JP2001099253A - Toroidal type continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To high-efficiently feed lubrication oil to a contact part between the inner surfaces of pockets and the rolling surface of a ball and to prevent the occurrence of reduction of rotation resistance and wear of a holder. SOLUTION: Recess grooves 42 and 42 are formed in the inner peripheral surfaces of pockets 36 and 36 situated at a main body 39 constituting a holder 34a, and in two spot positions on the opposite side in a peripheral direction. A sufficient amount of lubrication oil is fed to a contact part between the inner peripheral surface and the running surface through the recess grooves 42 and 42.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The toroidal type continuously variable transmission according to the present invention is used, for example, as a transmission unit of an automatic transmission for an automobile or as a transmission for various industrial machines.

[0002]

2. Description of the Related Art It has been studied to use a toroidal type continuously variable transmission as schematically shown in FIGS. This toroidal-type continuously variable transmission supports an input side disk 2 concentrically with an input shaft 1 and an output side disk at an end of an output shaft 3 as disclosed in, for example, Japanese Utility Model Application Laid-Open No. 62-71465. 4 is fixed. The input shaft 1 is mounted on the inner surface of a casing containing the toroidal-type continuously variable transmission or on a support bracket provided in the casing.
In addition, trunnions 6, 6 that swing about pivots 5, 5, which are twisted with respect to the output shaft 3, are provided.

In other words, the pivots 5, 5 are located on the outer surfaces of both ends of the trunnions 6, 6 concentrically with each other and do not intersect with the central axes of the input shaft 1 and the output shaft 3. Are provided in a direction substantially perpendicular to this direction. or,
At the center of each of the trunnions 6, 6, the base ends of the displacement shafts 7, 7 are attached.
It is supported in a state of protruding from the inner side surface. Therefore, when the trunnions 6 swing about the pivots 5, the inclination angles of the displacement shafts 7 change. Power rollers 8 and 8 are rotatably supported around the respective displacement shafts 7 and 7. These power rollers 8 are sandwiched between the input side and output side disks 2, 4.

The inner surfaces 2a and 4a of the input and output disks 2 and 4 facing each other have a cross section of
An arc-shaped concave surface centered on the pivot 5 is formed. Each of the power rollers 8, 8 formed on a spherical convex surface
Peripheral surfaces 8a, 8a are in contact with the inner side surfaces 2a, 4a.

Further, a loading device 9 of a loading cam type is provided between the input shaft 1 and the input disk 2, and the input disk 2 is directed toward the output disk 4 by this pressing device 9. Is pressed. The pressing device 9 includes a cam plate 10 that rotates together with the input shaft 1 and a retainer 1.
A plurality of (for example, four) rollers 1 held by
2 and 12. A cam surface 13 which is an uneven surface extending in the circumferential direction is formed on one side surface (the left side surface in FIGS. 7 to 8) of the cam plate 10, and an outer surface (FIGS. 7 to 8) of the input side disk 2. A right cam surface 14 is also formed with a similar cam surface 14. The plurality of rollers 12, 12
Are supported rotatably about an axis in a radial direction with respect to the center of the input shaft 1.

When the cam plate 10 rotates with the rotation of the input shaft 1 during use of the toroidal type continuously variable transmission configured as described above, a plurality of rollers 12, 1
2 is pressed against the cam surface 14 on the outer surface of the input disk 2. As a result, the input side disk 2 is pressed by the plurality of power rollers 8, 8, and at the same time, based on the engagement between the pair of cam surfaces 13, 14 and the plurality of rollers 12, The input side disk 2 rotates. And
The rotation of the input disk 2 is transmitted to the output disk 4 via the plurality of power rollers 8, 8, and the output shaft 3 fixed to the output disk 4 rotates.

When the rotational speed of the input shaft 1 and the output shaft 3 is changed, and when the deceleration is first performed between the input shaft 1 and the output shaft 3, the trunnions are centered on the pivots 5, 5. 6, the peripheral surface 8a of each of the power rollers 8, 8 is shifted toward the center of the inner surface 2a of the input side disk 2 and the output side disk 8 as shown in FIG. Each of the displacement shafts 7 is tilted so as to abut on the inner surface 4a of the inner surface 4a of the inner surface 4a.

On the other hand, when increasing the speed, the trunnions 6, 6 are swung in opposite directions so that the peripheral surfaces 8a, 8a of the power rollers 8, 8, as shown in FIG. Each of the displacement shafts 7 is inclined so as to abut against a portion of the inner surface 2a of the side disk 2 near the outer periphery and a portion of the inner surface 4a of the output side disk 4 near the center, respectively. If the inclination angle of each of the displacement shafts 7, 7 is set between those in FIGS. 7 and 8, an intermediate speed ratio can be obtained between the input shaft 1 and the output shaft 3.

Further, FIG. 9 shows an automatic transmission for an automobile incorporating a toroidal type continuously variable transmission as a transmission unit, which is described in a microfilm of Japanese Utility Model Application No. 61-87523 (Japanese Utility Model Application Laid-Open No. 62-199557). Is shown. The rotation of the crankshaft of the engine is transmitted to the input shaft 16 via the clutch 15, and the cam plate 10 spline-engaged with the intermediate portion of the input shaft 16 is rotated. Then, by the operation of the pressing device 9 including the cam plate 10, the input side disk 2 is rotated while being pressed toward the output side disk 4 to the left in FIG. 9. The rotation of the input disk 2 is transmitted to the output disk 4 by the power rollers 8.

The output disk 4 is supported around the input shaft 16 by a needle bearing 17, and a cylindrical output shaft 18 formed integrally with the output disk 4
An angular ball bearing 20 is supported inside the housing 19. On the other hand, one end (the right end in FIG. 9) of the input shaft 16 is provided inside the housing 19 with a roller bearing 21.
The other end is rotatably supported inside the housing 19 by an angular type ball bearing 22 via a sleeve 23.

A transmission gear 26 integrally formed with a drive-side forward gear 24 and a drive-side reverse gear 25 is spline-engaged with the outer peripheral surface of the output shaft 18. When the vehicle is moving forward, the transmission gear 26 is moved to the right so that the driving-side forward gear 24
And a driven-side forward gear 2 provided at an intermediate portion of the take-out shaft 27.
8 and the transmission gear 26 is moved to the left at the time of retreat, and the drive-side retreat gear 25 and the driven-side retreat gear 29 fixed to an intermediate portion of the take-out shaft 27 are connected to an intermediate gear (not shown). Mesh through.

When the automatic transmission for a vehicle having the toroidal type continuously variable transmission as a transmission unit configured as described above is used, the input shaft 16 is rotated by the engine via the clutch 15 and the transmission gear 26 is rotated. Is moved in an appropriate direction, the take-out shaft 27 can be rotated in any direction. Further, by swinging the trunnions 6, 6 to change the contact position between the peripheral surfaces 8a, 8a of the power rollers 8, 8 and the inner surfaces 2a, 4a of the input and output disks 2, 4, The rotation speed ratio between the input shaft 16 and the take-out shaft 27 can be changed.

During the operation of the automatic transmission for an automobile as described above, the input disk 2 is pressed toward the output disk 4 based on the operation of the pressing device 9. As a result, a thrust load in the right direction in FIG. 9 is applied to the input shaft 16 supporting the cam plate 10 constituting the pressing device 9 as a reaction force based on the pressing. This thrust load is applied between the nut 30 screwed to the end of the input shaft 16 and the sleeve 2.
3 and is supported by the ball bearing 22. or,
By the operation of the pressing device 9, a thrust load in the left direction in FIG. 9 is applied to the output shaft 18 via the input-side and output-side disks 2, 4 and the power rollers 8, 8. This thrust load is supported by the ball bearing 20 via a stop ring 31 externally fitted to the output shaft 18.

For example, during operation of the toroidal-type continuously variable transmission used as the transmission unit of the automatic transmission for an automobile as described above, the space between the inner side surfaces 2a and 4a of the input side and output side disks 2 and 4 is set. A thrust load is applied to each of the power rollers 8 and 8 held between the power rollers. Therefore, thrust ball bearings 32 are provided between the power rollers 8 and the trunnions 6 so as to support a thrust load applied to the power rollers 8. I have.

Each of these thrust ball bearings 32, 32 has a plurality of balls 33, 33, respectively,
3 is composed of a retainer 34 for holding the roller 3 so as to freely roll, and an outer ring 35. The plurality of balls 33, 33 are provided with a raceway surface formed on the outer end surface of each of the power rollers 8, 8,
It comes into rolling contact with the raceway surface formed on the inner surface of the outer ring 35. The retainer 34 is made of a metal or a synthetic resin in an annular shape, and the balls 33, 36 are formed in pockets 36, 36 formed at circumferentially equal positions in a diametrically intermediate portion.
33 are held one by one so as to freely roll. Further, the outer ring 35 formed in a ring shape is abutted against the inner surface of each of the trunnions 6, 6 via a thrust bearing 37 (see FIG. 10) such as a slide bearing or a needle bearing.

During operation of the toroidal type continuously variable transmission, the above-described thrust ball bearings 32, 32 rotate at high speed while supporting the thrust load applied to each of the power rollers 8, 8. Therefore, during operation of the toroidal type continuously variable transmission,
A sufficient amount of lubricating oil must be supplied to the thrust ball bearings 32, 32.

From such a viewpoint, each of the above thrust ball bearings 3
Conventionally, a structure described in Japanese Utility Model Laid-Open No. 7-35847 is known as a structure for supplying a sufficient amount of lubricating oil to 2, 32. 10 to 13 show this conventional structure. One or more oil supply holes 38 are formed in a part of the outer ring 35, and lubricating oil is forcibly fed into each of the oil supply holes 38 during operation of the toroidal type continuously variable transmission. The lubricating oil forcibly fed into each of the oil supply holes 38 forms a gap between the inner surface of the outer race 35 and the outer surface of the retainer 34 and the gap between the inner surface of the retainer 34 and the outer end surface of the power roller 8. It flows through the gap between the lubricating parts, and lubricates the rolling parts of the plurality of balls 33 during that.

The main body 39, which is made of a metal such as copper or steel and forms a ring shape, constitutes the retainer 34. Circular pockets 36, 36 to be movably held are formed. Also, grooves 40, 40 are formed on both the inner and outer surfaces of the main body 39.
Over the diametrical direction of the main body 39, the pockets 3
6 and 36 are formed.

During operation of the toroidal type continuously variable transmission incorporating the retainer 34 as described above, the thrust ball bearing 32 is formed by the force of the lubricating oil discharged from the oil supply hole 38 formed in the outer race 35 or the like. Even if the holder 34 is displaced in the axial direction and the inner surface of the retainer 34 and the outer end surface of the power roller 8 come into close contact with each other, as shown in FIG.
A sufficient amount of lubricating oil flows through each of the concave grooves 40, 40 in the pockets 36, 36 holding the holes. As a result, there is no shortage of lubricating oil existing in the contact portion between the raceway surface formed on the outer end surface of the power roller 8 and the rolling surface of each ball 33, and a part of the thrust ball bearing 32 is formed. The risk of significant wear or seizure can be reduced.

[0020]

In the case of the conventional structure as described above, the inner peripheral surfaces of the plurality of pockets 36, 36 formed in the retainer 34 constituting the thrust ball bearing 32, and the inside of each of these pockets 36, 36 However, it was not always possible to sufficiently reduce the friction of the rubbed portions of the balls 33, 33 held with the rolling surfaces. This reason will be described with reference to FIGS. When the toroidal-type continuously variable transmission is operated, the peripheral surface 8a of each of the power rollers 8 is subjected to a large thrust load generated by the pressing device 9 (see FIGS. 7 to 9) based on FIG.
Are applied in the directions indicated by arrows α and α. Then, as a result of these power rollers 8 being strongly clamped at two positions on the opposite side in the diametrical direction, as shown in an exaggerated manner in FIG. It is elastically deformed into the elliptical shape shown. Accordingly, the shape of the raceway surface with which each of the balls 33, 33 constituting the thrust ball bearing 32 abuts is also deformed into an elliptical shape, and the contact angle between each of the balls 33, 33 and the raceway surface is changed in the circumferential direction. Across the board.

As the torque is transmitted from the input disk 2 to the output disk 4 via the power rollers 8, the rotation center axes of the power rollers 8 tend to be inclined. For example, as shown in FIG. 16, the input side disk 2 is in the direction of arrow A, the power rollers 8 are in the direction of arrow B, the output side disk 4 is in the direction of arrow C,
When rotating, respectively, to the power roller 8 in the same direction as the rotational direction of the input side disk 2 from the input side disk 2, F _t becomes a force is applied. At the same time, the power roller 8 by reaction with the possible transmitting power to the output side disk 4 from the power rollers 8, in a direction opposite to the rotation direction of the output side disk 4, applied is also F _t becomes force. As a result, as shown in FIG. 17, a force having a magnitude of 2 _Ft is applied to the power roller 8 as a force to incline the power roller 8 in the rotation direction of the input side disk 2. As a result, the center axis of rotation of each of the power rollers 8 having the raceway surface formed on the outer end face thereof becomes inconsistent with the center axis of each of the outer rings 35, and these power rollers 8 and the respective outer rings 3
5 are non-parallel to each other.

As described above, the contact angles between the balls 33, 33 and the raceway surface become unequal in the circumferential direction, and the raceway surfaces forming the thrust ball bearing 32 are paired with each other. As a result of the non-parallelism, the revolving speed of each of the balls 33, 33 becomes uneven in the circumferential direction. FIG. 18 shows a state in which the revolution speed of each of the balls 33, 33 changes depending on the circumferential position. The retainer 34 rotates clockwise in FIG. 18, and the power roller 8
(See FIG. 14) is sandwiched from the left and right opposite sides in FIG. 18, the magnitude of the force consisting 2F _t shall exerted upward in FIG. The magnitude of the revolving speed of each of the balls 33, 33 is
In FIG. 18, it is represented as the length of an arrow extending from the center of each pocket 36, 36. However, the ratio of the lengths of these arrows is exaggerated compared to the ratio of the actual revolution speed.

As described above, the revolving speed of each of the balls 33, 33 constituting each of the thrust ball bearings 32 changes in the circumferential direction. As a result, the rolling surface of each of the balls 33 becomes the cage 34. May be strongly pressed against the inner peripheral surfaces of the pockets 36, 36 formed as described above. The arrows shown in FIG. 19 indicate that the rolling surfaces of the balls 33 are the pockets 36, 36, respectively.
Indicates the direction in which the inner peripheral surface is pressed, and the length of each arrow indicates the pressing strength. As is clear from FIG. 19, the balls 33, 3 are provided on the inner peripheral surfaces of the pockets 36, 36 provided in the retainer 34 during operation of the toroidal type continuously variable transmission.
The rolling surface of No. 3 (the portion of the rolling surface that comes into rolling contact with the raceway surface) may be strongly pressed.

While the rolling surfaces of the balls 33, 33 are strongly pressed against the inner peripheral surfaces of the pockets 36, 36, as shown in FIGS.
When the balls 33, 33 roll within the wheel 6, these FIGS.
There is a possibility that a sufficient oil film may not be easily formed in the contact portion 41 between the two surfaces shown in FIG. If the oil film formation of the contact portion 41 becomes insufficient, the rolling resistance of the balls 33, 33 increases, and the thrust ball bearings 32, 32 increase.
Not only does the transmission torque of the toroidal type continuously variable transmission deteriorate, but also the pockets 36, 36
Wear becomes remarkable. The toroidal-type continuously variable transmission of the present invention has been invented in view of such circumstances.

[0025]

The toroidal type continuously variable transmission according to the present invention has a rotary shaft and a rotary shaft around the rotary shaft, similarly to the above-described conventionally known toroidal type continuously variable transmission. First and second discs which are freely supported and whose inner surfaces are opposed to each other, and a plurality of discs which swing about a pivot axis which is twisted with respect to the center axis of the first and second discs A trunnion, a displacement shaft supported by each of the trunnions so as to protrude from the inner surface of each of the trunnions, and the first and second trunnions supported rotatably around the respective displacement shafts. A plurality of power rollers sandwiched between disks, and a thrust provided between each of the power rollers and the inner surface of each of the trunnions to support a load in a thrust direction applied to each of the power rollers. And a bearing. The inner surfaces of the first and second disks are each concave in cross section, and the peripheral surface of each of the power rollers is a spherical convex surface. Are in contact with each other. Each of the thrust ball bearings includes a plurality of balls, a retainer for rotatably holding the plurality of balls, and an outer ring supported on an inner surface of each of the trunnions. Further, each of these retainers includes a ring-shaped main body, and a plurality of pockets formed at a diametrically intermediate portion of the main body and holding the balls in a rollable manner inside the main body. It is. In particular, in the toroidal type continuously variable transmission of the present invention, an oil sump is placed on a portion of the inner peripheral surface of each pocket where the ball held in each pocket is pressed, more than an inner peripheral surface of each pocket. It is provided in a recessed state.

[0026]

The toroidal-type continuously variable transmission according to the present invention as described above has an inner peripheral surface of a pocket of a cage constituting a thrust ball bearing attached to a power roller, and rolling of the ball held in each pocket. A sufficient oil film can always be formed at the contact portion with the surface. Therefore, the transmission torque of the thrust ball bearing can be reduced to increase the transmission efficiency of the toroidal-type continuously variable transmission, and the occurrence of significant wear on the inner peripheral surface of each pocket can be prevented.

[0027]

1 and 2 show a first embodiment of the present invention. The feature of the present invention is that the cage 3
A ball 33 is formed on the inner peripheral surface of each pocket 36, 36 provided in the 4a.
(See FIGS. 14, 17, and 21) Oil reservoirs are formed on the inner peripheral surfaces of the pockets 36 and 36 so as to form a sufficient oil film on a portion where the ball 33 is pressed against, in other words, a portion that rubs against the rolling surface of the ball 33. The point is to form. 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, and the following description will focus on the characteristic parts of the present invention.

In the retainer 34a, a plurality of circular pockets 36, 36 are respectively formed at equal intervals in a circumferential direction on a main body 39 formed in a ring shape from a metal such as steel or copper. . In the case of this example, each of these pockets 36,
Of the inner peripheral surface of the main body 39, concave grooves 42, 42 are formed at two positions opposite to each other with respect to the circumferential direction of the main body 39 in such a manner as to open on both front and back surfaces of the main body 39,
The inside of each of the concave grooves 42 is used as an oil reservoir. Incidentally, both side edges of these concave grooves 42, 42 and the above-mentioned pockets 36,
The continuation portion with the inner peripheral surface of 36 is smoothly continuous with each curved surface.

A thrust ball bearing 32 (FIGS. 9, 14 and 1) for supporting the power roller 8 with the retainer 34a as described above.
7), the inner peripheral surfaces of the pockets 36, 36 of the retainer 34a and the balls 3 held in the respective pockets 36, 36.
A sufficient oil film can always be formed at the contact portions between the rolling surfaces 3 and 33. That is, since the lubricating oil is always supplied to the contact portion through the concave grooves 42, 42, the respective balls 33, 3
Even when each of the balls 33, 33 rolls in a state in which the ball 3 is pressed strongly against the inner peripheral surface of each of the pockets 36, a sufficient amount of lubricating oil is taken into the contact portion.
For this reason, the rotational torque of the thrust ball bearing 32 can be reduced to increase the transmission efficiency of the toroidal-type continuously variable transmission, and it is possible to prevent the inner peripheral surfaces of the pockets 36, 36 from being significantly worn.

Next, FIGS. 3 and 4 show a second example of the embodiment of the present invention. In the case of the retainer 34b of this example,
In the inner peripheral surfaces of the pockets 36, 36, circular concave holes 43, 43 are formed at two positions opposite to each other with respect to the circumferential direction of the main body 39 and at the center in the axial direction. , 43 are oil reservoirs. In addition, the periphery of the opening of each of the concave holes 43, 43 and the above-mentioned pockets 36, 36
Are also smoothly connected to the inner peripheral surface by curved surfaces.

In the case of this embodiment as well, the pocket 3
The inner peripheral surfaces of the holes 6, 36 and the rolling surfaces of the balls 33, 33 (see FIGS. 14, 17, 21) held in the pockets 36, 36 are provided in the recesses 43, 43. Since the lubricating oil accumulated in the pockets 36 is supplied, the rotational torque of the thrust ball bearing incorporating the retainer 34b can be reduced to increase the transmission efficiency of the toroidal-type continuously variable transmission. Significant wear on the peripheral surface can be prevented.

Next, FIGS. 5 and 6 show a third embodiment of the present invention. In the case of the retainer 34c of the present example,
In the axially central portion of the inner peripheral surface of each of the pockets 36, 36, an annular concave groove 44, 44 is formed, respectively.
The groove 36 is formed over the entire circumference, and the inside of each of the grooves 44 is used as an oil reservoir. The continuous portions between the side edges of the concave grooves 44 and the inner peripheral surfaces of the pockets 36 are smoothly connected to each other by curved surfaces.

In the case of this embodiment as well, the pocket 3
The abutment portions between the inner peripheral surfaces of the grooves 6 and 36 and the rolling surfaces of the balls 33 and 33 (see FIGS. 14, 17 and 21) held in the respective pockets 36 and 36 are provided with the concave grooves 44 and 44. Since the lubricating oil accumulated in the pockets 36 is supplied, the rotational torque of the thrust ball bearing incorporating the retainer 34c can be reduced to increase the transmission efficiency of the toroidal-type continuously variable transmission. Significant wear on the peripheral surface can be prevented.

[0034]

The toroidal type continuously variable transmission of the present invention is constructed and operated as described above, and incorporates this thrust ball bearing in order to ensure the lubrication of the thrust ball bearing attached to the power roller. The reliability and durability of the toroidal type continuously variable transmission can be improved.

[Brief description of the drawings]

FIG. 1 is a partial plan view of a retainer, showing a first example of an embodiment of the present invention.

FIG. 2 is an enlarged sectional view taken on line AA of FIG. 1;

FIG. 3 is a partial plan view of a cage, showing a second example of the embodiment of the present invention.

FIG. 4 is an enlarged sectional view taken along line BB of FIG. 3;

FIG. 5 is a partial plan view of the retainer, showing a third example of the embodiment of the present invention.

FIG. 6 is an enlarged sectional view taken along the line CC of FIG. 5;

FIG. 7 is a side view showing a basic configuration of a conventionally known toroidal-type continuously variable transmission in a state of maximum deceleration.

FIG. 8 is a side view similarly showing a state at the time of maximum acceleration.

FIG. 9 is a sectional view showing an example of a conventional specific structure.

FIG. 10 is an enlarged view of a portion D in FIG. 9;

FIG. 11 is a diagram illustrating only the retainer taken out and viewed from above in FIG. 10;

FIG. 12 is an enlarged sectional view taken along the line EE of FIG. 11;

FIG. 13 is a view as seen from the direction of arrow F in FIG. 12;

FIG. 14 is a partial cross-sectional view for explaining a force applied to the power roller during operation.

FIG. 15 is a schematic plan view exaggeratingly showing a state in which the power roller is elastically deformed during operation.

FIG. 16 is a schematic view from above of FIG. 14 for explaining another force applied to the power roller during operation.

FIG. 17 is a sectional view taken along the line GG of FIG. 14;

FIG. 18 is a diagram showing a state in which the revolution speed of each ball constituting the thrust ball bearing changes during operation, as viewed in the same direction as FIG. 16;

FIG. 19 shows a state in which a force is applied to each part of the cage with a change in the revolution speed of each ball constituting the thrust ball bearing during operation.
The figure shown in the state seen from the same direction as FIG.

FIG. 20 is a partial plan view illustrating a contact portion between the inner peripheral surface of the pocket and the rolling surface of the ball.

FIG. 21 is a partial sectional view of the same.

[Description of Signs] 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 Clutch 16 Input shaft 17 Needle bearing 18 Output shaft 19 Housing 20 Ball bearing 21 Roller bearing 22 Ball bearing 23 Sleeve 24 Drive-side forward gear 25 Drive-side reverse gear 26 Transmission gear 27 Take-out shaft 28 Follower-side forward gear 29 Driven-side reverse gear 30 Nut 31 Stop ring 32 Thrust ball bearing 33 Ball 34, 34a, 34b, 34c Cage 35 Outer ring 36 Pocket 37 Thrust bearing 38 Oil supply hole 39 Main body 40 Groove 41 Contact portion 42 Groove 43 Groove 44 Groove

 ──────────────────────────────────────────────────続 き Continued on the front page F term (reference) 3J051 AA03 BA03 BD02 BE09 CA05 CB07 ED20 FA02 3J063 AA02 AB33 BA20 BB11 CA01 CB36 CD02 XD03 XD42 XD73 3J101 AA02 AA32 AA42 AA54 AA63 BA35 CA14 FA32 GA11

Claims (1)

[Claims] 1. A rotating shaft, first and second disks rotatably supported around the rotating shaft and having respective inner surfaces facing each other, and a first and a second disk of the first and second disks. A plurality of trunnions swinging about a pivot axis at a position twisted with respect to the central axis, a displacement axis supported by each of the trunnions in a state of protruding from the inner surface of each trunnion, and a periphery of each of these displacement axes. In a state supported rotatably, a plurality of power rollers sandwiched between the first and second disks, and provided between each of these power rollers and the inner surface of each of the trunnions, A thrust ball bearing for supporting a load in the thrust direction applied to the power roller, wherein the inner surfaces of the first and second disks are arc-shaped concave surfaces in cross-section, and the peripheral surface of each of the power rollers is A spherical convex surface, each of these peripheral surfaces and each of the inner side surfaces are in contact with each other, and each of the thrust ball bearings has a plurality of balls and a retainer that holds the plurality of balls in a freely rolling manner. And an outer ring supported on the inner surface of each of the trunnions.These retainers are formed in an annular main body, each of which is formed at a diametrically intermediate portion of this main body, and the In a toroidal-type continuously variable transmission having a plurality of pockets for rollingly holding each ball, a portion of the inner peripheral surface of each pocket where the ball held in each pocket is pressed. A toroidal-type continuously variable transmission, wherein an oil sump is provided in a recessed state from the inner peripheral surface of each of these pockets.