JP2001263442A - Troidal continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a reception side oil feed passage to allow the lubricating oil to lubricate a radial needle bearing and a thrust ball bearing at low cost, and to ensure the strength of a pivotable support shaft portion of a displacement shaft having the reception side oil feed passage 37. SOLUTION: The reception side oil feed passage 37 is formed in the axial direction of the pivotable shaft portion 22. A bottomed circular hole 39 is formed in a center portion of a power roller 8A, and the total amount of the lubricating oil discharged from the reception side oil feed passage 37 is allowed to flow though the radial needle bearing and the thrust ball bearing 25, 26.

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 As a transmission unit of an automobile transmission,
The use of a toroidal-type continuously variable transmission as schematically illustrated in FIGS. 4 and 5 has been studied and has been partially implemented. This toroidal type continuously variable transmission supports an input side disk (first disk) 2 concentrically with an input shaft 1 as disclosed in, for example, Japanese Utility Model Laid-Open Publication No. Sho 62-71465. An output disk (second disk) 4 is fixed to an end of the output shaft 3 which is arranged concentrically with the output shaft. Inside the casing containing the toroidal-type continuously variable transmission, trunnions 6 and 6 that swing about pivots 5 and 5 that are twisted with respect to the input shaft 1 and the output shaft 3 are provided. .

That is, each of the trunnions 6, 6 has the above-mentioned pivots 5, 5 on the outer surfaces of both ends thereof, concentrically with each other, as shown in FIGS.
It is provided in the front and back direction. In addition, the trunnions 6, 6 support the base ends of the displacement shafts 7, 7 at the center thereof.
By swinging the trunnions 6 around the center 5, the tilt angles of the displacement shafts 7 can be adjusted freely. Power rollers 8, 8 are rotatably supported around displacement shafts 7, 7 supported by the trunnions 6, 6, respectively. The power rollers 8, 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
It has a concave surface obtained by rotating an arc around the pivot 5 or a curve close to such an arc. The peripheral surfaces 8a, 8a of the power rollers 8, 8 formed on the spherical convex surfaces are in contact with the inner side surfaces 2a, 4a.

[0005] 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 the pressing device 9. 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 of (for example, four) rollers 1 held by a holder 11.
2 and 12. On one side surface (left side surface in FIGS. 4 and 5) of the cam plate 10, a cam surface 13 which is an uneven surface extending in the circumferential direction is formed, and an outer side surface of the input side disk 2 (right side in FIGS. 4 and 5). Surface) also has a similar cam surface 14 formed thereon. Then, the plurality of rollers 12, 12 are
The input shaft 1 is rotatably supported about a radial axis with respect to the center of the input shaft 1.

When the cam plate 10 rotates with the rotation of the input shaft 1 when the toroidal-type continuously variable transmission having the above-described structure is used, a plurality of rollers 12, 12
Is pressed against the cam surface 14 on the outer surface of the input side 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 pressing of the pair of cam surfaces 13, 14 and the plurality of rollers 12, 12, The input 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. First, when deceleration between the input shaft 1 and the output shaft 3 is performed, the pivots 5 and 5 are centered. The trunnions 6 are swung so that the peripheral surfaces 8a of the power rollers 8 are close to the center of the inner surface 2a of the input disk 2 and the inner surface of the output disk 4 as shown in FIG. 4a
The respective displacement shafts 7, 7 are tilted so as to abut against the outer peripheral portions of the respective shafts.

On the other hand, when increasing the speed, the trunnions 6, 6 are swung about the pivots 5, 5, and the peripheral surfaces 8a, 8a of the power rollers 8, 8 are shown in FIG. As described above, a portion near the outer periphery of the inner surface 2a of the input disk 2 and a portion near the center of the inner surface 4a of the output disk 4
The respective displacement shafts 7, 7 are inclined so as to abut each other.
If the inclination angle of each of the displacement shafts 7, 7 is set between those in FIGS. 4 and 5, an intermediate speed ratio can be obtained between the input shaft 1 and the output shaft 3.

FIGS. 6 and 7 show Japanese Utility Model Application No. 63-6929.
3 shows a more specific toroidal-type continuously variable transmission described in Microfilm No. 3 (Japanese Utility Model Laid-Open No. 1-173552). Input disk 2 and output disk 4
Is rotatably supported around a cylindrical input shaft 15 via needle bearings 16 and 16, respectively. Further, the cam plate 10 is spline-engaged with the outer peripheral surface of the end portion (the left end portion in FIG. 6) of the input shaft 15, and is prevented from moving away from the input side disk 2 by the flange portion 17. The cam plate 10 and the rollers 12 are used to rotate the input side disk 2 based on the rotation of the input shaft 15.
The loading cam-type pressing device 9 is configured to rotate while pressing against the output side disk 4. An output gear 18 is connected to the output disk 4 by keys 19, 19 so that the output disk 4 and the output gear 18 rotate in synchronization.

Both ends of the pair of trunnions 6, 6 are supported by a pair of support plates 20, 20 so as to be swingable and displaceable in the axial direction (front and back directions in FIG. 6, and left and right directions in FIG. 7). . A circular hole 2 formed in the middle of each of the trunnions 6
The displacement shafts 7, 7 are supported on the portions 3, 23. Each of the displacement shafts 7 has a support shaft 21 and a pivot shaft 22, 22 which are parallel and eccentric to each other. Each of the support shaft portions 21 is inserted into each of the circular holes 2.
It is rotatably supported inside 3, 3 via radial needle bearings 24, 24. Further, the power rollers 8, 8 are rotatably supported around the respective pivot shaft portions 22, 22 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 22, 22 of the respective displacement shafts 7, 7 are eccentric with respect to the respective support shaft portions 21, 21 is the same as the rotation direction of the input side and output side disks 2, 4. (The left and right directions are opposite in FIG. 7). The eccentric direction is a direction substantially orthogonal to the direction in which the input shaft 15 is provided. Therefore, the power rollers 8 are supported to be slightly displaceable in the direction in which the input shaft 15 is disposed. As a result, even when the power rollers 8 are displaced in the axial direction of the input shaft 15 (the left-right direction in FIG. 6 and the front and back directions in FIG. 7) due to the elastic deformation of each component, etc. 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, the power rollers 8, 8 are sequentially arranged from the outer surface of the power rollers 8, 8. Thrust ball bearings 26, 26, which are thrust rolling bearings, for supporting the thrust load applied to the shaft 8, and thrust needle bearings 27, 27, which are other thrust bearings, are provided. Of these, thrust ball bearings 26, 26
Is to allow the rotation of the power rollers 8 while supporting the load in the thrust direction applied to the power rollers 8. Further, the thrust needle bearings 27, 27 support the thrust load applied from the power rollers 8, 8 to the outer races 28, 28 constituting the thrust ball bearings 27, 27, while supporting the pivot shaft portion 22, 2
2 and each of these outer rings 28, 28
Swinging around 21 is allowed.

Further, drive rods 29, 29 are respectively connected to one end (the left end in FIG. 7) of each of the trunnions 6, 6, and a drive piston 30, 30 are fixed. These drive pistons 30, 30 are fitted in drive cylinders 46, 46, respectively, in an oil-tight manner.

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 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 the rotation of the output side disk 4 is taken out from the output gear 18.

When changing the rotational speed ratio between the input shaft 15 and the output gear 18, the pair of drive pistons 30,
30 are displaced in opposite directions. With the displacement of each of the drive pistons 30, 30, the pair of trunnions 6,
6 are displaced in the opposite directions, for example, the lower power roller 8 in FIG. 7 is displaced to the right in FIG. 7 and the upper power roller 8 in FIG. 7 is displaced to the left in FIG. As a result, the peripheral surfaces 8a, 8a of the power rollers 8, 8 and the inner surfaces 2a, 4a of the input side disk 2 and the output side disk 4 are formed.
The direction of the tangential force acting on the abutting portion changes. Then, with the change in the direction of the force, each of the trunnions 6, 6 is pivotally supported by the support plates 20, 20,
5 oscillate in mutually opposite directions. As a result,
As shown in FIGS. 4 and 5 described above, each of the power rollers 8,
The contact position between the peripheral surfaces 8a, 8a of the base 8 and the inner surfaces 2a, 4a changes, and the rotational speed ratio between the input shaft 15 and the output gear 18 changes.

In the case of the toroidal type continuously variable transmission configured and operated as described above, it is necessary to feed lubricating oil to the radial needle bearing 25 and the thrust ball bearing 26 for supporting 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 (traction oil) to the bearings 25 and 26.

Conventionally, as a structure for feeding such a lubricating oil, a lubricating oil supply device as described in, for example, Japanese Utility Model Application Laid-Open No. 62-156658 and Japanese Patent Application Laid-Open No. 8-291850 has been known. . As shown in FIG. 8, the lubricating oil supply device according to the related art forms a feed-side oil supply passage 31 inside the trunnion 6 and has oil supply holes 32, 32 formed in an outer ring 28 constituting a thrust ball bearing 26. It is formed so that lubricating oil can be fed into the thrust ball bearing 26. Further, the radial needle bearing 25 is provided inside the pivot shaft portion 22 constituting the first half of the displacement shaft 7.
Lubricating oil is fed through the receiving-side oil supply passage 33 which is the oil supply passage described in the claims. The upstream end of the receiving-side oil supply passage 33 is open to a part of the base end face 34 of the pivot shaft part 22 that is separated from the support shaft part 21.

During operation of the toroidal type continuously variable transmission, lubricating oil is fed into the feed-side oil supply passage 31 by the action of a pump (not shown) incorporated in the transmission. Then, the lubricating oil flows out of the downstream end opening of the feed-side oil supply passage 31 into a gap space between the outer surface of the outer ring 28 and the inner surface of the trunnion 6 that constitute the thrust ball bearing 26. Further, the lubricating oil is supplied to the oil supply hole 32,
32, to the thrust ball bearing 26, to the radial needle bearing 25 through the receiving side oil supply passage 33,
Each is fed to lubricate both bearings 26 and 25.

[0019]

In the case of the conventional toroidal-type continuously variable transmission constructed and operated as described above, the processing of the receiving-side lubricating oil passage 33 is troublesome and costly. It becomes difficult to ensure the durability of the pivot shaft portion 22 in which the path 33 is provided. That is, the receiving side passage 3
3 is a main passage 35 provided only in the base end surface 34 side, provided in the axial direction of the pivot shaft portion 22 (vertical direction in FIG. 8).
And a plurality of branch passages 36, 36 for communicating the main passage 35 with the outer peripheral surface of the pivot shaft portion 22, so that the machining operation is troublesome. In particular, the main passage 35 is
It is formed in a portion of the pivot shaft portion 22 that is hard to receive a large load and that is off the center. In addition, each of the branch flow paths 3
Parts 6 and 36 are also difficult to receive large loads (non-load area)
Must be formed. Therefore, each of the branch flow paths 36,
36 cannot be formed in the diameter direction of the cross section of the pivot shaft portion 22 in many cases. In such a case, the drill blade for forming the branch flow paths 36, 36 cannot be abutted in a direction perpendicular to the tangential direction of the outer peripheral surface of the pivot shaft portion 22, The operation of forming the branch flow paths 36, 36 is complicated.

Further, it is troublesome to remove burrs generated during the processing, and the cost is increased. That is, when the burrs generated during the processing using a cutting machine such as a drilling machine are left, the burrs separated during use are separated from the inner surfaces 2a, 4a of the input and output disks 2, 4 and the power rollers 8, 8, peripheral surface 8a,
8a, and enters each of the surfaces 2a, 4a
a, 8a may be damaged. For this reason, it is necessary to remove burrs generated by the above processing, but it is troublesome to remove burrs generated at a branch portion between the main passage 35 and each of the branch passages 36, 36. Become. In addition, burrs are likely to occur at a portion where two holes intersect as in each of these branch portions, so that such a problem becomes conspicuous.

During operation of the toroidal type continuously variable transmission, the pivot shaft 22 is provided with the peripheral surface 8a of the power roller 8 supported by the pivot shaft 22 and the input side and output side disks 2. A large force in the rotational direction of each of the disks 2 and 4 is applied along with the friction between the inner surfaces 2a and 4a. Then, a large bending stress is applied to the pivot shaft portion 22 based on this force. If the branch passages 36, 36, which are holes perpendicular to the central axis of the pivot shaft 22, exist in the pivot shaft 22, the branch passages 36,
Stress concentrates on the 36 portion. For this reason, in the case of a toroidal-type continuously variable transmission that transmits a large torque, the branch passages 36, 36 must be provided unless the diameter of the pivot shaft portion 22 is increased.
Since there is a possibility that damage such as cracks may occur in the portion, it is difficult to reduce the size and weight. The toroidal-type continuously variable transmission of the present invention has been invented in view of such circumstances.

[0022]

A toroidal-type continuously variable transmission according to the present invention comprises a first and a second disk, a plurality of trunnions, and a plurality of , A plurality of power rollers, a plurality of thrust rolling bearings, a plurality of different thrust bearings, and an oil supply passage. The first and second disks are concentrically and rotatably supported with their inner surfaces facing each other. Each of the trunnions swings about a pivot axis which is twisted with respect to the central axes of the first and second disks. Each of the displacement shafts is composed of a support shaft portion and a pivot shaft portion that are eccentric to each other. The support shaft portion is rotatably supported by the trunnion, and the pivot shaft portion protrudes from the inner surface of the trunnion. Let me. Each of the above power rollers is
It is sandwiched between the first and second discs while being rotatably supported via a radial needle bearing around the pivot shaft portion. Each of the thrust rolling bearings is attached to an outer end surface of each of the power rollers to support a thrust load applied to each of the power rollers. or,
Each of the different thrust bearings is provided between an outer surface of a thrust bearing ring constituting each of the thrust rolling bearings and an inner surface of each of the trunnions, and a thrust direction applied from the power rollers to the respective thrust bearing rings. , While displacing each of the thrust bearing rings with respect to each of the trunnions. Further, the oil supply passage is provided inside the pivot shaft portion of each of the displacement shafts, and an upstream end thereof is opened to a base end surface of the pivot shaft portion. In particular, in the toroidal type continuously variable transmission of the present invention, each of the oil supply passages is provided inside the pivot shaft portion from the base end face of the pivot shaft portion to the distal end side of the pivot shaft portion. It is constituted by one linear oil supply hole formed in the above manner.

[0023]

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, the oil supply passage provided inside the pivot shaft portion is formed by a single oil passage formed from the base end face of the pivot shaft portion toward the distal end side. , The oil supply passage can be easily processed and the cost can be reduced, and the durability of the pivot shaft portion in which the oil supply passage is provided is ensured. Things become easier. Furthermore, the generation of burrs is small, and the generated burrs are easily removed.

[0025]

FIG. 1 shows a first example of an embodiment of the present invention corresponding to claims 1 and 2. The features of this example are that the structure of the receiving side oil supply passage 37 which is an oil supply passage provided inside the pivot shaft portion 22 constituting the displacement shaft 7 and the lubricating oil sent through the receiving side oil supply passage 37 are
Radial needle bearing 25 supporting power roller 8A
It is in the structure of the part that feeds efficiently to Since the structure and operation of the other parts are the same as those of the above-described conventional structure, the overlapping description will be omitted or simplified, and the following description will focus on features of the present invention.

A receiving-side oil supply passage 37 corresponding to the oil supply passage described in the claims is provided inside the pivot shaft portion 22 which constitutes the first half of the displacement shaft 7 for pivotally supporting the power roller 8A. Is provided. The receiving-side oil supply passage 37 is formed in the axial direction of the pivot shaft portion 22 (vertical direction in FIG. 1), and has an upstream end (upper end in FIG. 1) of the base end surface 34 of the pivot shaft portion 22. The downstream end (the lower end in FIG. 1) is opened to the distal end surface 38 of the pivot shaft portion 22.

A bottomed circular hole 39 is formed at the center of the power roller 8A, and is opened only on the outer end surface (the surface facing the inner surface of the trunnion 6 and the upper surface in FIG. 1) of the power roller 8A. It is formed in a state where it does. Such a circular hole 39 is
A pivot shaft portion 22 and a radial needle bearing 25 for supporting the power roller 8A can be freely inserted therein. In the center of the bottom surface 40 of the circular hole 39, a concave portion 41 is provided.
Is formed, and the bottom surface 40 and the distal end surface 3 of the pivot shaft portion 22 are formed.
8 are not in close contact with each other, and a refueling gap 42 is formed between the two surfaces 40 and 38.

During operation of the toroidal type continuously variable transmission of the present embodiment, which incorporates the displacement shaft 7 having the receiving-side oil supply passage 37 as described above and the power roller 8A having the circular hole 39 as described above, The lubricating oil supplied through the supply-side oil supply passage 31 provided in the inside 6 flows into the reception-side oil supply passage 37 from the upstream end of the reception-side oil supply passage 37. Then, the lubricating oil flowing in the receiving-side oil supply passage 37 enters the oil supply gap 42 from the downstream end opening of the receiving-side oil supply passage 37.

The lubricating oil that has entered the oil supply gap 42 in this manner directs the oil supply gap 42 toward the opening of the circular hole 39 provided at the back end (bottom) of the lubricating oil in the radial needle bearing 25. It flows while passing through the gap. Further, the lubricating oil flowing out of the circular hole 39 flows radially outward of the power roller 8A through a gap of the thrust ball bearing 26. As described above, in the case of the present embodiment, the receiving-side oil supply passage 37 is used.
Of the lubricating oil flowing out from the downstream end opening of the radial needle bearing 25 and the thrust ball bearing 2
Flow through 6. Therefore, the flow rate of the lubricating oil for lubricating these bearings 25, 26 is ensured, and
26 can have good lubricity.

In the case of this embodiment, the receiving side oil supply passage 37 extends from the base end surface 34 of the pivot shaft portion 22 to the front end surface 38.
And in the axial direction of the pivot shaft portion 22 (in the direction perpendicular to the base end face 34 and the tip end face 38). For this reason, the processing of the receiving side oil supply passage 37 is easy, and the cost can be reduced. That is, the operation of forming the receiving side oil supply passage 37 can be easily performed by abutting the drill blade at right angles to the base end surface 34 (or the distal end surface 38). In addition, the point where burrs are generated due to the processing is generated at the tip surface 38.
(Or the base end face 34), and since the burrs are present at locations exposed to the outside, the removal operation is easy. Accordingly, the operation of forming the receiving-side oil supply passage 37 itself and the removal of burrs caused by the formation operation are easy, and the cost can be reduced.

In addition, since the receiving side oil supply passage 37 is formed in the axial direction of the pivot shaft portion 22, bending stress acts on the pivot shaft portion 22 during operation of the toroidal type continuously variable transmission. Even in this case, the degree of stress concentration generated in the receiving side oil supply passage 37 is small. In other words, since there is no radial hole as in the above-described conventional structure, a large stress concentration does not occur due to bending stress. Therefore, it is easy to ensure the durability of the displacement shaft 7 including the pivot shaft portion 22 without particularly increasing the diameter of the pivot shaft portion 22. In addition, since the generated stress is reduced, it is possible to further reduce the weight of the displacement shaft 7 by reducing the thickness of the displacement shaft 7, thereby realizing a toroidal type continuously variable transmission having a small size and light weight and sufficient durability. Can be achieved.

Next, FIG. 2 shows a second embodiment of the present invention, which also corresponds to the first and second aspects of the present invention. In the case of the present example, a large diameter portion is provided at a part of the base end surface 34 of the pivot shaft portion 22 constituting the displacement shaft 7 at the upstream end opening of the receiving side oil supply passage 37 formed in the pivot shaft portion 22. A part 43 is formed. The large-diameter portion 43 faces the downstream end opening of the feed-side oil supply passage 31 (see FIG. 1) provided in the trunnion 6, and receives the lubricating oil discharged from the feed-side oil supply passage 31 on the receiving side. The oil supply passage 37 can be efficiently taken in. Other configurations and operations are the same as those of the above-described first example.

Next, FIG. 3 corresponds to claims 1 and 3.
13 shows a third example of the embodiment of the present invention. In the case of this example, the displacement shaft 7 is provided at the center of the power roller 8 and inside thereof.
Pivot shaft portion 22 and radial needle bearing 25
The power roller 8 is formed in a state where it is open at both axial end surfaces (upper and lower surfaces in FIG. 3). A receiving-side oil supply passage 37a, which is an oil supply passage described in the claims, is formed inside the pivot bearing 22 in a state where it is slightly inclined with respect to the center axis of the pivot shaft portion 22.
Both ends of the receiving side oil supply passage 37a are opened to the base end surface 34 of the pivot shaft portion 22 and the outer peripheral surface of the distal end portion of the pivot shaft portion 22. Further, a retaining ring 45 is engaged with a portion of the distal end of the pivot shaft portion 22 protruding from the outer end surface (the lower end surface in FIG. 3) of the power roller 8 to prevent the power roller 8 from coming off. ing. At the same time, this retaining ring 45
Are almost closed at the outer end side of the space in which the radial needle bearing 25 is installed.

During operation of the toroidal type continuously variable transmission of the present embodiment, which incorporates the displacement shaft 7 having the above-described receiving-side oil supply passage 37a and the power roller 8 having the above-described circular hole 44, the trunnion is operated. The lubricating oil fed through the feed-side oil supply passage 31 provided in the inside 6 receives the lubricating oil from the upstream end of the receive-side oil supply passage 37a.
flows into a. Then, the lubricating oil flowing in the receiving side oil supply passage 37a is discharged from the downstream end opening of the receiving side oil supply passage 37a to the inner diameter side of the radial needle bearing 25.

In this way, the radial needle bearing 2
The lubricating oil discharged into 5 flows toward the opening of the circular hole 44 located on the inner end face side of the power roller 8 while passing through the gap in the radial needle bearing 25. That is, since the opening on the outer end surface side of the power roller 8 among the openings at both ends of the circular hole 44 is almost closed by the retaining ring 45, the opening inside the circular hole 44 from the receiving side oil supply passage 37 a is formed. Almost the entire amount of the lubricating oil discharged to the inside flows through the circular hole 44 over the entire length of the radial needle bearing 25 in the axial direction, and flows out to the inner end face side of the power roller 8. Further, the lubricating oil flowing out of the circular hole 44 flows through the gap of the thrust ball bearing 26 in the radial direction of the power roller 8. Thus, in the case of the present example, the lubricating oil flowing out from the downstream end opening of the receiving side oil supply passage 37a is
Almost all of it flows through the radial needle bearing 25 and the thrust ball bearing 26. Therefore, the flow rate of the lubricating oil for lubricating these bearings 25 and 26 is secured,
The lubricity of these bearings 25 and 26 can be improved.

In the case of this embodiment, the receiving side oil supply passage 37a extends from the base end surface 34 of the pivot shaft portion 22 to the outer peripheral surface of the distal end portion thereof in a direction close to the axial direction of the pivot shaft portion 22. Is formed. Therefore, the processing of the receiving side oil supply passage 37a is easy, and the cost can be reduced. That is, the operation of forming the receiving side oil supply passage 37a can be easily performed by abutting the drill blade against the base end surface 34 at a large angle. Moreover, there is only one location where burrs are generated due to the processing, and only one location on the outer peripheral surface of the tip portion, and since the burrs are present at locations exposed to the outside, the removal operation is easy. Therefore, the operation of forming the receiving-side oil supply passage 37a itself is easy to remove the burrs that accompany the formation operation, and the cost can be reduced.

Further, since the receiving side oil supply passage 37a is formed in a direction close to the axial direction of the pivot shaft portion 22,
Even when a bending stress is applied to the pivot shaft portion 22 during operation of the toroidal type continuously variable transmission, the receiving side oil supply passage 37
The degree of stress concentration occurring in the portion a is small. In the case of the present example, the downstream end opening of the receiving side oil supply passage 37a is open to a portion that becomes the inner raceway of the radial needle bearing 25. Therefore, in order to prevent the presence of this opening from causing an edge load to be applied to the rolling surface of the needle constituting the radial needle bearing 25,
As shown in FIG. 3, it is necessary to consider disposing the opening in the non-load zone of the radial needle bearing 25.

That is, during operation of the toroidal type continuously variable transmission, the power rollers 8 supported by the radial needle bearings 25 are provided on the inner side surfaces 2a, 4a of the input side and output side disks 2, 4 (see FIGS. 4 to 6). ) Are strongly clamped between each other and slightly elastically deform. The circular hole 44 has a short diameter in the axial direction (the front and back direction in FIG. 3) of the discs 2 and 4 and a direction perpendicular thereto (the right and left in FIG. 3). Direction) is an ellipse whose major axis is the major axis.
In the radial needle bearing 25, a side corresponding to the short diameter is a load zone, and a side corresponding to the long diameter is a non-load zone. Therefore, when implementing the structure of the present example, the downstream end opening of the receiving side oil supply passage 37a is arranged in the non-load zone as shown in FIG. 3 to prevent the occurrence of the edge load. Also, when the structure of the present embodiment is implemented, as shown in FIG. 3, the upstream end opening of the receiving side oil supply passage 37a is aligned with the downstream end opening of the feed side oil supply passage 31 on the trunnion 6 side. Preferably, by providing a large-diameter portion 43 as shown in FIG.
1 is supplied to the receiving side oil supply passage 27a.
So that it can be imported efficiently.

[0039]

Since the present invention is constructed and operates as described above, a toroidal type continuously variable transmission having a light weight and sufficient durability can be realized at low cost.

[Brief description of the drawings]

FIG. 1 is an essential part cross-sectional view showing a first example of an embodiment of the present invention.

FIG. 2 is a sectional view showing the second example and corresponding to a portion A in FIG. 1;

FIG. 3 is a sectional view of a main part showing the third example.

FIG. 4 is a side view showing a basic configuration of a conventionally known toroidal type continuously variable transmission in a state of maximum deceleration.

FIG. 5 is a side view showing a state at the time of maximum speed increase.

FIG. 6 is a sectional view showing an example of a conventional specific structure.

FIG. 7 is a sectional view taken along line BB of FIG. 6;

FIG. 8 is an essential part cross-sectional view showing a conventional structure provided with an oil supply passage.

[Explanation of symbols]

 Reference Signs List 1 input shaft 2 input side disk (first disk) 2a inner surface 3 output shaft 4 output side disk (second disk) 4a inner surface 5 pivot 6 trunnion 7 displacement shaft 8, 8A power roller 8a peripheral surface 9 pressing device Reference Signs List 10 cam plate 11 retainer 12 roller 13, 14 cam surface 15 input shaft 16 needle bearing 17 flange 18 output gear 19 key 20 support plate 21 support shaft 22 pivot shaft 23 circular hole 24, 25 radial needle bearing 26 thrust Ball bearing 27 Thrust needle bearing 28 Outer ring 29 Drive rod 30 Drive piston 31 Feed-side oil supply passage 32 Oil supply hole 33 Receiving-side oil supply passage 34 Base end surface 35 Main passage 36 Branch passage 37, 37a Receiving-side oil supply passage 38 Tip surface 39 Circular hole 40 Bottom 41 Recess 42 Refueling gap 43 Large diameter part 44 Circular hole 45 Retaining ring 4 The drive cylinder

 ──────────────────────────────────────────────────続 き Continued on the front page F term (reference) 3J051 AA04 BA02 BA03 BB06 BD02 BE09 CA05 CB06 EC03 ED08 FA02 3J063 AB33 AC03 BA01 BA11 BB48 CB36 CD02 CD06 XA37 XD03 XD14 XD43 XD73 XE15 3J101 AA01 CA08 CA21 FA31 FA44 GA

Claims (3)

[Claims] 1. In a state where the inner side surfaces are opposed to each other,
First and second discs concentrically and rotatably supported, and a plurality of trunnions each swinging about a pivot that is twisted with respect to the center axis of the first and second discs And a plurality of shafts each of which comprises a support shaft portion and a pivot shaft portion which are eccentric to each other, the support shaft portion of which is rotatably supported by the trunnion, and the pivot shaft portion protrudes from the inner surface of the trunnion. And a plurality of power rollers sandwiched between the first and second disks in a state where each is rotatably supported via a radial needle bearing around the pivot shaft portion. And a plurality of thrust rolling bearings attached to the outer end surfaces of the power rollers to support the thrust load applied to the power rollers and to allow the rotation of the power rollers. And between the outer surface of the thrust bearing ring constituting the rolling bearing and the inner surface of each of the trunnions, while supporting a load in the thrust direction applied to each of the thrust bearing rings from each of the power rollers, And a plurality of other thrust bearings that allow displacement of each of the thrust bearing rings with respect to the above, and are provided inside the pivot shaft portion of each of the displacement shafts, and the upstream end thereof is opened to the base end surface of the pivot shaft portion. In the toroidal-type continuously variable transmission provided with the refueling passage, the refueling passage is provided inside the pivot shaft portion from the base end face of the pivot shaft portion to the distal end side of the pivot shaft portion. A toroidal-type continuously variable transmission characterized by being constituted by one linear oil supply hole formed so as to face. 2. A central hole of a power roller having a bottomed circular hole into which a pivot shaft and a radial needle bearing can be inserted so as to open only on the outer end face side of the power roller. The toroidal-type continuously variable transmission according to claim 1, wherein a downstream end of the oil supply hole is opened at a tip end surface of the pivot shaft portion. 3. A center hole of the power roller, a circular hole into which a pivot shaft and a radial needle bearing can be inserted.
2. The toroidal-type continuously variable transmission according to claim 1, wherein the power roller is formed so as to be open at both axial end surfaces thereof, and the downstream end of the oil supply hole is opened at the outer peripheral surface of the distal end portion of the pivot shaft portion.