JP2000193057A - Toroidal type continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To sufficiently feed a lubricant without exceeding its quantity fed to a thrust ball bearing whole body by supporting a thrust ball bearing outer ring in such a state as stopping the relative rotation to a displacement shaft and providing oil feed holes in prescribed parts of the outer ring of the thrust ball bearing. SOLUTION: In this toroidal type continuously variable transmission, the rotation of an input-side disc is transmitted to an output-side disc via a pair of power rollers 8 and, when changing the rotation speed ratio between the input and output sides, a pair of trunnions 6 are displaced inversely by a drive piston. In a thrust ball bearing 29 for supporting the power rollers 8 to the trunnions 6, its circular outer ring 31 is externally fitted around a flange part 35 formed in a base part of a pivot shaft 26 constituting the displacement shaft 7. Oil feed holes 38 communicating the both faces of the outer ring 31 with each other are provided in four parts towards more inside diameter side than the outer ring track 37 formed in the outer ring 31 at equal intervals in the circumferential direction along the central axis of the inner ring 31 so as to secure oil feeding performance.

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 for an automobile or as a transmission for various industrial machines.

[0002]

2. Description of the Related Art The use of a toroidal-type continuously variable transmission as schematically shown in FIGS. This toroidal type continuously variable transmission supports an input disk 2 concentrically with an input shaft 1 as disclosed in, for example, Japanese Utility Model Laid-Open Publication No. 62-71465.
The output side disk 4 is fixed to the end of the output shaft 3 which is arranged concentrically. Inside the casing containing the toroidal-type continuously variable transmission, trunnions 6, 6 that swing about pivots 5, 5 that are twisted with respect to the input shaft 1 and the output shaft 3, are provided.

That is, these trunnions 6, 6 arranged at portions off the central axis of the two disks 2, 4 have the pivots 5, 5 on the outer surfaces of both ends, respectively, and the center of the two disks 2, 4 They are provided in a direction perpendicular to the direction of the axis and concentric with each other. In addition, the trunnions 6 and 6 support the base ends of the displacement shafts 7 and 7 at the intermediate portions thereof, and swing the trunnions 6 and 6 about the pivots 5 and 5 so that the respective displacements can be adjusted. The inclination angles of the shafts 7, 7 can be adjusted freely. Power rollers 8 are rotatably supported around the displacement shafts 7 supported by the trunnions 6 respectively. The power rollers 8, 8 are sandwiched between the inner surfaces 2a, 4a of the input and output disks 2, 4 facing each other. Each of the inner side surfaces 2a, 4a has a concave section obtained by rotating an arc around the pivot 5 as described above. Then, the peripheral surfaces 8a, 8a of the power rollers 8, 8, which are formed into spherical convex surfaces, are connected to the inner surfaces 2a, 4a.
a.

A loading cam device 9 is provided between the input shaft 1 and the input disk 2, and the loading cam device 9 elastically presses the input disk 2 toward the output disk 4. The input side disk 2 is freely rotatable. The loading cam device 9 includes a loading cam 1 that rotates with the input shaft 1.
0 and a plurality (for example, four) of rollers 12, which are rotatably held by a retainer 11. One side of the loading cam 10 (right side in FIGS. 8 and 9)
A cam surface 13 which is uneven in the circumferential direction,
A cam surface 14 having a similar shape is also formed on the outer side surface (the left side surface in FIGS. 8 and 9) of the input side disk 2. Then, the plurality of rollers 12 are connected to the input shaft 1.
Are rotatably supported about a radial axis.

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

When the rotational speed ratio (speed change ratio) between the input shaft 1 and the output shaft 3 is changed, and when deceleration is first performed between the input shaft 1 and the output shaft 3, each of the pivots 5 The trunnions 6, 6 are swung in a predetermined direction as a center. The peripheral surfaces 8a, 8a of the power rollers 8, 8 are shown in FIG.
As shown in FIG. 5, the displacement shafts 7, 7 are inclined so as to abut against the central portion of the inner surface 2a of the input disk 2 and the outer peripheral portion of the inner surface 4a of the output disk 4, respectively. Conversely, when increasing the speed,
, Each of the trunnions 6 is swung in the opposite direction. The peripheral surface 8 of each of the power rollers 8
As shown in FIG. 9, the displacement shafts 7 a and 8 a abut against the outer peripheral portion of the inner surface 2 a of the input disk 2 and the central portion of the inner surface 4 a of the output disk 4, respectively. , 7 are tilted. If the inclination angle of each of the displacement shafts 7 is in the middle between FIGS. 8 and 9, an intermediate speed ratio can be obtained between the input shaft 1 and the output shaft 3.

FIGS. 10 to 11 show Japanese Utility Model Application No. 63-692.
1 shows an example of a more specific toroidal-type continuously variable transmission described in the microfilm of No. 93 (Japanese Utility Model Laid-Open No. 1-173552). The input-side disk 2 and the output-side disk 4 are rotatably supported around a cylindrical input shaft 15 via needle bearings 16 and 16, respectively. That is, the input side disk 2 and the output side disk 4
Through holes 17, 17 having a circular cross-sectional shape
Are formed so as to penetrate the inner surface and the outer surface of each of the disks 2 and 4 in the axial direction (the left-right direction in FIG. 10). The needle bearings 16 are provided between the inner peripheral surfaces of the through holes 17 and the intermediate outer peripheral surface of the input shaft 15. Also, retaining rings 19, 19 are locked in locking grooves 18, 18 formed in the inner peripheral surface of the end portions of the through holes 17, 17 near the inner surface, and the needle bearings 16,
16 is prevented from coming out of the through holes 17, 17 toward the inner surfaces 2 a, 4 a of the disks 2, 4. The loading cam 10 is spline-engaged with the outer peripheral surface of the input shaft 15 at the end (the left end in FIG. 10), and is prevented from moving away from the input disk 2 by the outward flange-shaped flange 20. ing. The loading cam 10 and the rollers 12 and 12 constitute a loading cam device 9 for rotating the input disk 2 while pressing the input disk 2 toward the output disk 4 based on the rotation of the input shaft 15. I have. An output gear 21 is connected to the output side disk 4 by keys 22, 22.
The output disk 4 and the output gear 21 rotate in synchronization.

Both ends of the pair of trunnions 6, 6 are supported on a pair of support plates 23, 23 so as to be swingable and displaceable in the axial direction (front and back directions in FIG. 10, and left and right directions in FIG. 11). I have. The displacement shafts 7, 7 are supported in circular holes 24, 24 formed in the middle portions of the trunnions 6, 6, respectively. Each of these displacement shafts 7 has a support shaft 25, 25 and a pivot shaft 26, 26 which are parallel and eccentric to each other. Each of the support shaft portions 25, 25 is provided with a radial needle bearing 27 inside the circular hole 24, 24.
It is rotatably supported via 27. The power rollers 8, 8 are rotatably supported around the pivot shafts 26, 26 via other radial needle bearings 28, 28, respectively.

The pair of displacement shafts 7, 7 are provided at positions opposite to the input shaft 15 by 180 degrees. or,
The direction in which the respective pivot shafts 26, 26 of the respective displacement shafts 7, 7 are eccentric with respect to the respective support shafts 25, 25 is the same as the rotation direction of the input side and output side disks 2, 4. In FIG. 11, the left and right directions are opposite. The eccentric direction is
The direction is substantially perpendicular to the direction in which the input shaft 15 is provided. Accordingly, the power rollers 8 are supported to be slightly displaceable in the direction in which the input shaft 15 is provided. As a result, the power rollers 8, 8 move in the axial direction of the input shaft 15 (see FIG. Even in the case of displacement in the left-right direction (the front-back direction in FIG. 11), this displacement can be absorbed without applying unreasonable force to the components.

Further, between the outer surface of each of the power rollers 8, 8 and the inner surface of the intermediate portion of each of the trunnions 6, 6, a thrust ball bearing 29, 29 and thrust needle bearings 30, 30 are provided. Of these, the thrust ball bearings 29, 29 allow rotation of the power rollers 8, 8 while supporting the load in the thrust direction applied to the power rollers 8, 8. Also, each of the above thrust needle bearings 3
0, 30 support the thrust loads applied from the power rollers 8, 8 to the outer races 31, 31 constituting the respective thrust ball bearings 29, 29 while supporting the pivot shaft portions 26, 2,
6 and the outer races 31, 31 are supported by the support shafts 25, 25.
Swinging around the center.

Further, drive rods 32, 32 are provided at one end (the left end in FIG. 11) of each of the trunnions 6, 6, respectively.
And drive pistons 33, 33 are fixedly mounted on the outer peripheral surface of the intermediate portion of each of the drive rods 32, 32. And
These drive pistons 33, 33 are oil-tightly fitted in drive cylinders 34, 34, respectively.

In the case of the toroidal type continuously variable transmission configured as described above, the rotation of the input shaft 15 is transmitted to the input side disk 2 via the loading cam device 9. The rotation of the input disk 2 is transmitted to the output disk 4 via the pair of power rollers 8, 8, and the rotation of the output disk 4 is extracted from the output gear 21. When changing the rotation speed ratio between the input shaft 15 and the output gear 21, the pair of drive pistons 33 are displaced in opposite directions. The pair of trunnions 6, 6 are displaced in opposite directions with the displacement of the driving pistons 33, 33. For example, the lower power roller 8 in FIG. Are displaced to the left in FIG. As a result, the direction of the tangential force acting on the contact portions between the peripheral surfaces 8a, 8a of the power rollers 8, 8 and the inner surfaces 2a, 4a of the input disk 2 and the output disk 4 changes. I do. Then, with the change in the direction of the force, each of the trunnions 6, 6 is pivoted around the pivots 5, 5, which are pivotally supported by the support plates 23, 23.
Swing in opposite directions. As a result, as shown in FIGS. 8 and 9 described above, the peripheral surfaces 8a, 8
a and the inner surfaces 2a, 4a change, and the rotational speed ratio between the input shaft 15 and the output gear 21 changes.

Incidentally, the input shaft 15 and the output gear 2
When transmitting the rotational force between the power rollers 8, the power rollers 8, 8 are displaced in the axial direction of the input shaft 15 based on the elastic deformation of the constituent members. Each of the displacement shafts 7 that pivotally support 8 rotates slightly about each of the support shaft portions 25. As a result of this rotation, the outer ring 3 of each of the thrust ball bearings 29, 29
The outer surfaces of the trunnions 6 and 6 are relatively displaced from each other. Since the thrust needle bearings 30, 30 exist between the outer surface and the inner surface, the force required for the relative displacement is small. Therefore, the force for changing the inclination angle of each of the displacement shafts 7 can be small as described above.

During operation of the toroidal-type continuously variable transmission configured and operated as described above, each of the power rollers 8 rotates at a high speed while receiving a large thrust load. Therefore, it is necessary to supply a sufficient amount of lubricating oil (traction oil) to the thrust ball bearing 29 provided between each of the power rollers 8, 8 and the inner surface of each of the trunnions 6, 6. For this reason, conventionally, as described in, for example, JP-A-7-174146, JP-A-7-35847, and the like, a lubrication hole is formed in an outer ring constituting a thrust ball bearing for supporting a power roller. In addition, it has been considered to form a groove for oil supply in a cage constituting the thrust ball bearing.

[0015]

In the case of the conventional structure, a thrust ball bearing 29 for allowing the rotation of the power roller 8 while supporting the thrust load applied to the power roller 8.
Did not consider refueling a particular part of the car. In other words, it has been thought that if any part of the entire circumference of the thrust ball bearing 29 is lubricated, the lubricating oil flows from the part to the other part, and the necessary lubrication can be performed.

However, the thrust load applied to the thrust ball bearing 29 during operation of the toroidal type continuously variable transmission is as follows.
It is not uniform over the entire circumference, but is large in the longitudinal direction of the trunnion 6 and small in the direction perpendicular to it. That is, as shown in FIG. 12, when considering the points existing at equal intervals in the circumferential direction on the raceway surface of the thrust ball bearing 29, the magnitude of the thrust load at each point is as shown in FIG. 13. Become. FIG. 13 shows that a larger thrust load is applied to the outer diameter side. The reason that the magnitude of the thrust load differs in this way is that the trunnion 6 is curved in a direction in which the inner surface becomes concave based on a large thrust load applied to the power roller 8 during operation.

In view of the fact that the magnitude of the thrust load applied to the thrust ball bearing 29 differs at a specific phase in the circumferential direction, if the lubrication state of the thrust ball bearing 29 is devised, a small amount of lubrication can be obtained. With sufficient lubrication,
The rolling resistance of the thrust ball bearing 29 can be reduced (torque increase due to excessive lubricating oil supply) and rolling fatigue life can be ensured (rolling fatigue life can be prevented from decreasing due to insufficient lubricating oil supply). However, the conventional toroidal-type continuously variable transmission does not take such a thing into consideration.

In particular, in order to feed the lubricating oil into the thrust ball bearing 29, it is preferable to form an oil supply hole in a part of the outer ring 31 constituting the thrust ball bearing 29. 7 is rotatably fitted and supported on the displacement shaft 7. For this reason, the outer ring 31
The phase of the oil supply hole formed in the circumferential direction in the circumferential direction cannot be restricted due to the relationship with the magnitude of the thrust load applied to the thrust ball bearing 29. In view of the above circumstances, the toroidal type continuously variable transmission according to the present invention realizes a structure in which a specific portion of the thrust ball bearing 29 is supplied with oil.
No. 9 was invented in order to achieve both reduction of rolling resistance and securing of rolling fatigue life.

[0019]

The toroidal-type continuously variable transmission according to the present invention, like the above-mentioned conventional toroidal-type continuously variable transmission, has the inner surfaces facing each other and is concentric with each other. And the first and second disks rotatably supported, and the torsion not intersecting with the central axes of the first and second disks, but being at right angles to the directions of the central axes of the two disks. A trunnion swinging about a pivot at the position, a circular hole formed in the middle of the trunnion in a direction perpendicular to the pivot, and a support shaft and a pivot shaft parallel and eccentric to each other. A shaft, a radial needle bearing provided between the outer peripheral surface of the support shaft portion and the inner peripheral surface of the circular hole and rotatably supporting the displacement shaft with respect to the trunnion; Out of the above trunnion A power roller sandwiched between the first and second disks and rotatably supported around the pivot shaft protruding from the side surface, and a power roller interposed between the first and second disks and an outer surface of the power roller. A thrust ball bearing that allows the power roller to rotate while supporting a thrust load applied to the power roller; and an outer surface of the thrust ball bearing outer ring and the trunnion that constitute the thrust ball bearing. The supporting shaft portion and the thrust ball bearing outer ring are provided between the power roller and the thrust ball bearing outer ring while supporting the thrust load applied to the thrust ball bearing outer ring. And an allowable thrust bearing. The inner surface of each of the first and second disks is a concave surface having an arc-shaped cross section, and the peripheral surface of the power roller is a spherical convex surface. Abut each other. In particular, in the toroidal type continuously variable transmission of the present invention, the thrust ball bearing outer ring is supported in a state where relative rotation with respect to the displacement shaft is prevented, and a part of the thrust ball bearing outer ring is provided. In at least a portion corresponding to a portion where the thrust load received by the thrust ball bearing is large, an oil supply hole for supplying lubricating oil to this portion is provided.

[0020]

The toroidal-type continuously variable transmission according to the present invention configured as described above transmits the rotational force between the first and second disks and the speed ratio between the two disks. Is the same as that of the conventionally known toroidal-type continuously variable transmission as described above. In particular, in the case of the toroidal-type continuously variable transmission of the present invention, lubricating oil is supplied to a portion of the thrust ball bearing that supports the power roller, where the thrust ball bearing receives a large thrust load, and the entire thrust ball bearing is supplied. The lubricating oil to be supplied can be sufficiently supplied without making the amount excessive.

[0021]

1 and 2 show a first embodiment of the present invention. A feature of the present invention is that a thrust ball bearing 2 for supporting the power roller 8 on the trunnion 6 is provided.
9 is a structure of a portion for supplying lubricating oil. The structure and operation of the other parts, including the conventional structure described above, are the same as those of various conventionally known or considered toroidal-type continuously variable transmissions, and therefore illustration and description of equivalent parts are omitted or omitted. For simplicity, the following description focuses on the features of the present invention.

The ring-shaped outer ring 31 constituting the thrust ball bearing 29 is externally fitted to a flange 35 formed at the base end of the pivot shaft 26 constituting the displacement shaft 7. A key 17 is provided between the outer peripheral edge of the flange 35 and the inner peripheral edge of the outer ring 31 to prevent the outer ring 31 from rotating with respect to the displacement shaft 7. Since the amount of swing displacement of the displacement shaft 7 with respect to the trunnion 6 is limited, the degree of deviation between the length direction of the trunnion 6 and the phase in the circumferential direction of the outer ring 31 is limited.

An outer raceway 37 formed on the outer race 31
Oil supply holes 38, 38 for communicating both sides of the outer ring 31 at circumferentially equidistant positions at four locations on the inner diameter side of the outer ring 31
Are provided in parallel with the central axis of the inner ring 31. Two of the four oil supply holes 38 are arranged in the longitudinal direction of the trunnion 6. Oiling grooves 40 are formed on both surfaces of the retainer 39 constituting the thrust ball bearing 29.

During operation of the toroidal type continuously variable transmission, the lubricating oil supplied through the piston rod 32 (FIG. 11) and the oil supply passage 41 provided inside the trunnion 6 and discharged to the inner surface of the middle portion of the trunnion 6 The inner diameter side of the thrust ball bearing 29 and the radial needle bearing 2 through a second oil supply passage 42 provided in the pivot shaft portion 26 of the displacement shaft 7.
8 as well as the rolling surfaces of the balls 43, 43 constituting the thrust ball bearing 29, the outer raceway 37, and the power roller 8 via the oil holes 38, 38 and the oil grooves 40, 40. Of the inner ring raceway 44 formed on the inner end face of the roller.

As described above, in the case of the toroidal-type continuously variable transmission of the present invention, the thrust ball bearing 29 supporting the power roller 8 is a portion where the thrust load received by the thrust ball bearing 29 is large. Lubricating oil is fed directly to both ends in the longitudinal direction of the trunnion 6 without passing through other parts. Therefore, the lubricating oil can be sufficiently supplied to both ends in the longitudinal direction of the trunnion 6 without making the amount of the lubricating oil supplied to the entire thrust ball bearing 29 excessive.

Next, FIGS. 3 and 4 show a second example of the embodiment of the present invention. In the case of this example, of the four oil supply holes 38 formed in the outer ring 31, the downstream ends of the two oil supply holes 38 located in the longitudinal direction of the trunnion 6 are connected to the inner peripheral edge of the outer ring 31. It is opened inside concave grooves 45, 45 provided between the outer raceway 37. In addition, the outer ring 3
Numeral 1 is externally fitted and fixed to a flange 35 provided on the displacement shaft 7 by interference fit to prevent relative rotation with respect to the displacement shaft 7.

In the case of this embodiment, the lubricating oil discharged from the two oil supply holes 38, 38 located in the longitudinal direction of the trunnion 6 passes through the grooves 45, 45 of the thrust ball bearing 29. And efficiently sent to the part where the largest thrust load is applied. The configuration and operation of the other parts are the same as in the case of the first example described above, and therefore, the same reference numerals are given to the same parts, and redundant description will be omitted.

FIG. 5 shows a third embodiment of the present invention.
An example is shown. In the case of this example, the inner peripheral surface of the outer ring 31 constituting the thrust ball bearing is formed in an oval shape.
The outer circumference of the outer ring 31 and the displacement shaft 7 is prevented from rotating by fitting the outer ring to an oval flange formed at the intermediate portion of the displacement shaft 7. Other configurations and operations are the same as those of the above-described first example, and therefore illustration and description of the equivalent parts are omitted.

Next, FIGS. 6 and 7 show a fourth embodiment of the present invention. In the case of this example, of the four oil supply holes 38, 38 a formed in the outer ring 31, two oil supply holes 38 a, 38 a positioned in the length direction of the trunnion 6 are inclined with respect to the central axis of the outer ring 31. And the downstream end of each of the oil supply holes 38a, 38a is opened at a portion of the inner ring side of the outer ring raceway 37 formed in the outer ring 31 so as not to come into contact with the rolling surfaces of the balls 43, 43. .

In the case of the present embodiment, the lubricating oil discharged from the two oil supply holes 38a, 38a located in the length direction of the trunnion 6 is applied to the portion of the outer raceway 37 where the largest thrust load is applied. , Sent directly. Also in the case of the present example, similarly to the case of the above-described second example, the outer ring 31 is externally fixed to the flange 35 provided on the displacement shaft 7 by interference fitting to prevent relative rotation with respect to the displacement shaft 7. ing. Since the configuration and operation of the other parts are the same as those of the first example described above, the same reference numerals are given to the same parts, and redundant description will be omitted.

In implementing the present invention, the structure for preventing the relative rotation between the outer race 31 and the displacement shaft 7 and the structure for feeding the lubricating oil to the thrust ball bearing 29 are appropriately changed in combination. Can also be implemented. Further, the outer ring 31
The structure for preventing the relative rotation between the shaft and the displacement shaft 7 is as follows.
Other conventionally known structures such as spline engagement can also be employed.

[0032]

The toroidal type continuously variable transmission according to the present invention is constructed and operates as described above. Therefore, without sending excessive lubricating oil to the thrust ball bearing for supporting the power roller, the thrust ball can be used. The durability of the bearing can be secured. And by eliminating the need to pump in excess lubricant,
It is possible to prevent an increase in resistance due to lubricating oil in the thrust ball bearing portion, and to reduce power loss in a pump portion for supplying lubricating oil. As a result, a toroidal type continuously variable transmission having excellent efficiency and durability can be realized, which can contribute to the practical use of the toroidal type continuously variable transmission.

[Brief description of the drawings]

FIG. 1 is a sectional view of a power roller supporting portion with respect to a trunnion, showing a first example of an embodiment of the present invention.

FIG. 2 is a view seen from below in FIG. 1 with a power roller, a retainer and a ball removed, and a part of a displacement shaft omitted.

FIG. 3 is a view similar to FIG. 1, showing a second example of the embodiment of the present invention;

FIG. 4 is a view as viewed from below in FIG. 3, excluding a power roller, a retainer and balls, and omitting a part of a displacement shaft.

FIG. 5 is a view similar to FIG. 4, but showing a third example of the embodiment of the present invention;

FIG. 6 is a view similar to FIG. 1, showing the fourth example.

FIG. 7 is a view from below in FIG. 6, excluding a power roller, a retainer and balls, and omitting a part of a displacement shaft.

FIG. 8 is a schematic side view showing the toroidal-type continuously variable transmission to which the present invention is applied at the time of maximum deceleration.

FIG. 9 is a schematic side view similarly showing a state at the time of maximum acceleration.

FIG. 10 is a sectional view showing an example of a specific structure of a toroidal-type continuously variable transmission.

FIG. 11 is a sectional view taken along line AA of FIG. 10;

FIG. 12 is a schematic diagram for explaining a phase of a thrust ball bearing for supporting a power roller on a trunnion.

FIG. 13 is a diagram showing a relationship between a circumferential phase and a magnitude of a thrust load of a thrust ball bearing for supporting a power roller on a trunnion.

[Explanation of symbols]

 Reference Signs List 1 input shaft 2 input side disk 2a inner surface 3 output shaft 4 output side disk 4a inner surface 5 pivot 6 trunnion 7 displacement shaft 8 power roller 8a peripheral surface 9 loading cam device 10 loading cam 11 retainer 12 roller 13, 14 cam surface Reference Signs List 15 input shaft 16 needle bearing 17 through hole 18 locking groove 19 retaining ring 20 flange portion 21 output gear 22 key 23 support plate 24 circular hole 25 support shaft portion 26 pivot shaft portion 27 radial needle bearing 28 radial needle bearing 29 thrust ball Bearing 30 Thrust needle bearing 31 Outer ring 32 Drive rod 33 Drive piston 34 Drive cylinder 35 Flange 36 Key 37 Outer ring track 38, 38a Oil supply hole 39 Cage 40 Oil supply groove 41 Oil supply passage 42 Second oil supply passage 43 Ball 44 Inner ring track 45 Groove

Claims (1)

[Claims] 1. In a state where the inner side surfaces are opposed to each other,
First and second disks concentrically and rotatably supported, and a position perpendicular to the direction of the central axes of the first and second disks which do not intersect with the central axes of the first and second disks. A trunnion that swings about a pivot at a torsion position, a circular hole formed in the middle of the trunnion in a direction perpendicular to the pivot, a support shaft and a pivot that are parallel and eccentric to each other. A displacement axis having a portion,
A radial needle bearing provided between the outer peripheral surface of the support shaft portion and the inner peripheral surface of the circular hole to rotatably support the displacement shaft with respect to the trunnion; A power roller sandwiched between the first and second disks while being rotatably supported around the pivot shaft portion protruding from the inner surface of the trunnion, and an outer surface of the power roller. A thrust ball bearing that is attached to the power roller and allows rotation of the power roller while supporting a load in the thrust direction applied to the power roller; and an outer surface of a thrust ball bearing outer ring that constitutes the thrust ball bearing, and The pivot shaft portion and the thrust ball bearing outer ring are provided between the power roller and the thrust ball bearing outer ring, while supporting the thrust load applied to the thrust ball bearing outer ring from the power roller. A thrust bearing that allows rocking about the portion, the inner surfaces of the first and second disks are each concave in cross section, and the peripheral surface of the power roller is a spherical convex surface. In a toroidal-type continuously variable transmission in which the peripheral surface and the inner surfaces of the two disks are in contact with each other, the thrust ball bearing outer ring is supported in a state where relative rotation with respect to the displacement shaft is prevented. Has been
Further, at least a portion of the outer ring of the thrust ball bearing corresponding to a portion where the thrust ball bearing receives a large thrust load is provided with an oil supply hole for supplying lubricating oil to this portion. Toroidal type continuously variable transmission.