JP2001124164A - Toroidal continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To secure the rolling fatigue service life of an outer race orbit of an outer race regardless of a large load applied to a part of the outer race for constituting a thrust ball bearing. SOLUTION: Delivery holes 45a, 45b are arranged in a part opposed to a pitch circle of a thrust ball bearing 26 on an inside surface of a trunnion 6. Lubricating oil is delivered to a part for receiving a large load by a part of an outer race 28 from these respective delivery holes 45a, 45b to restrain a temperature rise in this part to solve the subject.

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 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. In this toroidal type continuously variable transmission, for example, as disclosed in Japanese Utility Model Laid-Open Publication No. Sho 62-71465, an input side disk 2 corresponding to a first disk described in the claims is concentrically arranged with an input shaft 1. An output disk 4 corresponding to a second disk described above is fixed to an end of an output shaft 3 which is supported and arranged concentrically with the input shaft 1. Inside the casing containing the toroidal type continuously variable transmission,
Although it does not intersect with the central axis of the input shaft 1 and the output shaft 3, it swings around the pivots 5, 5 which are in a twisted position which is perpendicular or nearly perpendicular to the direction of this central axis. A moving trunnion 6 is provided.

That is, each of the trunnions 6, 6 has the pivots 5, 5 concentrically provided on the outer surfaces of both ends. In addition, a base end of the displacement shafts 7, 7 is supported at an intermediate portion between the trunnions 6, 6, and the trunnions 6, 6 are pivoted about the pivots 5, 5, whereby
The tilt angles of the displacement shafts 7, 7 can be adjusted freely. Power rollers 8 are rotatably supported around the displacement shafts 7 supported by the trunnions 6 respectively. And each of these power rollers 8, 8 is
The input side and output side disks 2 and 4 are sandwiched between inner surfaces 2a and 4a facing each other. Each of the inner side surfaces 2a, 4a is obtained by rotating a circular arc or a curve close to such a circular arc centered on the pivot 5 around the central axis of the input shaft 1 and the output shaft 3. It is concave. The peripheral surfaces 8a, 8a of the power rollers 8, 8 formed in spherical convex surfaces are brought into contact with the inner side surfaces 2a, 4a.

[0004] 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 so as to be elastic. It can be pressed freely. The pressing device 9 includes a cam plate 10 that rotates together with the input shaft 1, and a plurality (for example, four) of rollers 12, which are rotatably held by a holder 11. The cam plate 10
On one side surface (the left side surface in FIGS. 3 and 4), a drive side cam surface 13 which is an uneven surface extending in the circumferential direction is formed, and the outer side surface of the input side disk 2 (the right side surface in FIGS. 3 and 4). Also, a driven cam surface 14 having a similar shape is formed. And
The plurality of rollers 12, 12 are supported so as to freely roll around 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, the driving-side cam surface 13 has a plurality of rollers 12, 12.
Is pressed against the driven cam surface 14 formed 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, the input side disk is pressed based on the pressing between the driving side and driven side cam surfaces 13, 14 and the plurality of rollers 12, 12. 2 rotates. 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 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. On the other hand, when increasing the speed,
Each of the trunnions 6 and 6 is swung in the opposite direction about 5. The peripheral surface 8 of each of the power rollers 8
As shown in FIG. 4, each of the displacement shafts 7a and 8a comes into contact with a portion of the inner surface 2a of the input disk 2 near the outer periphery and a portion of the inner surface 4a of the output disk 4 near the center. , 7 are tilted. If the inclination angle of each of the displacement shafts 7, 7 is set between those in FIGS. 3 and 4, the input shaft 1 and the output shaft 3
, An intermediate speed ratio can be obtained.

FIGS. 5 and 6 show Japanese Utility Model Application No. 63-69293.
FIG. 1 shows an example of a more specific toroidal type continuously variable transmission described in the microfilm of Japanese Utility Model Application Publication No. Hei 1-173552. The input side disk 2 and the output side disk 4 are rotatably supported around a cylindrical input shaft 15 via needle bearings 16, 16, respectively.
The cam plate 10 is spline-engaged with the outer peripheral surface of the input shaft 15 at the end (the left end in FIG. 5), and is prevented from moving away from the input disk 2 by the flange 17. The cam plate 10 and the rollers 12, 12 are used to load and rotate the input disk 2 while pressing the input disk 2 toward the output disk 4 based on the rotation of the input shaft 15. Is composed. The output side disk 4 is provided with an output gear 18 and a key 1.
The output side disk 4 and the output gear 18 rotate in synchronization with each other.

The pivots 5, 5 provided concentrically at both ends of the pair of trunnions 6, 6 are attached to a pair of support plates 20, 20.
The radial needle bearings 40, 40 each having an outer ring whose outer peripheral surface is a spherical convex surface, are supported so as to be swingable and displaceable in the axial direction of the pivots 5, 5 (front and back in FIG. 5, right and left in FIG. 6). I have. Then, displacement shafts 7, 7 are formed in circular holes 21, 21 formed in the middle portions of the trunnions 6, 6, respectively.
I support. Each of these displacement shafts 7, 7 is parallel and eccentric to the support shafts 22, 22, and the pivot shafts 23, 2,
3 respectively. Each of the support shaft portions 22,
22 is rotatably supported inside the circular holes 21, 21 via radial needle bearings 24, 24.
Further, the power rollers 8, 8 are rotatably supported around the pivot shafts 23, 23 via other radial needle bearings 25, 25.

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 shaft portions 23, 23 of these displacement shafts 7, 7 are eccentric with respect to the respective support shaft portions 22, 22 is in the same direction with respect to the rotation direction of the input side disk 2 (the left and right opposite direction in FIG. 6). ). The eccentric direction is a direction substantially orthogonal 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, based on a large load applied to each component in the state of transmission of the rotational force,
Even when the power rollers 8, 8 tend to be displaced in the axial direction of the input shaft 15 (the left-right direction in FIG. 5 and the front-back direction in FIG. 6) due to the elastic deformation of these constituent members, This displacement can be absorbed without applying excessive force to each part.

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 26, 26 and thrust bearings such as thrust needle bearings 27 and 27. The thrust ball bearings 26 support rotation of the power rollers 8 while supporting the load applied to the power rollers 8 in the thrust direction. The thrust bearings such as the thrust needle bearings 27 and 27 and the slide bearings support the thrust load applied from the power rollers 8 and 8 to the outer rings 28 and 28 that constitute the thrust ball bearings 26 and 26. The pivot shafts 23, 23 and the outer races 28, 28 are allowed to swing about the support shafts 22, 22.

Further, drive rods 29, 29 are connected to one end (left end in FIG. 6) of each of the trunnions 6, 6, and a drive piston 30, 30 are fixed. The drive pistons 30 are oil-tightly fitted in the drive cylinders 31, 31, 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 pressing device 9. Then, the rotation of the input side disk 2 is transmitted to the output side disk 4 via the pair of power rollers 8, 8, and further, the output side disk 4
Is taken out from the output gear 18. Input shaft 15
When changing the rotation speed ratio between the output gear 18 and
The pair of drive pistons 30, 30 are displaced in directions opposite to each other. The pair of trunnions 6, 6 are displaced in opposite directions with the displacement of the drive pistons 30, 30, respectively. For example, the lower power roller 8 in FIG. Are displaced to the left in FIG. As a result, each of these power rollers 8,
8 acts on the contact portions between the peripheral surfaces 8a, 8a and the inner side surfaces 2a, 4a of the input-side disk 2 and the output-side disk 4.
The direction of the tangential force changes. Then, with the change in the direction of the force, each of the trunnions 6 is moved to the supporting plate 2.
It swings in opposite directions about pivots 5, 5 pivotally supported by 0, 20. As a result, as shown in FIGS. 3 and 4 described above, the contact positions between the peripheral surfaces 8a, 8a of the power rollers 8, 8 and the inner surfaces 2a, 4a change, and the input shaft 15 The rotation speed ratio with the output gear 18 changes.

The input shaft 15 and the output gear 1 are
When transmitting the rotational force to the power rollers 8, the power rollers 8, 8 are displaced in the axial direction of the input shaft 15 based on the elastic deformation of the constituent members. Each of the displacement shafts 7 that pivotally support 8 rotates slightly about each of the support shaft portions 22. As a result of this rotation, the outer ring 2 of each of the thrust ball bearings 26, 26
The outer surfaces of the trunnions 6, 6 and the inner surfaces of the trunnions 6, 6 are relatively displaced. Since the thrust needle bearings 27 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.

In the case of a toroidal type continuously variable transmission constructed and operated as described above, a radial needle bearing 25 and a thrust ball bearing 26 for supporting the power rollers 8 and 8 are provided.
It is necessary to feed lubricating oil (traction oil) to each bearing part existing in the combination part of the trunnions 6, 6, the displacement shafts 7, 7, and the power rollers 8, 8. What is important is that the power rollers 8, 8 rotate at high speed while receiving a large load during operation of the toroidal type continuously variable transmission. Therefore, in order to ensure the durability of the radial needle bearing 25 and the thrust ball bearing 26, it is necessary to supply a sufficient amount of lubricating oil to each bearing portion including the bearings 25 and 26.

For this reason, in the case of the structure described in the microfilm of Japanese Utility Model Application No. 63-69293 (Japanese Utility Model Application Laid-Open No. 1-173552) shown in FIGS. Inside of one side and each drive rod 2
The oil supply holes 32a, 3
2b. And the drive rod 2 of these
Hydraulic oil present in each of the drive cylinders 31, 31 can be freely fed as lubricating oil from the low pressure chamber side of the drive cylinders 31, 31 into oil supply holes 32b, 32b provided on the sides 9 and 29. On the other hand, each of the trunnions 6,
The lubricating oil sent out from the downstream ends of the oil supply holes 32a provided on the 6 side can be discharged from the inner peripheral surfaces of the circular holes 21 and the inner surface of the middle portion of the trunnions 6, 6 respectively. During operation of the toroidal-type continuously variable transmission, the operating oil present on the low-pressure chamber side of each of the drive cylinders 31, 31 is filled with the inner peripheral surface of each of the circular holes 21, 21 and the inner surface of the intermediate portion of each of the trunnions 6, 6. From the two bearings 2
Lubricate each bearing section, including 5, 26. The structure and operation of this part are described in more detail in Japanese Utility Model Publication No. 4-48351.

[0016]

In the case of the conventional structure shown in FIG. 6, each trunnion 6, 6 such as a radial needle bearing 25 and a thrust ball bearing 26 for supporting the power rollers 8, 8 and each displacement. The outer ring 28 that constitutes the thrust ball bearing 26 is efficiently cooled only by considering that lubricating oil is supplied to each bearing portion existing in the combination portion of the shafts 7 and the power rollers 8. I do not consider doing. Therefore, during operation of the toroidal-type continuously variable transmission, the temperature of a part of the outer ring 28 significantly increases, and there is a possibility that the durability of the outer ring 28 may not always be sufficiently ensured. This reason will be described with reference to FIGS.

During operation of the toroidal-type continuously variable transmission, a large thrust load is applied to each of the power rollers 8 in a direction pressed against the inner surface of each of the trunnions 6. Then, based on the thrust load, each of the trunnions 6
However, it is elastically deformed in a direction in which the inner side surface becomes an arc-shaped concave surface. As a result, the balls 33, 3 constituting the thrust ball bearing 26 are formed.
3 and the contact pressure between the inner raceway 34 formed on the outer end surface of each power roller 8 and the outer raceway 35 formed on the inner side surface of each outer race 28 (see FIGS. 5 and 6). The thrust ball bearings 26 become uneven throughout the circumferential direction. Specifically, pivots 5, 5, 5 provided at both ends of each trunnion 6 are provided.
The contact pressure at the positions shown in FIG.
As shown in FIG. 8, the contact pressure at the position shown in FIG. 7 where the phase in the circumferential direction is shifted by 90 degrees is reduced as shown in FIG.

At the position shown in FIG. 7 where the contact pressure between the rolling surfaces of the balls 33, 33 and the inner raceway 34 and the outer raceway 35 increases for such a reason, the operation of the thrust ball bearing 26 is performed. The amount of generated heat increases. In particular, since each of the power rollers 8 rotates at a high speed during operation of the toroidal-type continuously variable transmission, the temperature of a part of each of the power rollers 8 does not particularly increase with the increase in the heat generation amount. In the case of each of the outer rings 28, there is a problem. That is, these outer wheels 28 hardly rotate even during operation of the toroidal type continuously variable transmission. Therefore, unless the cooling of each of these outer rings 28 is particularly taken into consideration, the temperature of each of these outer rings 28 at the above-mentioned position may significantly increase with the increase in the amount of generated heat. Then, at these positions, the outer raceway 35
When the temperature of a part of the outer ring raceway rises significantly, damage such as early peeling is likely to occur in the outer raceway 35 at each of these positions.

On the other hand, in the case of the conventional toroidal-type continuously variable transmission, as is apparent from FIG. 6, the downstream end opening of the oil supply hole 32a formed inside the trunnion 6 is
The outer ring 28 is provided at a portion closer to the inner diameter than the inner peripheral edge. Therefore, the outer raceway 35 cannot be efficiently cooled by the lubricating oil discharged from the oil supply hole 32a. The present invention has been made in view of the above-described circumstances, and has been described above.
Invented in order to realize a toroidal-type continuously variable transmission having excellent durability by efficiently cooling a part where the temperature tends to rise in a part of the transmission 5.

[0020]

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. First and second disks which are rotatably supported independently of each other, and about a pair of concentric axes which are respectively concentric with respect to the central axes of the first and second disks. A plurality of swinging trunnions, a plurality of displacement shafts provided at an intermediate portion of each of the trunnions so as to protrude from the inner surface of each of the trunnions, and a state in which the trunnions are rotatably supported around the respective displacement shafts. A plurality of power rollers sandwiched between the first and second disks, and a thrust ball bearing provided between an outer end surface of each of the power rollers and an inner surface of each of the trunnions; Each The downstream end provided in the anion and a oil supply passage is opened to the inner surface of the trunnions. In particular, in the toroidal type continuously variable transmission of the present invention, a portion of the inner surface of each of these trunnions that faces the pitch circle of each of the thrust ball bearings and faces an extension of the central axis of each of the pivots. The discharge port is provided with a discharge port that opens each downstream end. The upstream ends of these discharge holes are respectively connected to the oil supply passages.

[0021]

The toroidal-type continuously variable transmission of the present invention configured as described above has the same operation as the above-mentioned conventional toroidal-type continuously variable transmission, and operates between the first disk and the second disk. By transmitting the rotational force and changing the inclination angle of the trunnion, the rotational speed ratio between these two disks is changed. In particular, in the case of the toroidal type continuously variable transmission of the present invention, lubrication is performed on a part of the outer ring that constitutes a thrust ball bearing for rotatably supporting each power roller, where a load received from the ball is particularly large. The oil is discharged to cool this part efficiently. Therefore, it is possible to prevent the temperature of a part of the outer ring from being significantly increased, and to prevent the outer ring raceway formed on the outer ring from being damaged such as early peeling.

[0022]

1 and 2 show an embodiment of the present invention. A feature of the present invention lies in a structure for efficiently cooling a part of the outer ring 28 constituting the thrust ball bearing 26, particularly a part where the temperature rise is apt to be remarkable. Since the structure and operation of the other parts are the same as those of the conventional structure shown in FIGS. 5 and 6, overlapping illustration and description of equivalent parts are omitted or simplified.
Hereinafter, the description will focus on the characteristic portions of the present invention and the portions not described with reference to FIGS.

Oil supply passage 36 provided inside trunnion 6
Is formed by connecting a first oil supply hole 37 and a second oil supply hole 38 in series with each other in the flow direction of the lubricating oil. The first oil supply hole 37 is formed in the outer half (upper half of FIG. 1) of the trunnion 6 in parallel with the center axis of a pair of pivots 5 provided at both ends of the trunnion 6. The trunnion 6 is provided so as to penetrate a circular hole 21 provided at an intermediate portion thereof. Restriction plugs 39, 39 are fitted and fixed to both ends of the first lubrication hole 37 at both ends of the trunnion 6, respectively. Therefore, a part of the lubricating oil fed into the first oil supply hole 37 passes through a throttle hole formed at the center of each of the throttle plugs 39, 39, and the radial needle bearing that supports the pivots 5, 5. 40, 40 (see FIG. 6). On the other hand, the second oil supply hole 38 is connected to the pair of pivots 5,
5 (left side in FIGS. 1 and 2), a through hole 41 formed in the center of the pivot 5 is provided in a state of crossing the through hole 41, and one end (upper end in FIG. I'm communicating. Further, the other end of the second oil supply hole 38 has the through hole 41.
The opening on the opposite side of the first oil supply hole 37 with respect to
It is completely closed by the plug 42.

In the assembled state of the toroidal type continuously variable transmission, a hydraulic cylinder as an actuator for displacing the trunnion 6 in the axial direction of each of the pivots 5, 5 is formed inside the through hole 41. The distal end of the drive rod 29a is fitted inside. The tip of the drive rod 29a (the right end in FIGS. 1 and 2) and the end of the trunnion 6 are formed in a tubular shape having an oil supply hole for feeding lubricating oil therein. Are fixedly connected to each other by a connecting pin 43 inserted in the diametrical direction.
Further, the downstream end of the oil supply hole provided at the center of the drive rod 29a is closed by the connecting pin 43. In addition, a portion closer to the center of the tip of the drive rod 29a than the portion where the coupling pin 43 is inserted (leftward portion in FIGS. 1 and 2) is provided with an oil supply hole provided in the center of the drive rod 29a. A communication hole (not shown) for communicating with the second oil supply hole 38 is formed.

On the other hand, a concave groove 44 is formed on the inner peripheral surface of the circular hole 21 at a position matching with the first oil supply hole 37 over the entire circumference. Further, discharge holes 45 are provided at three positions between the inner side surface of the trunnion 6 and the first oil supply hole 37.
a, 45b and 46 are formed respectively. The discharge holes 4 at both ends of the discharge holes 45a, 45b, 46
The downstream ends of the shafts 5a and 45b are opposed to the pitch circle P of the thrust ball bearing 26 and extend along the extension line α of the central axis of each of the pivots 5 and 5 provided concentrically on both end surfaces of the trunnion 6. Each downstream end is opened at the opposing portion.

Therefore, the discharge holes 45a, 45 at both ends are provided.
The lubricating oil discharged from b is discharged to a part of the outer ring 28 constituting the thrust ball bearing 26, where the load received from the balls 33, 33 becomes particularly large, to efficiently cool this part. That is, the lubricating oil discharged from each of the discharge holes 45a and 45b is supplied to the thrust needle bearing 2 provided between the inner surface of the trunnion 6 and the outer surface of the outer ring 28.
7, the ball 33 on the outer surface of the outer ring 28,
It is poured into a portion where the load received from 33 becomes particularly large.
Then, the lubricating oil removes the heat of this portion and then flows to the surroundings. For this reason, it is possible to prevent the temperature of a part of the outer ring 28 from being significantly increased, and to prevent the outer ring track 35 formed on the outer ring 28 from being damaged such as early peeling.

In order to supply the lubricating oil for cooling the outer race 28 in this manner, the discharge holes 45a, 45a are formed in a part of the race plate 49 constituting the thrust needle bearing 27.
Through holes 50, 50 are provided in portions matching b. Although the rolling surfaces of the needles 51 constituting the thrust needle bearing 27 may abut the through holes 50, 50, the thrust needle bearing 27
Is for allowing a slight swing displacement of the outer ring 28, so that the rolling surfaces of the needles 51, 51 are not particularly damaged. Of course, the peripheral portions of the through holes 50 are subjected to processing such as deburring and chamfering to prevent an excessive edge load from being applied to the rolling surface.

On the other hand, the downstream end of the discharge hole 46 at the intermediate portion is connected to the inner end surface of the pivot shaft 23 constituting the displacement shaft 7 supported in the circular hole 21 and to the outer peripheral surface of the support shaft 22. It opens to the eccentric part. Another oil supply hole 47 is provided in the pivot shaft portion 23, and the downstream ends of the branch discharge holes 48 a and 48 b branched from the another oil supply hole 47 are formed on the outer peripheral surface of the pivot shaft portion 23 by The thrust ball bearing 26 or the radial needle bearing 25 is opened at a portion facing the inner diameter side.

During operation of the toroidal type continuously variable transmission, lubricating oil is fed into an oil supply hole provided at the center of the drive rod 29a by oil supply means such as an oil supply pump (not shown).
Then, the lubricating oil is sent to the first oil supply hole 37 via the second oil supply hole 38. As described above, the lubricating oil sent to the first oil supply hole 37 is supplied to each of the discharge holes 45a,
45b to cool a part of the outer ring 28,
From the discharge hole 46 to the oil supply hole 47 and the branch discharge hole 48
The bearings 25 and 26 are fed to the bearings including the radial needle bearing 25 and the thrust ball bearing 26 through a and 48b to lubricate the bearings 25 and 26.

[0030]

Since the present invention is constructed and operates as described above, a toroidal type continuously variable transmission having excellent durability can be realized.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view illustrating an example of an embodiment of the present invention in a state where a trunnion, a power roller, a thrust ball bearing, a drive rod end, and the like are taken out.

FIG. 2 is a view of the trunnion and the end of a drive rod taken out and viewed from below in FIG. 1;

FIG. 3 is a side view showing a basic configuration of a conventionally known toroidal-type continuously variable transmission in a state of maximum deceleration.

FIG. 4 is a side view showing a state at the time of maximum speed increase.

FIG. 5 is a sectional view showing an example of a conventional specific structure.

FIG. 6 is a sectional view taken along the line AA of FIG. 5;

FIG. 7 is a view for explaining a load applied to a thrust ball bearing.
FIG. 6 is a schematic view from above of FIG. 5.

FIG. 8 is a diagram showing a magnitude of a load applied to a ball constituting a thrust ball bearing.

[Explanation of symbols]

 Reference Signs List 1 input shaft 2 input side disk 2a inner surface 3 output shaft 4 output side disk 4a inner surface 5 pivot 6 trunnion 7 displacement shaft 8 power roller 8a peripheral surface 9 pressing device 10 cam plate 11 retainer 12 roller 13 drive side cam surface 14 Driven cam surface 15 Input shaft 16 Needle bearing 17 Collar 18 Output gear 19 Key 20 Support plate 21 Circular hole 22 Support shaft 23 Pivot shaft 24 Radial needle bearing 25 Radial needle bearing 26 Thrust ball bearing 27 Thrust needle bearing 28 Outer ring 29, 29a Drive rod 30 Drive piston 31 Drive cylinder 32a, 32b Oil supply hole 33 Ball 34 Inner ring raceway 35 Outer ring raceway 36 Oil supply passage 37 First oil supply hole 38 Second oil supply hole 39 Throttle plug 40 Radial needle bearing 41 Communication Hole 42 plug 43 connecting pin 44 Groove 45a, 45b discharge hole 46 discharge hole 47 oil supply hole 48a, 48b branched discharge hole 49 race plate 50 hole 51 needle

 ──────────────────────────────────────────────────続 き Continued on the front page F term (reference) 3J051 AA03 BA03 BD02 BE09 CA05 CB07 ED08 FA02 3J063 AA02 AB33 AC04 BA11 CA01 CB36 XD03 XD12 XD42 XD62 XD73 XE15

Claims (1)

[Claims] 1. In a state where the inner side surfaces are opposed to each other,
First and second discs rotatably supported concentrically and independently of each other, and a pair of concentric pairs each being twisted with respect to the center axis of the first and second discs; A plurality of trunnions swinging about a pivot, a plurality of displacement shafts provided at an intermediate portion of each of the trunnions so as to protrude from the inner surface of each of the trunnions, and rotatably supported around these respective displacement shafts In this state, a plurality of power rollers sandwiched between the first and second disks, and a thrust ball provided between an outer end surface of each of the power rollers and an inner surface of each of the trunnions. In a toroidal-type continuously variable transmission including a bearing and an oil supply passage provided inside each of the trunnions and having a downstream end opened to the inner surface of each of the trunnions, A portion of the side surface facing the pitch circle of each of the thrust ball bearings and a portion facing an extension of the central axis of each of the pivots is provided with discharge holes having respective downstream ends, and upstream of each of the discharge holes. A toroidal-type continuously variable transmission characterized in that ends thereof are respectively connected to the oil supply passage.