

FIG. 6 is a sectional view showing a power roller support structure in a toroidal type continuously variable transmission according to a fourth embodiment.

FIG. 7 is a sectional view showing a power roller support structure in a toroidal type continuously variable transmission according to a fifth embodiment.

FIG. 8 is a sectional view showing a power roller support structure in a toroidal type continuously variable transmission according to a sixth embodiment.

FIG. 9 is a sectional view showing a power roller supporting structure in a toroidal type continuously variable transmission according to a seventh embodiment.

FIG. 10 is a sectional view showing a power roller support structure in a toroidal type continuously variable transmission according to an eighth embodiment.

FIG. 11 is a sectional view showing a power roller support structure in a toroidal type continuously variable transmission according to a ninth embodiment.

FIG. 12 is a sectional view showing a power roller support structure in a toroidal type continuously variable transmission according to a tenth embodiment.

FIG. 13 is a sectional view showing a power roller support structure in a toroidal type continuously variable transmission according to an eleventh embodiment.

FIG. 14 is a sectional view showing a power roller support structure in a toroidal type continuously variable transmission according to a twelfth embodiment.

FIG. 15 is a sectional view showing a power roller supporting structure in a toroidal type continuously variable transmission according to a thirteenth embodiment.

FIG. 16 is a diagram showing a power roller outer ring in the toroidal type continuously variable transmission according to the thirteenth embodiment.

FIG. 17 is a sectional view showing a power roller supporting structure in a toroidal type continuously variable transmission according to a fourteenth embodiment.

FIG. 18 is a sectional view showing a power roller support structure in a conventional toroidal type continuously variable transmission.

[Explanation of symbols]

 15a Power roller rotating shaft 17a Trunnion 18a Input disk 18b Output disk 18c, 18d Power roller 19a Tilting shaft 91 Power roller housing 92, 92 'Ball bearing 93 Inner ring 93', 93 "Solid inner ring 94 Outer ring 94 'Non-axial outer ring 96a first roller bearing 96b second roller bearing 100 pressing force 101 power transmission force 96c common roller bearing 96d common roller bearing

 ────────────────────────────────────────────────── ─── Continued on the front page (72) Inventor Haruyoshi Hisamura Nissan Motor Co., Ltd., 2 Takaracho, Kanagawa-ku, Yokohama, Kanagawa Prefecture (72) Inventor Shunichi Oshitari 2 Takaracho, Kanagawa-ku, Yokohama, Kanagawa Prefecture 72) Inventor Jun Watanabe Nissan Motor Co., Ltd. F-term (reference) 3J051 AA03 BA03 BD02 BE09 CA05 CB07 ED08 ED20 FA02 2 Takara-cho, Kanagawa-ku, Yokohama-shi, Kanagawa

Claims (12)

[Claims] An input disk and an output disk coaxially disposed opposite to each other, a power roller pressed between the input and output disks so as to transmit power, and the power roller is rotatable with respect to a power roller housing. And a power roller supporting member that is tiltable about a swing axis orthogonal to the power roller rotation axis while supporting the input and output disk so as to be able to move in parallel along the rotation axis direction (hereinafter, the left and right direction). The power roller, comprising an inner ring frictionally contacting the input / output disk, an outer ring rotatably supporting the inner ring, and a ball bearing interposed between the inner ring and the outer ring, In a toroidal-type continuously variable transmission that receives a contact load input from the input / output disk to the inner ring due to the pinching pressure by an outer ring via a ball bearing, the outer ring and the power roller storage portion A first roller bearing for supporting a pressing force acting in the direction of the axis of rotation of the power roller (hereinafter referred to as the front-rear direction), and power transmission acting in the direction of the oscillating axis orthogonal to the axis of rotation of the power roller (hereinafter referred to as the vertical direction). A toroidal-type continuously variable transmission, wherein a pair of second roller bearings for supporting a force are arranged along a left-right direction of a power roller. 2. The toroidal-type continuously variable transmission according to claim 1, wherein the shape of the outer ring is a shape having a flat portion extending in the left-right direction at upper and lower portions of an outer peripheral surface, and a shape of the power roller storage portion. The power roller storage portion has a flat portion extending in the left-right direction at a portion facing the flat portion, and the second roller bearing is disposed between two sets of the opposite flat portions. Toroidal type continuously variable transmission. 3. 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 transmit power, and the power roller is rotatable with respect to a power roller storage portion. And a power roller supporting member capable of tilting around a swing axis perpendicular to the power roller rotation axis while supporting the power roller so as to be able to move in parallel in the left-right direction. An inner ring that comes into frictional contact, an outer ring that rotatably supports the inner ring, and a ball bearing interposed between the inner ring and the outer ring; In the toroidal-type continuously variable transmission that receives the contact load input to the outer ring via a ball bearing, between the outer ring and the power roller housing, the power roller rotating shaft Toroidal, characterized in that a pair of common roller bearings that support both a pressing force acting in the front-rear direction and a power transmission force acting in the vertical direction are arranged at an inclined position along the left-right direction of the power roller at separated vertical positions. Type continuously variable transmission. 4. The toroidal-type continuously variable transmission according to claim 3, wherein the shape of the outer race is a shape having an inclined plane portion extending in the left-right direction at a vertical position away from a power roller rotation shaft, and The shape of the roller accommodating portion has a shape in which a portion of the power roller accommodating portion facing the inclined flat portion has an inclined flat portion extending in the left-right direction, and the common roller bearing is provided between two sets of opposed inclined flat portions. A toroidal-type continuously variable transmission characterized by being arranged. 5. An input disk and an output disk coaxially opposed to each other, a power roller pressed between the input and output disks so as to transmit power, and the power roller is rotatable with respect to a power roller storage portion. And a power roller supporting member capable of tilting around a swing axis perpendicular to the power roller rotation axis while supporting the power roller so as to be able to move in parallel in the left-right direction. An inner ring that comes into frictional contact, an outer ring that rotatably supports the inner ring, and a ball bearing interposed between the inner ring and the outer ring; In the toroidal-type continuously variable transmission that receives the contact load input to the outer ring via a ball bearing, between the outer ring and the power roller housing, the power roller rotating shaft A pair of common roller bearings, which support both the pressing force acting in the front-rear direction and the power transmission force acting in the up-down direction, are arranged at the top and bottom of the power roller at an angle along the left-right direction of the power roller. Continuously variable transmission. 6. The toroidal-type continuously variable transmission according to claim 3, wherein a contact line connecting a contact point of the ball bearing with the inner raceway and a contact point of the outer raceway is formed on the inner race of the power roller. A toroidal type stepless, characterized in that the radial load acting on the roller is set to be inclined from the front-rear direction so as to be covered by the ball bearing, and the inner ring of the power roller is a solid inner ring having no shaft through hole. transmission. 7. The toroidal-type continuously variable transmission according to claim 6, wherein the solid inner ring has a dome shape in which the thickness in the front-rear direction is increased and the area of a spherical portion in contact with the input / output disk is enlarged. Features a toroidal type continuously variable transmission. 8. The toroidal-type continuously variable transmission according to claim 6, wherein a lubricating oil reservoir is provided between the solid inner ring and the outer ring, and a first lubricating oil supply pipe is provided from the power roller support member. And a lubricating structure for guiding lubricating oil supplied through an outer ring shaft oil passage to a ball bearing via a lubricating oil reservoir. 9. The toroidal-type continuously variable transmission according to claim 8, wherein a space between an oil sump concave portion formed on the solid inner ring and an oil sump convex portion formed on the outer ring is a lubricating oil sump. A continuously variable toroidal transmission. 10. The toroidal-type continuously variable transmission according to claim 8, wherein the outer ring shaft center oil passage is an outer ring inclined oil passage having an inclination angle with respect to the front-rear direction. Toroidal type continuously variable transmission. 11. The toroidal-type continuously variable transmission according to claim 8, wherein a lubricating oil guide structure is provided in the lubricating oil reservoir to guide lubricating oil to a region where a load of a ball bearing is large. Toroidal type continuously variable transmission. 12. The toroidal-type continuously variable transmission according to claim 8, wherein an outer ring shaft oil passage that guides lubricating oil to a lubricating oil reservoir having an oil reservoir recess formed in the solid inner ring has an opening end that is oily. A toroidal-type continuously variable transmission, wherein a second lubricating oil supply pipe is provided near the reservoir recess.