JPH1151135A - Toroidal type continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To realize efficient mounting work of a locking ring which restricts the displacement of a ball by providing a small diameter part between an input side disc and an output side disc on an outer peripheral face of an intermediate part of a rotary shaft, making a locking groove even with the small diameter part, and mounting the locking ring in the locking groove through the small diameter part freely. SOLUTION: A small diameter part 51 is formed over whole periphery in a part between an input side disc 2B and an output side disc 4 on an outer peripheral face of an intermediate part of an input shaft 15. A difference in steps h between an outer peripheral face of the small diameter part 51 and a part other than this outer peripheral face is larger than a width W over the direction of a diameter of a locking ring 50. A locking groove 49 is formed over whole periphery on an inner peripheral face close to an inner face 2a of the disc 2B in a condition in which it crosses a ball spline groove 46 on inside diameter side in the orthogonal direction. The locking ring 50 is mounted in the locking groove 49 through the small diameter part 51 while an opening part on inside diameter side of the locking groove 49 is made even with the small diameter part 51. Consequently, the extra work that a plurality of balls 48, 48 are bonded to a ball spline groove 47 on outside diameter side becomes unnecessary, and the assembly work becomes easy.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

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

[0002]

2. Description of the Related Art The use of a toroidal-type continuously variable transmission as schematically shown in FIGS. This toroidal type continuously variable transmission supports an input 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 side disk (second disk) 4 is fixed to an end of the output shaft 3 which is arranged concentrically with the above.
Inside the casing containing the toroidal-type continuously variable transmission, trunnions 6, 6 swinging about pivots 5, 5 which are twisted with respect to the input shaft 1 and the output shaft 3, are provided.
Is provided.

Each of the trunnions 6, 6 has the pivots 5, 5 on the outer surfaces of both ends. In addition, the trunnions 6 and 6 support the base ends of the displacement shafts 7 and 7 at the intermediate portions thereof, and swing the trunnions 6 and 6 about the pivots 5 and 5 so that the displacements of the trunnions 6 and 6 are adjusted. The inclination angles of the shafts 7, 7 can be adjusted freely. Power rollers 8 are rotatably supported around the displacement shafts 7 supported by the trunnions 6 respectively. And
These power rollers 8, 8 are sandwiched between inner surfaces 2a, 4a of the input-side and output-side disks 2, 4 facing each other. Each of these inner surfaces 2a, 4a
Each section has a concave surface obtained by rotating an arc about the pivot 5. Then, the peripheral surfaces 8a, 8a of the respective power rollers 8, 8 formed on the spherical convex surface,
The inner surfaces 2a and 4a are in contact with each other.

[0004] A loading device 9 of a loading cam type is provided between the input shaft 1 and the input disk 2, and the input disk 2 is directed toward the output disk 4 by this pressing device 9 so as to be elastic. It can be pressed freely. The pressing device 9 includes a cam plate 10 that rotates together with the input shaft 1, and a plurality (for example, four) of rollers 12, which are rotatably held by a holder 11. The cam plate 10
On one side surface (left side surface in FIGS. 8 and 9), a cam surface 13 which is an uneven surface extending in the circumferential direction is formed.
The same cam surface 14 is also provided on the outer side surface (the right side surface in FIGS. 8 and 9).
Is formed. Then, the plurality of rollers 12, 1
2 is rotatably supported with respect to the center of the input shaft 1 about a radial axis.

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 configuration is used, the cam surface 13 causes the plurality of rollers 12, 12 to move to the input side disk. 2 against the cam surface 14 formed on the outer surface. 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, and the output shaft 3 fixed to the output side disk 4 rotates.

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

FIGS. 10 to 11 show Japanese Utility Model Application No. 63-692.
1 shows an example of a more specific toroidal-type continuously variable transmission described in the microfilm of No. 93 (Japanese Utility Model Laid-Open No. 1-173552). The input side disk 2 and the output side disk 4 are rotatably supported around a cylindrical input shaft 15 via needle bearings 16, 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. 10) 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, 12 are used to load and rotate the input disk 2 while pressing the input disk 2 toward the output disk 4 based on the rotation of the input shaft 15. Is composed. 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 on a pair of support plates 20, 20 so as to be swingable and displaceable in the axial direction (front and back directions in FIG. 10, and left and right directions in FIG. 11). I have. The displacement shafts 7, 7 are supported by circular holes 23, 23 formed in the middle portions of the trunnions 6, 6, respectively. 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, 21 is provided inside the above-mentioned circular hole 23, 23 with a radial needle bearing 24,
It is rotatably supported via 24. The power rollers 8, 8 are rotatably supported around the pivot shafts 22, 22 via 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. In FIG. 11, the left and right directions are opposite. The eccentric direction is
The direction is substantially perpendicular to the direction in which the input shaft 15 is provided. Accordingly, the power rollers 8 are supported to be slightly displaceable in the direction in which the input shaft 15 is provided. As a result, the power rollers 8, 8 move in the axial direction of the input shaft 15 (see FIG. Even in the case of displacement in the left-right direction (the front-back direction in FIG. 11), this displacement can be absorbed without applying unreasonable force to the components.

Further, between the outer surface of each of the power rollers 8, 8 and the inner surface of the intermediate portion of each of the trunnions 6, 6, a thrust ball bearing 26, 26 and thrust needle bearings 27, 27 are provided. The thrust ball bearings 26 support rotation of the power rollers 8 while supporting the load applied to the power rollers 8 in the thrust direction. Each of such thrust ball bearings 26, 26 has a plurality of balls 29, 29, and each of these balls 2
Circular retainers 28, 2 that hold rolling rolls 9, 29 freely
8 and an annular outer ring 30, which is a thrust bearing ring. The inner raceway of each thrust ball bearing 26, 26 is formed on the outer surface of each of the power rollers 8, 8, and the outer raceway is formed on the inner surface of each of the outer races 30, 30, respectively.

The thrust needle bearings 27, 2
7 comprises a race 31, a retainer 32, and needles 33,33. The race 31 and the retainer 32 are combined so as to be slightly displaceable in the rotation direction. Such thrust needle bearings 27, 27 are arranged such that the races 31, 31 are in contact with the inner surfaces of the trunnions 6, 6, and the inner surfaces and the outer races 30, 30, respectively.
Between the outer surface of the The thrust needle bearings 27, 27 support the thrust loads applied to the outer rings 30, 30 from the power rollers 8, 8, respectively, while supporting the pivot shafts 22, 22, and the outer rings 30, 30.
However, swinging about the support shaft portions 21 and 21 is allowed.

Further, drive rods 36, 36 are provided at one end (the left end in FIG. 11) of each of the trunnions 6, 6, respectively.
And drive pistons 37, 37 are fixedly provided on the outer peripheral surface of the intermediate portion of each of the drive rods 36, 36. And
These drive pistons 37 are fitted in drive cylinders 38 in an oil-tight manner, respectively.

In the case of the toroidal type continuously variable transmission configured as described above, the rotation of the input shaft 15 is transmitted to the input side disk 2 via the pressing device 9. Then, the rotation of the input side disk 2 is transmitted to the output side disk 4 via the pair of power rollers 8, 8, and further, the output side disk 4
Is taken out from the output gear 18. Input shaft 15
When changing the rotation speed ratio between the output gear 18 and
The pair of drive pistons 37 are displaced in directions opposite to each other. The pair of trunnions 6, 6 are displaced in opposite directions with the displacement of the drive pistons 37, 37. For example, the lower power roller 8 in FIG. Power roller 8 on the left side of FIG.
Each is displaced. As a result, the direction of the tangential force acting on the contact portions between the peripheral surfaces 8a, 8a of the power rollers 8, 8 and the inner surfaces 2a, 4a of the input disk 2 and the output disk 4 changes. I do. Then, with the change in the direction of the force, the trunnions 6 swing in opposite directions about the pivots 5 pivotally supported by the support plates 20. As a result, as shown in FIGS. 8 and 9 described above, the contact positions between the peripheral surfaces 8a, 8a of the power rollers 8, 8 and the inner surfaces 2a, 4a change, and the input shaft 15 The rotation speed ratio with the output gear 18 changes.

In this manner, the input shaft 15 and the output gear 1
When transmitting the rotational force to the power rollers 8, the power rollers 8, 8 are displaced in the axial direction of the input shaft 15 based on the elastic deformation of the constituent members. Each of the displacement shafts 7 pivotally supporting the pivot 8 slightly rotates around the support shaft portions 21. As a result of this rotation, the outer ring 30 of each of the thrust ball bearings 26, 26,
The outer side surface of the trunnion 6 and the inner side surface of each of the trunnions 6 are relatively displaced. Since the thrust needle bearings 27 exist between the outer surface and the inner surface, the force required for the relative displacement is small. Therefore, the force for changing the inclination angle of each of the displacement shafts 7 can be small as described above.

Further, in order to increase the transmittable torque, two input disks 2A and 2B and two output disks 4 and 4 are provided around the input shaft 15 as shown in FIGS. A structure in which two input-side disks 2A and 2B and two output-side disks 4 and 4 are arranged in parallel with each other in the power transmission direction is also conventionally known. In each of the structures shown in FIGS. 12 and 13, an output gear 18 a is supported around an intermediate portion of the input shaft 15 so as to freely rotate with respect to the input shaft 15, and a cylinder provided at the center of the output gear 18. The output side disks 4 and 4
Are spline-engaged. Needle bearings 16 and 16 are provided between the inner peripheral surface of each of the output side disks 4 and 4 and the outer peripheral surface of the input shaft 15, and these output side disks 4 and 4 are provided around the input shaft 15. The rotation of the input shaft 15 and the displacement of the input shaft 15 in the axial direction are freely supported. The input disks 2A and 2B are rotatably supported on both ends of the input shaft 15 together with the input shaft 15.

However, the input side disk 2A (left side in FIGS. 12 to 13) has a rear surface (left side in FIGS. 12 to 13) directly on the loading nut 39 (in the case of the structure shown in FIG. 13) or large. The input shaft 15 is brought into contact with an elastic disc spring 45 in the case of the structure shown in FIG.
In the axial direction (the left-right direction in FIGS. 12 and 13). On the other hand, the input side disk 2B facing the cam plate 10 is supported on the input shaft 15 by a ball spline 40 so as to be freely displaceable in the axial direction. Then, the rear side of the input side disk 2B (FIG. 12)
13 and the front surface of the cam plate 10 (the left surface in FIGS. 12 to 13).
And are provided in series with each other. Disc spring 4 of these
1 is an inner surface 2a of each of the disks 2A, 2B, 4;
a, and serves to apply a preload to the contact portion between the power rollers 8, 8 and the peripheral surfaces 8a, 8a. Further, the thrust needle bearing 42 plays a role of permitting relative rotation between the input side disk 2B and the cam plate 10 when the pressing device 9 is operated.

In the case of the structure shown in FIG. 12, the output gear 18a is connected to a partition 44 provided inside the housing.
In addition, a pair of angular ball bearings 43, 43 are rotatably supported in a state where displacement in the axial direction is prevented. On the other hand, in the case of the structural example shown in FIG. 13, the displacement of the output gear 18a in the axial direction is free. As shown in FIGS. 12 and 13 described above, a so-called double-cavity toroidal in which two input disks 2A and 2B and two output disks 4 and 4 are arranged in parallel in the power transmission direction. The reason why the type continuously variable transmission supports one or both of the input disks 2A, 2B facing the cam plate 10 on the input shaft 15 by the ball splines 40, 40a so as to be displaceable in the axial direction is as follows. Next. The rotations of these two disks 2A, 2B are completely synchronized. While providing the above function, both the disks 2A and 2B are allowed to be displaced in the axial direction with respect to the input shaft 15 based on the elastic deformation of the constituent members accompanying the operation of the pressing device 9.

The ball splines 40 and 40a installed for the above-described purpose are provided in the inner diameter side ball spline grooves 46 formed in the inner peripheral surfaces of the input side disks 2A and 2B and in the outer peripheral surface of the intermediate portion of the input shaft 15. The formed outer diameter side ball spline grooves 47 and these two ball spline grooves 46, 4
A plurality of balls 4 rotatably provided between the 7
8, 48. As for the ball spline 40 for supporting the input disk 2B on the pressing device 9 side, a locking ring 50 is formed in a locking groove 49 formed in a portion of the inner peripheral surface of the input disk 2B near the inner surface 2a. Lock the
The plurality of balls 48, 48 are connected to the input side disk 2.
A and 2B are restricted from being displaced toward the inner side surface 2a.
Further, the balls 48, 48 are prevented from falling out from between the inner diameter side and outer diameter side ball spline grooves 46, 47. In the structure shown in FIG. 12, the ball spline 40a for supporting the input disk 2A remote from the pressing device 9 is related to the locking groove 49a formed on the outer peripheral surface of the intermediate portion of the input shaft 15. Locking the retaining ring 50a restricts displacement of the plurality of balls 48, 48 toward the inner side surface 2a of the input side disk 2A.

[0019]

In the case of the conventional structure, the operation of locking the locking ring 50 in the locking groove 49 formed in the inner peripheral surface of the input side disk 2B on the pressing device 9 side is troublesome, and a toroidal type is required. This has caused the manufacturing cost of the continuously variable transmission to be high. That is, after the input disk 2B is externally fitted around the intermediate portion of the input shaft 15, the locking ring 5 is provided between the inner peripheral surface of the input disk 2B and the outer peripheral surface of the input shaft 15.
There is no gap enough to pass zero. Because of this,
Prior to externally fitting the input side disk 2B to the input shaft 15, it is necessary to mount the locking ring 50 in the locking groove 49. The input side disk 2B to which the locking ring 50 is mounted in advance in this way is externally fitted to a part of the input shaft 15 where the outer diameter side ball spline groove 47 is formed. In the groove 47 part,
A plurality of balls 48, 48 are lightly bonded in advance with grease or the like.

Since the lubrication of the internal mechanism of the toroidal type continuously variable transmission including the ball spline 40 is performed by traction oil, the outer diameter side ball spline groove 47 is originally required.
There is no need to apply grease to the surface. Therefore, the operation of lightly adhering the plurality of balls 48, 48 with the grease or the like is necessary only for assembling with the locking ring 50 mounted on the locking groove 49. In this way, the work of fitting the input-side disc 2B to the input shaft 15 in a state where the locking ring 50 is mounted on the locking groove 49 is troublesome. This has increased the manufacturing cost of the toroidal type continuously variable transmission.
The toroidal type continuously variable transmission of the present invention has been invented in order to eliminate such troubles.

[0021]

The toroidal-type continuously variable transmission according to the present invention has a rotary shaft and a ball spline around an intermediate portion of the rotary shaft, similarly to the above-mentioned conventional toroidal-type continuously variable transmission. By supporting the first disk, it is possible to freely displace in the axial direction with respect to the rotation axis and rotate in synchronization with the rotation axis, and to rotate the first disk in a state where the first disk and the inner surface face each other. A second disk, which is rotatably supported relative to the rotating shaft, around a middle portion of the shaft, a trunnion that swings around a pivot that is twisted with respect to the rotating shaft, and a supporting shaft eccentric to each other And a pivot shaft portion, of which a support shaft portion is rotatably supported by the trunnion, and a displacement shaft having the pivot shaft portion protruding from the inner surface of the trunnion, and a periphery of the pivot shaft portion. Rotatably supported In this state, a power roller sandwiched between the inner surfaces of the first and second disks and a portion provided between the part of the rotating shaft and the first disk are provided. And a loading device of a loading cam type for rotating the first disk while pressing the disk toward the second disk. This pressing device,
For example, a cam plate which is supported on a part of the rotating shaft while limiting the displacement of the rotating shaft in the axial direction and rotates during operation, and a cam disc which is located on both side surfaces of the cam plate and which is outside the first disk. A first cam surface formed on one side surface facing the side surface and having irregularities extending in a circumferential direction, and a second cam surface formed on the outer surface of the first disk has irregularities extending in a circumferential direction. And a plurality of rolling elements sandwiched between the first and second cam surfaces. The ball spline includes an inner-diameter-side ball spline groove formed on the inner peripheral surface of the first disk, an outer-diameter-side ball spline groove formed on the outer peripheral surface of an intermediate portion of the rotating shaft, and both of the ball spline grooves. A plurality of balls provided rotatably between them, a locking groove formed in a portion of the inner peripheral surface of the first disk near the inner surface, and The plurality of balls comprise a locking ring for limiting displacement of the first disk toward the inner surface. In particular, in the toroidal-type continuously variable transmission of the present invention, a small-diameter portion is provided between the first and second disks on the outer peripheral surface of the intermediate portion of the rotating shaft, and the opening of the locking groove is provided. The small diameter portion is aligned with the small diameter portion so that the locking ring can be freely attached to the locking groove through the small diameter portion. The opening of the locking groove and the small-diameter portion allow, for example, the rolling surfaces of a plurality of rolling elements constituting the pressing device to abut against the projections of the first and second cam surfaces. Before they are brought into contact with each other.

[0022]

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, after the first disk is externally fitted on the rotating shaft, a plurality of balls constituting the ball spline are connected to both the inner diameter side and the outer diameter side. The work of inserting between the ball spline grooves and the work of mounting the locking ring on the inner peripheral surface of the first disk can be performed. Therefore, extra work such as bonding the plurality of balls to the outer-diameter-side ball spline grooves is unnecessary, and the assembling work of the toroidal-type continuously variable transmission is facilitated.

[0024]

1 to 7 show an embodiment of the present invention. The feature of the present invention is to facilitate the work of mounting the input disk 2B, which is the first disk, around the input shaft 15 that is the rotating shaft via the ball spline 40. In the structure. Since the structure and operation of the other parts are the same as those of the above-described conventional structure, overlapping illustration and description will be omitted or simplified, and the following description will focus on features of the present invention.

A small-diameter portion 51 is formed over the entire circumference on the outer peripheral surface of the intermediate portion of the input shaft 15 between the input side disk 2B and the output side disk 4 facing the input side disk 2B. Has formed. The step h (see FIG. 2) between the outer peripheral surface of the small-diameter portion 51 and a portion of the outer peripheral surface of the input shaft 15 deviating from the small-diameter portion 51 is larger than the width W ₅₀ of the locking ring 50 in the diameter direction. It is large (h> W ₅₀ ). The locking ring 50 is formed in a partially annular shape by an elastic material such as stainless steel spring, synthetic resin having oil resistance and heat resistance, and imparts elasticity in a direction of expanding the diameter in a free state. .

On the other hand, a locking groove 49 is provided on the inner peripheral surface of the input disk 2B near the inner surface 2a of the input disk 2B (to the left of FIGS. 1 to 7).
Is formed over the entire circumference in a state of crossing the inner diameter side ball spline groove 46 formed on the inner peripheral surface at right angles. The locking ring 50 is attached to the locking groove 49 through the small diameter portion 51 in a state where the inner diameter side opening of the locking groove 49 and the small diameter portion 51 are aligned.

In the illustrated example, the inner diameter side opening of the locking groove 49 and the small diameter portion 51 define the rolling surfaces of the rollers 12, which are a plurality of rolling elements constituting the pressing device 9. One side of the cam plate 10, which is one cam surface (left side in FIGS. 1, 3, and 5)
(The axial movement amount of the input-side disk 2B) before abutting the cam surface 13 formed on the input-side disk 2B and the protrusion of the cam surface 14 formed on the outer surface of the input-side disk 2B as the second cam surface. Are less than or equal to the cam lift amount by the pressing device 9). In this manner, the relationship between the heights of the protrusions of the cam surfaces 13 and 14 and the positions where the locking grooves 49 and the small-diameter portions 51 are formed is determined by connecting the input disk 2B to the shaft of the input shaft 15. This is because the pressing device 9 can be used to move in the direction. That is, the operation of moving the input side disk 2B in the axial direction of the input shaft 15 in order to mount the locking ring 50 in the locking groove 49 is performed by rotating the cam plate 10 constituting the pressing device 9. In order to be able to do it with light power.

In the illustrated example, a locking groove 49a is formed on the outer peripheral surface of the intermediate portion of the input shaft 15 at an end opposite to the outer diameter side ball spline groove 47 with respect to the small diameter portion 51, A locking ring 50a is mounted in the locking groove 49a.
The locking ring 50a has elasticity in the direction of reducing the outer diameter in a free state, contrary to the locking ring 50. The locking ring 50a has a role of preventing the plurality of balls 48 from coming off the outer surface of the input side disk 2B.

In the case of the toroidal-type continuously variable transmission of the present invention having the above-described configuration, the input side disk 2B is externally fitted to the input shaft 15, and then the plurality of ball splines 40 are formed. The operation of inserting the balls 48, 48 between the inner diameter side and the outer diameter side ball spline grooves 46, 47, and the locking ring 5 on the inner peripheral surface of the input side disk 2B.
The work of mounting 0 can be performed. That is, the operation of assembling the structure of the present invention as described above is performed as follows. still,
This assembling work is performed on the inner side surface 2a of the input side disk 2B.
Is preferred because gravity acts in a direction to calm down each member.

A locking ring 50a is previously mounted in a locking groove 49a provided on the outer peripheral surface of the intermediate portion of the input shaft 15. In this state, the outer peripheral edge of the locking ring 50a is
Does not protrude from the outer peripheral surface. Therefore, the input shaft 1
5, the components of the pressing device 9 and the input side disk 2B are externally fitted. At this time, the input side disk 2B
Does not yet have the locking ring 50 attached thereto. Then, the input side disc 2B is externally fitted to the input shaft 15, and the two ball spline grooves 46, 47 are aligned in a state where the inner and outer diameter ball spline grooves 46, 47 are aligned with each other.
The plurality of balls 48, 48 are inserted between 47.

Next, as shown in FIGS. 3 and 4, the cam plate 10 of the pressing device 9 is rotated to rotate the input side disk 2.
B in the axial direction of the input shaft 15, and
9 is opened to the small diameter portion 51. Then, the locking ring 50 is fitted through the small-diameter portion 51 into a portion of the input side disk 2B near the inner peripheral surface 2a, and the locking ring 50 and the locking groove 49 are aligned.
Then, due to the elasticity of the locking ring 50 itself, the locking ring 50 and the locking groove 49 are engaged as shown in FIGS. When the locking ring 50 is mounted in the locking groove 49 in this manner, the balls 48, 48 contacting the locking ring 50a are used.
Is not exposed from the outer surface of the input side disk 2B, or if it is exposed, only less than half the diameter is exposed. The reason for this is that, when attaching the locking ring 50,
This is to prevent the balls 48, 48 from falling off the outer surface of the input side disk 2B.

After the locking ring 50 is mounted in the locking groove 49 as described above, the cam plate 10 is rotated in the opposite direction (or further in the same direction) to rotate the rollers 12 and 12.
Are brought into contact with the concave portions of the cam surfaces 13 and 14. As a result, the locking groove 49 does not come off from the small diameter portion 51, and the locking ring 50 does not fall out of the locking groove 49.
The toroidal-type continuously variable transmission of the present invention is constructed as described above, and is assembled as described above. Therefore, extra work such as bonding the plurality of balls 48 to the outer-diameter-side ball spline groove 47 is performed. Becomes unnecessary, and the assembling work becomes easy.
The trunnions 6, 6 and the power rollers 8, 8 (FIG. 12)
13) Insert the plurality of balls 48, 48 constituting the ball spline 40 as described above between the inner and outer diameter ball spline grooves 46, 47, and simultaneously input the disc 2B After the locking ring 50 is mounted on the inner peripheral surface of the device, it is mounted on a predetermined portion.

[0033]

The toroidal type continuously variable transmission according to the present invention is constructed and operates as described above. Therefore, the rotary shaft such as the input shaft and the first disk such as the input side disk are connected via the ball spline. Work becomes easier. For this reason, the assembling work of the toroidal type continuously variable transmission incorporating the ball spline can be streamlined, and the toroidal type continuously variable transmission can be reduced in cost.

[Brief description of the drawings]

FIG. 1 is an essential part cross-sectional view showing an example of an embodiment of the present invention in a state where an input shaft and an input side disk are combined via a ball spline.

FIG. 2 is an enlarged cross-sectional view of the central part of FIG.

FIG. 3 is an essential part cross-sectional view showing an example of the embodiment of the present invention in a state where the input shaft and the input-side disk are being combined via a ball spline.

FIG. 4 is an enlarged cross-sectional view of the center upper part of FIG. 3;

FIG. 5 is an essential part cross-sectional view showing a state following the state shown in FIG. 3;

FIG. 6 is an enlarged cross-sectional view of the center upper part of FIG. 5;

FIG. 7 is a sectional view similar to FIG. 6, showing a state following the state of FIG. 6;

FIG. 8 is a side view showing a basic configuration of a conventionally known toroidal-type continuously variable transmission in a state of maximum deceleration.

FIG. 9 is a side view showing a state at the time of maximum speed increase.

FIG. 10 is a sectional view showing a first example of a conventional specific structure.

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

FIG. 12 is a partial cross-sectional view showing a second example of a conventional specific structure.

FIG. 13 is a partial sectional view showing the third example.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Input shaft 2, 2A, 2B Input side disk (1st disk) 2a Inner surface 3 Output shaft 4 Output side disk (2nd disk) 4a Inner surface 5 Pivot 6, 6A Trunnion 7 Displacement axis 8 Power roller 8a circumference Surface 9 Pressing device 10 Cam plate 11 Cage 12 Roller 13, 14 Cam surface 15 Input shaft 16 Needle bearing 17 Flange 18, 18 a Output gear 19 Key 20 Support plate 21 Support shaft 22 Pivot shaft 23 Round hole 24 25 Radial needle bearing 26 Thrust ball bearing 27 Thrust needle bearing 28 Cage 29 Ball 30 Outer ring 31 Race 32 Cage 33 Needle 36 Driving rod 37 Driving piston 38 Driving cylinder 39 Loading nut 40, 40a Ball spline 41 Disc spring 42 Thrust needle Bearing 43 angular contact type ball shaft 44 partition wall 45 servings plate spring 46 the inner diameter side ball spline groove 47 outer diameter side ball spline groove 48 ball 49,49a locking grooves 50,50a retaining ring 51 the small diameter portion

Claims (1)

[Claims] 1. A rotation shaft and a support around a middle portion of the rotation shaft through a ball spline, whereby a displacement in an axial direction with respect to the rotation shaft and a rotation synchronized with the rotation shaft can be freely performed. A disk, a second disk which is supported around the intermediate portion of the rotating shaft in a state where the first disk and the inner surface face each other, and which can freely rotate relative to the rotating shaft, and It consists of a trunnion that swings about a pivot in a torsion position, a support shaft and a pivot shaft that are eccentric to each other, and among these, the support shaft is rotatably supported by the trunnion, and the pivot is With the displacement shaft protruding from the inner surface of the trunnion, and the first and the second, while being rotatably supported around the pivot shaft portion,
A power roller sandwiched between the inner surfaces of the second disks, and provided between a part of the rotating shaft and the first disk, and the first disk is attached to the second disk. A loading cam-type pressing device for rotating the first disk while pressing the first disk, wherein the ball spline includes an inner-diameter-side ball spline groove formed on an inner peripheral surface of the first disk; An outer-diameter-side ball spline groove formed on an outer peripheral surface of an intermediate portion of the first disk, a plurality of balls rotatably provided between the two ball spline grooves, and an inner surface of an inner peripheral surface of the first disk. A locking groove formed in the deviating portion, and a locking ring which locks in the locking groove to limit displacement of the plurality of balls toward the inner surface of the first disk. For a toroidal-type continuously variable transmission There are, the first at an intermediate portion outer peripheral surface of the rotary shaft, provided with a small-diameter portion between the second disk each other while being aligned with the opening of the engagement groove and the small diameter portion,
A toroidal-type continuously variable transmission, wherein the locking ring is freely attachable to the locking groove through the small diameter portion.