JP2000291756A - Toroidal type continuously variable transmission - Google Patents

Abstract

(57) [Summary] [PROBLEMS] To realize a compact, lightweight and high-performance structure. SOLUTION: First pivots 29, 29 provided at both ends of first trunnions 27, 27 are supported by support holes 31, 31 provided in yokes 54, 55 fixed to the inner surface of a casing 5. These support portions are provided with ball splines 56, 56 and radial needle bearings 57, 57, respectively. The loads applied to the first trunnions 27 during operation cancel each other in the yokes 54 and 55. or,
The axial displacement and oscillating displacement of each of the first trunnions 27, 27 correspond to the above-mentioned ball splines 56, 56.
And the radial needle bearings 57, 57 allow smooth operation.

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. This toroidal-type continuously variable transmission is disclosed in, for example, Japanese Utility Model Laid-Open No. 62-71465.
An input disk 2 is supported concentrically with the input shaft 1, and an output disk 4 is fixed to an end of an output shaft 3 arranged concentrically with the input shaft 1. Inside the casing 5 (FIGS. 15 to 17 to be described later) containing the toroidal type continuously variable transmission, it swings around the pivots 6, 6 which are twisted with respect to the input shaft 1 and the output shaft 3. Trunnions 7 and 7 are provided.

That is, each of the trunnions 7, 7 has the above-mentioned pivots 6, 6 concentrically provided on the outer surfaces of both ends. Therefore, these pivots 6, 6 do not intersect with the central axes of the discs 2, 4, but are provided at right angles to the direction of the central axes. At the center of these trunnions 7, 7, the base ends of the displacement shafts 8, 8 are supported, and the trunnions 7, 8 around the pivots 6, 6 are centered.
The tilt angle of each of the displacement shafts 8, 8 can be freely adjusted by swinging the shaft 7. Power rollers 9, 9 are rotatably supported around displacement shafts 8, 8 supported by the trunnions 7, 7, respectively. These power rollers 9, 9 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 obtained by rotating an arc centered on the pivot 6 about the input shaft 1 and the output shaft 3. It has a concave surface. Then, the peripheral surfaces 9a, 9a of the power rollers 9, 9, which are formed as spherical convex surfaces, are brought into contact with the inner side surfaces 2a, 4a.

[0004] A loading device 10 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 10 so as to be elastic. It can be pressed freely. The pressing device 10 includes a cam plate 11 that rotates together with the input shaft 1,
It is composed of a plurality of (for example, four) rollers 13, 13 held by a holder 12. On one side surface (the left side surface in FIGS. 13 and 14) of the cam plate 11, a cam surface 14 which is an uneven surface extending in the circumferential direction is formed.
A similar cam surface 15 is also formed on the outer side surface (the right side surface in FIGS. 13 and 14). And the plurality of rollers 1
3 and 13 are supported rotatably about an axis in a radial direction with respect to the center of the input shaft 1.

When the cam plate 11 rotates with the rotation of the input shaft 1 during use of the toroidal type continuously variable transmission configured as described above, a plurality of rollers 13
Is pressed against a cam surface 15 formed on the outer surface of the input side disk 2. As a result, at the same time that the input side disk 2 is pressed by the power rollers 9, 9, based on the pressing of the pair of cam surfaces 14, 15 and the rollers 13, 13, 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 9, 9, and the output shaft 3 fixed to the output side disk 4 rotates.

In the case where the rotational speed ratio (speed change ratio) between the input shaft 1 and the output shaft 3 is changed, and when the deceleration is first performed between the input shaft 1 and the output shaft 3, each of the pivots 6 The trunnions 7, 7 are swung in a predetermined direction as a center, so that the peripheral surfaces 9a, 9a of the power rollers 9, 9 are located near the center of the inner surface 2a of the input side disk 2 as shown in FIG. The displacement shafts 8 are inclined so as to abut against the outer peripheral portion of the inner surface 4a of the output side disk 4, respectively. Conversely, when increasing the speed, the trunnions 7, 7 are swung in opposite directions about the respective pivots 6, 6,
As shown in FIG. 14, the peripheral surfaces 9a, 9a of the power rollers 9, 9 are respectively disposed on the inner surface 2a of the input disk 2 near the outer periphery and the inner surface 4a of the output disk 4 near the center. The displacement shafts 8, 8 are tilted so as to be in contact with each other. If the inclination angles of the displacement shafts 8 and 8 are set between those in FIGS. 13 and 14, an intermediate speed ratio can be obtained between the input shaft 1 and the output shaft 3.

When an actual automobile transmission is constituted by the toroidal-type continuously variable transmission as described above, the input disk 2, the output disk 4, and the power rollers 9, 9 are connected to each other.
A so-called double-cavity toroidal-type continuously variable transmission in which two sets of the input-side disc 2, the output-side disc 4, and the power rollers 9, 9 are arranged in parallel to each other in the power transmission direction is also provided. Has been widely known.
FIGS. 15 to 17 show a type of such a double-cavity toroidal-type continuously variable transmission which is described in Japanese Patent Publication No. H8-23386 and is conventionally known.

An input shaft 1a is supported inside the casing 5 so as to be rotatable only. A circular transmission shaft 16 is supported around the input shaft 1a concentrically with the input shaft 1a and freely rotates relative to the input shaft 1a. In the portion of the transmission shaft 16 near both ends of the intermediate portion,
The first and second input side disks 17 and 18 corresponding to the first and second outer disks described in claim 2, respectively, with the ball splines 19 and 18 facing each other with the inner surfaces 2a and 2a facing each other. Support via 19. Therefore,
The first and second input side disks 17 and 18 are rotatably supported inside the casing 5 concentrically and synchronously with each other.

Around the intermediate portion of the transmission shaft 16,
The first and second output disks 20, 21 corresponding to the first and second inner disks described in claim 2,
Support via 2. The sleeve 22 has an output gear 23 integrally provided on the outer peripheral surface of the intermediate portion, has an inner diameter larger than the outer diameter of the transmission shaft 16, and has a pair of support walls 24 provided in the casing 5. Rolling bearing 25, 2
5 supports the transmission shaft 16 concentrically and freely rotatable only. The first and second output side disks 2
0 and 21 are thus provided around the intermediate portion of the transmission shaft 16,
Sleeve 22 rotatably supported on transmission shaft 16
Are spline-engaged with both inner side surfaces 4a, 4a facing each other. Therefore,
The first and second output disks 20 and 21 have their inner surfaces 4a and 4a opposed to the inner surfaces 2a and 2a of the first and second input disks 17 and 18, respectively. The first and second input disks 17 and 18 are concentric with the first and second input disks 17 and 18.
8 and is rotatably supported independently.

Further, the first,
At the side positions of the second output disks 20 and 21, the output disks 20 and 21 are sandwiched from both sides.
The pair of yokes 26a and 26b are supported. These two yokes 26a and 26b correspond to the yokes constituting the first and second support means according to the second aspect, respectively, by pressing a metal plate such as steel, or The metal material is forged to form a rectangular frame. These yokes 26a, 26b are provided at respective four corners with first and second trunnions 27, which will be described later.
Circular support holes 31, 31 for swingably supporting first and second pivots 29, 30 provided at both ends of the transmission shaft 16 are provided at both ends in the axial direction (the left-right direction in FIG. 15) of the transmission shaft 16. Circular locking holes 32, 32 are formed at the center of the width direction of the portion (the left-right direction in FIGS. 16 and 17). The pair of yokes 26a and 26b, each having such a shape,
Supporting posts 33a and 33b formed at portions facing each other on the inner surface of the casing 5 are supported to be slightly displaceable. Each of the support posts 33a and 33b is provided between the inner surface 2a of the first input side disk 17 and the inner surface 4a of the first output side disk 20 in the first cavity 34 and the second input side disk 18, respectively. The second cavity 35, which is a portion between the side surface 2 a and the inner side surface 4 a of the second output side disk 21, is provided so as to face each other. Therefore, in a state where the yokes 26a, 26b are supported by the support posts 33a, 33b, one end of each of the yokes 26a, 26b is on the outer peripheral portion of the first cavity 34, and the other end is on the second cavity. The outer peripheral portion 35 is opposed to each other.

A pair of first trunnions 27, 27 are provided in the first cavity 34 at diametrically opposite positions of the first input side disk 17 and the first output side disk 20 in the second cavity 35. A pair of second trunnions 28, 28 are arranged at diametrically opposite positions of the second input side disk 18 and the second output side disk 21, respectively. The first trunnions 27 are provided concentrically at both ends of the first trunnions 27.
As shown in FIG. 16, a total of four first pivots 29, 29 are attached to one end of the pair of yokes 26a, 26b, respectively.
It is supported so that it can swing and displace in the axial direction. That is, the first pivots 29, 29 are provided inside the support holes 31, 31 formed at one end of each of the yokes 26a, 26b.
Are supported by radial needle bearings 36, 36. Each of these radial needle bearings 36 includes an outer ring 37 whose outer peripheral surface is a spherical convex surface and whose inner peripheral surface is a cylindrical surface, and a plurality of needles 38, 38. Therefore, the first pivots 29, 29 are connected to the yokes 26a, 2
6b is supported at both ends in the width direction at one end thereof so as to be swingable in each direction and displaceable in the axial direction. Further, a pair of second pivots 30, 30 provided concentrically at both ends of each of the second trunnions 28, 28 are housed in the second cavity 35 as shown in FIG. , 27
Are supported by the same structure as each of the first pivots 29, 29 provided above.

As described above, the first and second trunnions 27 are supported inside the casing 5 so as to be able to swing and displace in the axial direction of the first and second pivots 29 and 30. Circular holes 39, 39 are formed in the intermediate portion 28 as shown in FIGS. The first and second displacement shafts 40, 4 are respectively formed in these circular holes 39, 39.
Supports 1. These first and second displacement axes 40, 4
1 is a support shaft 4 which is parallel and eccentric to each other
2 and 42 and pivot shafts 43 and 43. Among these, the respective support shaft portions 42, 42 are rotatably supported inside the respective circular holes 39, 39 via radial needle bearings 44, 44. In addition, first and second power rollers 45 and 46 are rotatably supported around the pivot shafts 43 and 43 via separate radial needle bearings 47 and 47.

The first and second cavities 34, 3
The first and second displacement shafts 40 provided one by one for every 5
41 is, for each of the first and second cavities 34, 35,
It is provided at a position opposite to the input shaft 1a and the transmission shaft 16 by 180 degrees. In addition, these first and second displacement axes 4
Each of the pivot shaft portions 43, 43 of the support shaft portions 0, 41
The directions eccentric to 2 are the first and second input sides,
The rotation direction of each of the output-side disks 17, 18, 20, 21 is the same direction (upside-down direction in FIGS. 16 to 17). The eccentric direction is a direction substantially orthogonal to the direction in which the input shaft 1a is provided. Accordingly, the first and second power rollers 45 and 46 are supported so as to be slightly displaceable in the direction in which the input shaft 1a and the transmission shaft 16 are arranged. As a result, the first and second power rollers 45 and 45 are caused by a change in the amount of elastic deformation of each component based on a change in torque transmitted by the toroidal-type continuously variable transmission.
Reference numeral 46 denotes the axial direction of the input shaft 1a and the transmission shaft 16 (FIG. 15).
(The left-right direction of FIG. 16 and the front-back direction in FIGS. 16 to 17), this displacement can be absorbed without applying excessive force to the constituent members.

Each of the first and second power rollers 4
5, 46 and the first and second trunnions 27,
28, a thrust ball bearing 48, 48 and a thrust bearing 49 such as a slide bearing or a needle bearing, in order from the outer surface side of the first and second power rollers 45, 46. 49 are provided. Of these, the thrust ball bearings 48 are provided with the first and second power rollers 4 respectively.
The first and second power rollers 45 and 46 are allowed to rotate while supporting the thrust load applied to the first and second power rollers 5 and 46. Further, the thrust bearings 49, 49 support the thrust loads applied to the outer rings 50, 50 of the thrust ball bearings 48, 48 from the first and second power rollers 45, 46 while supporting the pivotal support. The shaft portions 43, 43 and the outer rings 50, 50 are allowed to swing around the support shaft portions 42, 42.

Further, the first and second trunnions 27,
Drive rods 51 and 51 are connected to one end of the drive rod 28 (the lower end in FIGS. 16 to 17), respectively.
Driving pistons 52, 52 are fixedly provided on the outer peripheral surface of the intermediate portion of the first and the 51. Each of these drive pistons 52, 52
Are oil-tightly fitted in the drive cylinders 53, 53, respectively. These drive pistons 52, 52 and drive cylinders 53, 53 displace the first and second trunnions 27, 28 in the axial direction of the first and second pivots 29, 30, respectively. Configure the actuator. or,
Pressure oil can be freely supplied and discharged into and from each of the drive cylinders 53 based on switching of a control valve (not shown).

Further, a loading device 10 of the loading cam type is provided between the input shaft 1a and the first input side disk 17. The pressing device 10 includes the input shaft 1
The cam plate 11 is spline-engaged with an intermediate portion of the shaft a and is supported in a state where displacement in the axial direction is prevented, and rotates with the input shaft 1a. And a roller 13. Then, based on the rotation of the input shaft 1a, the first input side disk 17 is rotated while being pressed against the second input side disk 18.

During operation of the toroidal type continuously variable transmission configured as described above, the rotation of the input shaft 1a is transmitted to the first input side disk 17 via the pressing device 10, and the first input side disk 17 and the second input side disk 17 are rotated. The two input side disks 18 rotate in synchronization with each other. The rotation of the first and second input-side disks 17 and 18 causes the first and second power rollers 45 and 46 provided in the first and second cavities 34 and 35 respectively to form a pair. The rotation of the first and second output disks 20, 21 is transmitted to the first and second output disks 20, 21 via the output gear 23.
Taken out. When the rotational speed ratio between the input shaft 1a and the output gear 23 is changed, one pair is provided for each of the first and second cavities 34 and 35 based on the switching of the control valve. Drive piston 52, 52
Is displaced in the opposite direction by the same distance for each of the cavities 34 and 35.

With the displacement of the drive pistons 52, 52, a total of four trunnions 27, 28 are paired.
Are displaced in opposite directions, for example, the first and second power rollers 45 and 46 on the right side of FIGS. Roller 4
5, 46 are respectively displaced to the upper side of each figure. As a result, the peripheral surfaces 9a, 9a of the first and second power rollers 45, 46 and the first and second input side disks 17,
18 and the direction of the tangential force acting on the contact portions of the first and second output side disks 20, 21 with the inner side surfaces 2a, 4a are changed. The first and second trunnions 27 and 28 are moved by the yoke 26 with the change in the direction of the force.
The first and second pivots 29 and 30 pivotally supported by a and 26b swing in opposite directions. As a result, as shown in FIGS. 13 and 14, the peripheral surfaces 9a and 9a of the first and second power rollers 45 and 46 and the disks 1
The contact position between the inner shafts 2a, 4a of the 7, 18, 20, 21 changes, and the rotation speed ratio between the input shaft 1a and the output gear 23 changes.

In the case of the conventional structure shown in FIGS. 15 to 17, the first and second trunnions 27 and 28 are placed inside the casing 5 with the support posts 33a and 33b and the yoke 26 respectively.
a, 26b. For this reason, the increase in the number of parts not only complicates parts production, parts management and assembling work, but also increases the height of the toroidal type continuously variable transmission in the vertical direction in FIGS. It is difficult to reduce the weight. Further, if the size and the weight are forcibly reduced to enable installation in a limited space, the strength of each part is insufficient, and sufficient durability cannot be secured.

On the other hand, Japanese Patent Application Laid-Open No. 10-274300
The publication describes a structure in which pivots provided at both ends of each trunnion constituting a toroidal-type continuously variable transmission are pivotally supported by support members directly fixed to the inner surface of a casing.
According to such a structure, it is possible to reduce the size and weight by reducing the number of parts to some extent. However, in the case of the toroidal-type continuously variable transmission described in the above publication, a support member for supporting the pivot at each trunnion end is provided independently for each trunnion.

[0021]

SUMMARY OF THE INVENTION The above-mentioned Japanese Patent Application Laid-open No. Hei 10-2
In the case of the structure described in Japanese Patent No. 74300, a load acting on each trunnion during operation of the toroidal-type continuously variable transmission is directly applied to the casing. That is, during operation of the toroidal-type continuously variable transmission, a large thrust load is applied to each of the power rollers based on a large surface pressure applied to a contact portion between the inner surface of both the input and output disks and the peripheral surface of each power roller. Is added. Then, the thrust load is applied to the support portion of the pivot provided at the end of each trunnion via each trunnion. In the case of the structure described in the above-mentioned publication, a large load applied to the pivot in this way is directly applied to the casing. The casing of the transmission is often made of a light alloy such as an aluminum alloy in order to reduce the weight.In spite of the large load, in order to prevent the displacement of the pivot and to ensure the durability of the casing,
It is necessary to take measures such as increasing the thickness of the casing, which goes against the reduction in size and weight.

When the toroidal type continuously variable transmission is operated, each trunnion is elastically deformed in a direction in which its inner surface becomes concave due to a large thrust load applied from each power roller. As a result, the center axis of the pivot provided at the end of each of the trunnions and the center axis of the circular hole provided in the support member fixed to the inner surface of the casing become slightly non-parallel. The structure described in the above-mentioned publication does not consider that the trunnions can be smoothly displaced even in such a state without damaging the constituent members.
The toroidal-type continuously variable transmission of the present invention has been invented in view of such circumstances.

[0023]

SUMMARY OF THE INVENTION Among the toroidal-type continuously variable transmissions of the present invention, the toroidal-type continuously variable transmission according to the first aspect is similar to the conventionally known toroidal-type continuously variable transmission. The casing, the input side and the output side discs which are rotatably supported concentrically and independently of each other inside the casing, and intersecting the center axis of the discs at a portion between these discs. However, there are an even number of concentric or parallel pivots, which are present at a twist position perpendicular to the direction of the central axis, and a plurality of trunnions swinging about each of these pivots. Displacement shafts protruding from the inner surface of each trunnion, and a plurality of shafts sandwiched between the inner surfaces of the input side and output side disks while being rotatably supported around the respective displacement shafts. It comprises a power roller, provided on a side of the power rollers and a support means for supporting freely displaceable across the respective pivot the swing displacement and axial direction.
In particular, in the toroidal-type continuously variable transmission according to the first aspect, a yoke for supporting the pivots provided at the ends of the plurality of trunnions and supporting the ends at the ends of the plurality of trunnions is provided in the casing. It is directly supported and fixed to the inner surface. At the same time, the respective pivots can be displaced in the axial direction by splines with respect to the end of the yoke, and needle bearings for supporting the respective pivots so that they can swing freely are provided on the inner diameter side of the splines. I have.

Also, in the toroidal-type continuously variable transmission according to the second aspect, similarly to the above-described conventional toroidal-type continuously variable transmission, the casing and the inside surfaces of the casing are opposed to each other inside the casing. In the state, the first and second outer disks supported concentrically and rotatably in synchronization with each other, and the first and second outer disks in a state where the inner surfaces thereof face the inner surface of the first outer disk. And a first inner disk rotatably supported independently of the first and second outer disks, and the first inner disk with its inner surface facing the inner surface of the second outer disk. A second inner disk concentric with the disk and rotatably supported in synchronization with the first inner disk, and a central axis of each of the disks at a portion between the first outer disk and the first inner disk. There is no difference, but four first concentric or parallel first pivots which are present at a twist position perpendicular to the direction of the central axis, and swing about these first pivots. A pair of first trunnions, a first displacement axis protruding from the inner surface of each of the first trunnions, and the first outer disc inside the first outer disc while being rotatably supported around each of the first displacement axes. A pair of first power rollers sandwiched between the side surface and the inner surface of the first inner disk, and a portion between the second outer disk and the second inner disk, which intersects the central axis of each of these disks. Although there is nothing, four concentric or parallel second pivots existing at a twist position perpendicular to the direction of the central axis, and a pair of pivots about each of the second pivots. Second trunnions and each of these second tigers The second displacement shaft protruding from the inner surface of the ON, and in a state rotatably supported around each of the second displacement shaft, between the inner surface of the second outer disk and the inner surface of the second inner disk. 1 pinched by
The pair of second power rollers, the first and second inner disks, and the two inner disks are sandwiched from both sides, and one end of the pair is located between the first outer disk and the first inner disk. And first and second support means provided substantially parallel to each other with the other end positioned between the second outer disk and the second inner disk. The first supporting means swings the first two pivots of the four first pivots and the second second pivots of the four second pivots, respectively. The second support means is configured to support the remaining two of the four first pivots and the remaining two of the four second pivots. The second pivot is supported so as to be swingable and displaceable in the respective axial directions. In particular, in the toroidal-type continuously variable transmission of the present invention, the first and second support means constitute a yoke for supporting the pivots provided at the ends of the plurality of trunnions at the four corners thereof, It is directly supported and fixed to the inner surface of the casing. At the same time, the above-mentioned pivots are freely displaceable in the axial direction by splines with respect to the four corners of the yoke, and needle bearings for supporting these pivots so that they can swing freely are provided.
The spline is provided on the inner diameter side.

[0025]

With the toroidal-type continuously variable transmission of the present invention configured as described above, the input side disk or the first and second outer disks are connected to the output side disk or the first and second inner disks. In addition to transmitting the rotational force, the operation when changing the speed ratio between the input side disk or the first and second outer disks and the output side disk or the first and second inner disks is conventionally known. It is the same as a known toroidal-type continuously variable transmission. In particular, in the case of the toroidal type continuously variable transmission of the present invention, the number of parts is reduced because the yoke constituting the support means or the first and second support means is directly supported and fixed to the inner surface of the casing. Parts production,
At the same time as simplifying parts management and assembly work, the height and size can be reduced to ensure durability and to reduce size and weight. In addition, since the yoke supports the pivots provided at the ends of the plurality of trunnions, all or a part of the force applied to the plurality of trunnions can be offset in the yoke. For this reason, since a large load is not applied to the casing supporting the yoke, the supporting portions of the pivots can be displaced or the durability of the casing can be increased without increasing the thickness of the casing. It is possible to prevent the property from being impaired. Further, since the spline and the needle bearing are provided between the pivot and the yoke, the displacement of the trunnion with respect to the yoke can be performed smoothly and accurately.

[0026]

1 to 7 show a first embodiment of the present invention. The feature of this example is that first pivots 29, 29 provided at both ends of each first trunnion 27, 27 are provided.
And the structure for reliably synchronizing the inclination angles of the first trunnions 27, 27. The structure and operation of other parts
Since the structure is the same as that of the conventional structure shown in FIGS. 15 to 17, the illustration and description of the equivalent parts are omitted or simplified, and the following description will focus on the characteristic parts of this example. or,
Regarding the second pivots 30, 30 (FIG. 17) provided at both ends of the second trunnions 28, 28, the first pivots 2
With the same structure as that of 9, 29, it is supported on the casing 5, and the inclination angles of the second trunnions 28, 28 are surely synchronized. The following description will be made only for the first trunnions 27, 27 in principle, except for the portions that need to be described in relation to the second trunnions 28, 28.

A pair of yokes 5 constituting first and second support means are provided at opposing portions in the casing 5.
4 and 55 are directly connected to and fixed to the casing 5 in parallel with each other. The positioning accuracy of each of the yokes 54 and 55 with respect to the casing 5 is strictly regulated by the engagement between a knock pin protruding on one side and a locking hole formed on the other side (both are not shown). Circular support holes 31, 31 are formed at positions where the four yokes 54, 55 are aligned with each other at the four corners. Then, among the support holes 31, 31, the yokes 54, 5,
The first pivots 29, 29 are respectively provided inside the support holes 31, 31 formed at one end of the ball spline 5, respectively.
6, 56 and the radial needle bearings 57, 57,
It is supported so as to be displaceable and swingable in the axial direction.

The ball spline outer races 58, 58 which form the ball splines 56, 56 are provided at the opening side halves of the support holes 31, 31 so as to be able to freely swing slightly and extend in the axial direction. It fits internally with limited displacement. For this reason, the small-diameter portions 59, 59 having an inner diameter smaller than the inner side are formed in the opening-side half of each of the support holes 31, 31, respectively.
Is formed. And these small diameter portions 59, 59
The ball spline outer races 58, 58 constituting the respective ball splines 56, 56 are fitted therein. The outer peripheral surfaces of the ball spline outer rings 58, 58 in the axially intermediate portion are partially spherical convex surfaces 60, 60.
The radius of curvature of each of these convex surfaces 60, 60 is
It is almost the same as 内径 of the inner diameter of 1, 31.

Further, the outer race 58 for each of the above-mentioned ball splines,
Outer flange-shaped flanges 61, 61 are provided on the outer peripheral surface of one end in the axial direction of 58, and locking grooves 62, 6 are provided on the outer peripheral surface of the other end in the axial direction.
2 are formed over the entire circumference. Such outer races 58 for ball spline position the respective flanges 61, 61 on the back side of the support holes 31, 31, respectively, and the respective flanges 61, 61 and the respective locking grooves 62 , 6
Each of the small diameter portions 5 between the retaining rings 63, 63 locked to
9 and 59 are assembled so as to be sandwiched from both sides in the axial direction.
In this state, the distance between the flanges 61, 61 and the retaining rings 63, 63 is slightly larger than the axial length of the small diameter portions 59, 59. Therefore, each of the ball spline outer rings 58, 58 is supported in each of the support holes 31, 31 so as to be able to slightly swing and displace.

In addition, the outer race 58 for each ball spline described above,
58, a plurality of outer ring-side ball spline grooves 6
4 and 64 are formed in the axial direction (up and down directions in FIGS. 1 and 3 to 5). And, on the inner diameter side of each of the ball spline outer rings 58, 58, the ball spline inner rings 65, 65 which are also the outer rings of the respective radial needle bearings 57, 57, are concentric with the respective radial needle bearings 57, 57. Has been placed. Inner ring-side ball spline grooves 66, 66 are formed in the outer peripheral surface of each of the ball spline inner rings 65, 65 in portions facing the outer ring-side ball spline grooves 64, 64, respectively, in the axial direction. ing. A plurality of balls 67, 67 are arranged between each of the inner race-side ball spline grooves 66, 66 and each of the outer race-side ball spline grooves 64, 64, and the respective ball splines 56, 56 are arranged. Make up.

Also, the inner race 65 for each of the ball splines described above,
65, the radial needle bearings 57,
The outer raceways 68, 68 having a cylindrical surface shape for 57 are provided. Then, the outer raceways 68, 68 and the first pivots 2 provided at both ends of the first trunnions 27, 27 are provided.
A cylindrical inner raceway 69 formed on the outer peripheral surface of each of the 9, 29;
69, a plurality of needles 70, 7
0, the radial needle bearings 57, 57
Is composed.

One of the first pivots 29, 29 provided at both ends of the first trunnions 27, 27, to which the drive rods 51, 51 are connected (the lower end in FIGS. 1, 3).
Pinions 72, 72 for constituting a gear transmission mechanism 71 described later are externally fitted and fixed to the distal ends of the first pivots 29, 29. On the other hand, a disc-shaped holding plate 73 is provided at the tip of the first pivots 29, 29 at the other end (upper end in FIGS. 1 and 3 to 5) opposite to the drive rods 51, 51 at the center. The first and second pivots 29, 29 are fixed by screwing the screw rods 74 into screw holes 75, 75 provided at the center of the first pivots 29, 29. Such pinions 72, 72 and holding plates 73, 7
3 prevents the ball spline inner rings 65, 65 from moving in the axial direction and the balls 67, 67 from falling off. The balls 67, 67 are prevented from falling off to the opposite side by the base ends of the inner races 65, 65 (ends of the first trunnions 27, 27 at the center in the axial direction). This is achieved by retaining rings 85, 85 locked to.

Incidentally, in the structure of the present embodiment, the assembling work of the ball spline 56 and the radial needle bearing 57 as described above is performed as follows. As shown in FIG. 4, the radial needle bearing 57 including the ball spline inner ring 65 is previously mounted on a first pivot 29 provided at the other end of the first trunnion 27, and a spacer 76 and a retaining ring 77 are provided. And keep it out. The ball spline outer ring 58 is mounted inside the support hole 31 formed in the yoke 54 in advance, as shown in FIG. In this state, the balls 67, 67 constituting the ball spline 56 are formed on the outer peripheral surface of the ball spline inner ring 65 through a through hole 86 formed in a part of the casing 5 which is aligned with the support hole 31. The inner ring-side ball spline grooves 66, 66 and the outer ring-side ball spline grooves 64, 64 formed on the inner peripheral surface of the ball spline outer ring 58.
, A plurality of each is inserted. Then, after the insertion, as shown in FIG.
The through hole 86 is closed by a cover plate 87.

In the case of this embodiment, a pair of first trunnions 27, 27 provided to face each other are connected to each other by a gear transmission mechanism 71, so that the first trunnions 27, 27 are connected to each other. A pair of first power rollers 4 supported
The inclination angles of 5 and 45 are made to exactly match each other. In order to provide the gear transmission mechanism 71, one side (FIGS.
A recess 78 is provided in the yoke 55 (below 3). Therefore, in a state where the yoke 55 and the cylinder case 79 are superimposed, there is a gap between the two members 55 and 79.
A space 80 for accommodating the gear transmission mechanism 71 is formed. Gear transmission mechanism 71 housed in this space 80
Consists of a pair of pinions 72, 72 having the same shape and the same number of teeth as one another, and one rack 81 having teeth of the same pitch formed at both end edges. Each of these pinions 7
Reference numerals 2 and 72 are externally fitted and fixed to non-cylindrical portions formed at the distal ends of the first pivots 29 and 29 provided at the ends of the first trunnions 27 and 27, respectively. Accordingly, each of the first trunnions 27, 27 rotates in synchronization with each of the pinions 72, 72. When the gear ratio is changed, the first trunnions 27, 27 are connected to the first pivots 29, 29, respectively.
Displace in the axial direction of. Therefore, each of the pinions 72, 7
A suitable backlash (to the extent that there is no problem in matching the inclination angle) is provided in the meshing portion between the rack 2 and the rack 81, and the pinions 72, 72 and the rack 81 are provided.
Allows relative displacement with

Also, the rack 81 can freely move only in the axial direction of the input shaft 1a (the front and back directions in FIGS. 1 and 3).
It is supported in the space 80. For this reason, in the illustrated example, the rack 81 is supported on the yoke 55 so as to be freely movable in parallel by rolling bearings (linear bearings) 82, 82 of a linear motion type. That is, guide recesses 83 are formed on the lower surface of the yoke 55 fixed to the inner surface of the casing 5 so as to face the rack 81 in the displacement direction of the rack 81, respectively.

Further, guide flanges 84, 84 are formed in the middle portion of the rack 81 at portions corresponding to the guide recesses 83, 83, respectively. Each of these guide flanges 8
The thickness of the guide recesses 4 and 84 is slightly smaller than the width of the guide recesses 83 and 83, and the guide flanges 84 and 84 are loosely inserted into the guide recesses 83 and 83, respectively.
The rolling bearings 82 are provided between one side surface of each of the flange portions 84 and one inner surface of each of the guide concave portions 83. Such rolling bearings 82, 82 are provided with respective flange portions 84, 8 provided on the rack 81.
4 is arranged at a position sandwiching the rolling bearings 82 from both sides (or opposite to the case shown in the drawing, the respective flanges 84, 84 sandwich the rolling bearings 82, 82 from both sides).

Therefore, the rack 81 is connected to the yoke 55
On the other hand, the guide recesses 83 can be smoothly displaced by a light force without being inclined in the direction of the guide recesses 83. or,
When a force perpendicular to the displacement direction is applied to the rack 81, one of the pair of rolling bearings 82, 82 attached to the rack 81,
82 supports the force and compensates for the smooth displacement of the rack 81.

Each of the pinions 7 supported as described above
The racks 2 and 72 and the rack 81 are provided with the respective pinions 72 and 7.
The gear transmission mechanism 71 is configured by combining the teeth formed on the outer peripheral edge of the rack 2 and the teeth formed on both side edges of the rack 81 in a state where they are meshed with each other. This gear transmission mechanism 71
While minimizing backlash, each pinion 7
The pitch circle diameters of 2, 72 are increased to some extent (within the range where interference with other members can be prevented). Accordingly, the first trunnions 27, 27 to which the respective pinions 72, 72 are fixed, and the respective first trunnions 2
The inclination angles of the first power rollers 45, 45 supported by 7, 27 can be made to exactly match each other. Although not shown, a gear transmission mechanism having the same structure is provided between each of the first trunnions 27, 27 and the second trunnions 28, 28 (FIG. 17).
The inclination angle between 7, 27 and the second trunnions 28, 28
They try to match each other.

As described above, in the case of the toroidal type continuously variable transmission according to the present invention, the yokes 54 and 55, which are members constituting the first and second support means, are attached to the inner surface of the casing 5. It is directly supported and fixed. For this reason, the support posts 33a and 33b (FIGS. 15 to 17) required in the above-described conventional structure are not required, and the number of components is reduced, thereby simplifying component production, component management, and assembling work.
The height can be reduced, and the size and weight can be reduced while ensuring durability.

Further, in the case of the present invention, the first and second trunnions 2 are formed at the four corners of the yokes 54 and 55.
7 and 28, 2 each, 4 trunnions 2 in total
The first and second pivots 29, 30 provided at the ends of 7, 28 are supported. Therefore, each of these first and second trunnions 2
All of the forces applied to the yokes 54, 55
Can be offset within. This will be described with reference to FIG. As described above, during operation of the toroidal-type continuously variable transmission, a large thrust load is applied to the first and second trunnions 27 and 28 from the first and second power rollers 45 and 46, respectively, as indicated by an arrow α in FIG. In the direction shown by. Each of these thrust loads is indicated by an arrow β in FIG.
The first and second cavities 34 and 35 (FIG. 1) are divided into a component force in the diametric direction and a component force in the axial direction of the input shaft 1a indicated by an arrow γ in FIG.

As is apparent from FIG. 6 showing such a direction of the force, the diametrical component force β of the first and second cavities 34 and 35 is equal to the first and second cavities 34 and 35 arranged in the same cavity.
The second trunnions 27 and 28 have the same size in opposite directions. The component force γ of the input shaft 1a in the axial direction is the same in the opposite direction and the same in each of the first and second trunnions 27 and 28 arranged in adjacent cavities. Therefore, all of the forces applied to the first and second trunnions 27 and 28 are canceled out in the yokes 54 and 55, and the casing 5 supporting the yokes 54 and 55 reaches the casing 5.
This power is not added. Therefore, a large load is not applied to the casing 5, and the first and second pivots 2 can be provided without increasing the thickness of the casing 5 in particular.
9 and 30 are displaced or the casing 5
Can be prevented from being damaged.

Each of the first pivots 29, 29 and the yoke 5
4 and 55, the ball spline 56 and the radial needle bearing 57 are provided.
The displacement of each of the first trunnions 27, 27 with respect to 4, 55 can be performed smoothly and accurately. That is, as is clear from the above description, the first trunnions 27, 27 are displaced in the axial direction of the first pivots 29, 29 during the shifting operation of the toroidal type continuously variable transmission. On the basis of the first pivots 29, 29. In the case of this example, the axial displacement of these displacements is
By the ball spline 56, the swing displacement is smoothly performed by the radial needle bearing 57, respectively.
The speed change operation of the toroidal-type continuously variable transmission based on each of these displacements can be performed quickly and accurately.

Further, the outer race 5 for each of the ball splines described above.
8 and 58 are partially spherical convex surfaces 60, respectively.
60, regardless of the elastic deformation of the first trunnions 27, 27, the radial needle bearings 57,
Edge load can be prevented from being applied to a contact portion between the rolling surfaces of the needles 70, 70 constituting the outer ring raceway 68 and the inner ring raceway 69. That is, a large thrust load is applied to each of the first power rollers 45, 45 during operation of the toroidal type continuously variable transmission, and the first trunnions 27, 27 are exaggerated in FIG. 7 based on the thrust load. Thus, the inner surfaces facing each other are elastically deformed in a direction in which the inner surfaces become concave. Then, based on this elastic deformation, the center axis of each of the first pivots 29, 29 and the center axis of each of the support holes 31, 31 become slightly inconsistent. Therefore, in such a case, in the structure of the present embodiment, the respective outer races 58 for ball spline swing and displace in the respective support holes 31. And each of these ball spline outer rings 58,
The central axis of the ball spline inner ring 65, 65, which is also the outer ring of each of the radial needle bearings 57, 57 disposed on the central axis and the inner diameter side of 58, is the same as the central axis of each of the first pivots 27, 27. Leave it matched. The structure of the present embodiment compensates for the mismatch between the central axis of each of the first pivots 29, 29 and the central axis of each of the support holes 31, 31 in this way, and prevents the aforementioned edge load from being applied.

Further, as shown in the illustrated example, the gear transmission mechanism 71
In order to make the inclination angles of the first power rollers 45, 45 coincide with each other,
Peripheral surface 9a, 9a and the inner surface 2 of each disk 17, 20
A significant slippage is prevented from occurring at the abutment portions a and 4a, and the efficiency of the toroidal type continuously variable transmission can be sufficiently ensured. The gear transmission mechanism 71 sets the inclination angle between the first power rollers 45, 45, and between the first power rollers 45, 45 and the second power rollers 46, 46 (see FIG. 17). It is effective to exactly match, but when practicing the present invention, each of these power rollers 4
The synchronization mechanism for matching the inclination angles of 5, 46 with each other is as follows:
It is not limited to the gear transmission mechanism 71 as shown. A conventionally well-known cable-type synchronization mechanism may be used.

Further, when the present invention is implemented with a toroidal type continuously variable transmission of a double cavity type, the load applied to the yoke is almost completely canceled in the yoke, and the casing supporting the yoke has a large size. It is effective in preventing the application of force. However, as shown in FIGS. 13 and 14, a certain effect can be obtained even with a single-cavity toroidal type continuously variable transmission in which one input side disk 2 and one output side disk 4 are provided. Can be. However, in the case of a single-cavity toroidal-type continuously variable transmission, as shown in FIG. 8, depending on the operation state, the power rollers 9 and 9 connect the trunnions 7 and 7 to the casing to which the yoke 88 is fixed. A part of the load applied to is applied.

That is, when the rotational speeds of the input side disk 2 and the output side disk 4 are made equal to each other (the gear ratio is 1), as shown in FIG. 7, loads of the same magnitude are applied in opposite directions. Therefore, the load applied to each of the trunnions 7, 7 is almost completely canceled in the yoke 88, and no load is applied to the casing supporting the yoke 88. On the other hand, when the rotational speeds of the input side disk 2 and the output side disk 4 are made different from each other (the gear ratio is set to other than 1), as shown in FIG. Of the load applied to 7, the axial component force of the input-side disk 2 and the output-side disk 4 remains without being canceled and is applied to the casing. Since the magnitude of the component force applied to the casing is originally smaller than the load applied to each of the trunnions 7, 7, if the yoke 88 is fixed to the casing at a plurality of locations, the aforementioned Japanese Patent Application Laid-Open
Unlike the structure described in Japanese Unexamined Patent Publication No. -274300, in which the load applied to each trunnion is transmitted to the casing as it is, it is possible to prevent deformation of the casing and ensure durability at a practically acceptable level.

Next, FIGS. 9 to 11 show a second example of the embodiment of the present invention. In this example, each first trunnion 2
Of the first pivots 29, 29 provided at both end portions of 7, 27,
The structure of a portion for supporting the first pivots 29, 29 at the other end portion on the opposite side to the drive rods 51, 51 with respect to the casing 5 is different from that of the above-described first example. That is, in this example,
In order to assemble the ball splines 56 for supporting the first pivots 29 near the other end to the yoke 54, the through holes 86 (FIGS. 4 and 5) as in the above-described first example are unnecessary. This eliminates the need for a cover plate 87 (FIG. 5) for closing the through hole 86, thereby reducing costs and improving the strength of the casing 5.

For this reason, in the case of the present example, two small-diameter portions 59 formed on the opening half of the support hole 31 of the yoke 54 are located at two positions on the opposite side in the diameter direction. Notched notches 89, 89 are formed. Also, at two positions on the outer peripheral surface of the ball spline outer ring 58 on the diametrically opposite side of the outer peripheral surface thereof (upper end portions in FIGS. 9 to 10), protruding pieces 90, 90 which can pass through the notches 89, 89 respectively.
Is formed. A locking notch 91 is formed at the center of the outer peripheral edge of one of the protruding pieces 90 (rightward in FIG. 10 and upper right in FIG. 11). A portion corresponding to the small-diameter portion 59 of the support hole 31 provided in the yoke 54 and located between the notches 89, 89 and aligned with the locking notch 91 includes a screw hole 92. The tip of a set screw 93 screwed into the screw hole 92 is engaged with the locking notch 91.

The structure of the present embodiment as described above is assembled as follows. A radial needle bearing 57 and a ball spline 56 are assembled to the end of the first pivot 29 in advance. The plurality of balls 67, 67 constituting the ball spline 56 are prevented from coming off by a retaining ring locked on the inner peripheral surface of the end of the outer race 58 for ball spline or the outer peripheral surface of the end of the inner race 65 for ball spline. deep. And
With the notches 89, 89 and the projecting pieces 90, 90 aligned, the projecting pieces 90, 90 are inserted into the support holes 31, and then the ball spline outer ring 58 is And the locking notch 91 is aligned with the screw hole 92. Next, the set screw 93 is screwed into the screw hole 92, and the tip of the set screw 93 is advanced into the locking notch 91. As a result, the respective notches 89, 89 and the respective protruding pieces 90, 90 remain out of phase, and the ball spline outer ring 58 can be supported in the support hole 31. Other configurations and operations are the same as those of the first example described above.

Next, FIG. 12 shows a third example of the embodiment of the present invention. In the case of this example, the outer ring-side ball spline grooves 64, 64 formed on the inner peripheral surface of the ball spline outer ring 58 and the inner ring-side ball spline grooves 66, 66 formed on the outer peripheral surface of the ball spline inner ring 65. Rollers 94, 94 are interposed therebetween. Therefore, the radial load capacity of the spline portion can be increased.
The rollers 94 do not roll with the axial movement of the first pivots 29. Therefore, in the case of this example, the force required for the axial movement of these first pivots 29, 29 is larger than in the case of the above-described first example and the above-mentioned second example. The axial movement is
Since the driving cylinder 53 (FIGS. 1 and 9) is used with a stronger force, if the diameter and the hydraulic pressure of the driving cylinder 53 can be ensured, practically sufficient responsiveness can be obtained. Other configurations and operations are the same as in the case of the above-described first example.

[0051]

Since the present invention is constructed and operates as described above, it can be made small, light and inexpensive, and can contribute to the realization of a toroidal type continuously variable transmission having excellent transmission efficiency and durability. .

[Brief description of the drawings]

FIG. 1 is a view showing a first example of an embodiment of the present invention and corresponding to an AA cross section in FIG. 15;

FIG. 2 is a sectional view taken along line BB of FIG.

FIG. 3 is an enlarged sectional view showing a right part of FIG. 1;

FIG. 4 is a view corresponding to a portion C in FIG. 1 and showing a state during assembly.

FIG. 5 is a view showing a state of completion of assembly, corresponding to a portion C in FIG. 1;

6 is a diagram showing a state of a force applied to a yoke constituting the double-cavity toroidal type continuously variable transmission, as viewed from above in FIG.

FIG. 7 is a partial cross-sectional view corresponding to the upper right part of FIG. 1 and exaggeratingly showing the deformation state of the trunnion during operation.

FIG. 8 is a view similar to FIG. 6, illustrating a state of a force applied to a yoke constituting the single-cavity toroidal type continuously variable transmission.

FIG. 9 is a view showing a second example of the embodiment of the present invention and corresponding to an AA cross section in FIG. 15;

FIG. 10 is an enlarged view of a portion D in FIG. 9;
11 shows the EOF section, and the lower side shows the EOG section of FIG. 11.

FIG. 11 is a view as viewed from above in FIG. 10 with the casing omitted;

FIG. 12 is a view similar to FIG. 3, showing a third example of the embodiment of the present invention;

FIG. 13 is a side view showing a basic configuration of a conventionally known toroidal-type continuously variable transmission in a state of maximum deceleration.

FIG. 14 is a side view showing a state at the time of maximum speed increase.

FIG. 15 is a sectional view showing an example of a conventional specific structure.

16 is a sectional view taken along line AA of FIG.

FIG. 17 is a sectional view taken along the line HH in FIG.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1, 1a Input shaft 2 Input side disk 2a Inner surface 3 Output shaft 4 Output side disk 4a Inner surface 5 Casing 6 Pivot 7 Trunnion 8 Displacement shaft 9 Power roller 9a Peripheral surface 10 Pressing device 11 Cam plate 12 Cage 13 Roller 14 Cam Surface 15 Cam surface 16 Transmission shaft 17 First input side disk 18 Second input side disk 19 Ball spline 20 First output side disk 21 Second output side disk 22 Sleeve 23 Output gear 24 Support wall 25 Rolling bearing 26a, 26b Yoke 27 First trunnion 28 Second trunnion 29 First pivot 30 Second pivot 31 Support hole 32 Locking hole 33a, 33b Support post 34 First cavity 35 Second cavity 36 Radial needle bearing 37 Outer ring 38 Needle 39 Circular hole 40 First displacement Axis 41 Second displacement axis 42 Bearing part 43 Pivot shaft part 44 Radial needle bearing 45 First power roller 46 Second power roller 47 Radial needle bearing 48 Thrust ball bearing 49 Thrust bearing 50 Outer ring 51 Drive rod 52 Drive piston 53 Drive cylinder 54 Yoke 55 Yoke 56 Ball Spline 57 Radial needle bearing 58 Outer ring for ball spline 59 Small diameter portion 60 Convex surface 61 Flange 62 Lock groove 63 Retaining ring 64 Outer ring side ball spline groove 65 Inner ring for ball spline 66 Inner ring side ball spline groove 67 Ball 68 Outer ring raceway 69 Inner ring raceway 70 Needle 71 Gear Transmission Mechanism 72 Pinion 73 Holding Plate 74 Screw Rod 75 Screw Hole 76 Spacer 77 Retaining Ring 78 Recess 79 Cylinder Case 80 Space 81 Rack 82 Rolling Bearing 83 Guide Recess 84 Guide flange 85 Retaining ring 86 Through hole 87 Cover plate 88 Yoke 89 Notch 90 Protrusion 91 Locking notch 92 Screw hole 93 Set screw 94 Roller

 ──────────────────────────────────────────────────続 き Continuation of the front page (72) Inventor Takashi Imanishi 1-5-50 Kumeinuma Shinmei, Fujisawa-shi, Kanagawa Prefecture Nippon Seiko Co., Ltd. (72) Inventor Takashi Machida 1-150 Kumeinuma Shinmei, Fujisawa-shi, Kanagawa Prefecture F-term in NSK Ltd. (reference) 3J051 AA03 AA08 BA03 BB02 BD02 BE09 CA05 CB07 EC03 ED14 ED20 FA02

Claims (4)

[Claims] 1. A casing, an input side disk and an output side disk which are rotatably supported concentrically and independently of each other inside the casing, and a central axis of the two disks at a portion between the two disks. Although it does not intersect, there is an even number of concentric or parallel pivots that exist at a twist position that is perpendicular to the direction of this central axis, and a plurality of pivots that swing about each of these pivots. The trunnion, the displacement shaft protruding from the inner surface of each of the trunnions, and the input side and the output side of the disk are sandwiched between the inner surfaces of the two disks in a state of being rotatably supported around the respective displacement axes. A toroidal-type continuously variable transmission comprising a plurality of power rollers and supporting means provided on the side of each of the power rollers to support the pivots so as to be able to swing and displace in the axial direction. In the machine, a yoke for supporting the pivots provided at the ends of the plurality of trunnions and supporting the ends at the ends of the plurality of trunnions is directly supported and fixed to the inner surface of the casing. On the other hand, the above-mentioned respective pivots can be displaced in the axial direction by splines, and needle bearings for supporting these respective pivots so as to be freely displaceable are provided on the inner diameter side of the splines. transmission. 2. A casing, first and second outer disks rotatably supported concentrically and synchronously with each other in a state in which the inner surfaces face each other inside the casing, and inner surfaces thereof. A first inner disk concentric with the first and second outer disks in a state where the first inner disk is opposed to the inner surface of the first outer disk, and a first inner disk rotatably supported independently of the first and second outer disks. A second inner disk rotatably supported concentrically with the first inner disk with its inner surface facing the inner surface of the second outer disk, and synchronously with the first inner disk; The portion between the outer disk and the first inner disk does not intersect with the center axis of each of these disks, but exists at a twisted position perpendicular to the direction of the center axis. I Or four parallel first axes, a pair of first trunnions swinging about these first axes, a first displacement axis projecting from the inner surface of each first trunnion, A pair of first power rollers sandwiched between an inner surface of the first outer disk and an inner surface of the first inner disk while being rotatably supported around the first displacement axis; The portion between the two outer disks and the second inner disk does not intersect with the center axis of each of these disks, but exists at a twisted position perpendicular to the direction of the center axis, concentric with each other, or Four parallel second pivots, a pair of second trunnions swinging about the respective second pivots, a second displacement axis protruding from the inner surface of each of the second trunnions, While being rotatably supported around the displacement axis, A pair of second power rollers sandwiched between the inner surface of the second outer disk and the inner surface of the second inner disk; With one end positioned at the portion between the first outer disk and the first inner disk, and the other end positioned at the portion between the second outer disk and the second inner disk. And first and second support means provided substantially parallel to each other, wherein the first support means comprises two of the four first pivots and the four first pivots. The two pivots of the second pivot are supported so as to swing and be displaceable in their respective axial directions. The second support means includes:
The remaining two first pivots of the four first pivots and the two second pivots of the four second pivots are supported swingably and displaceably in their respective axial directions. In the toroidal-type continuously variable transmission, the first and second supporting means are provided, and the yokes for supporting the pivots provided at the ends of the plurality of trunnions at the four corners thereof are provided in the casing. The spline is directly supported on the inner surface of the yoke, and each of the pivots is axially displaceable with respect to the four corners of the yoke by splines. A toroidal-type continuously variable transmission characterized in that it is provided on the inner diameter side of. 3. The spline is a ball spline,
An outer peripheral surface of an outer ring having a ball spline groove constituting the ball spline formed on an inner peripheral surface thereof has a partially spherical convex surface, and the convex surface is fitted in a circular hole formed in the yoke so as to be swingably displaceable. A toroidal-type continuously variable transmission according to any one of claims 1 to 2. 4. A gear transmission mechanism is provided between the plurality of trunnions to synchronize the tilting of each of the trunnions.
The toroidal-type continuously variable transmission according to claim 1.