JP2000213610A - Toroidal continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve efficiency of assembling work so as to lower a production cost while securing transmittable torque by preventing respective balls from falling off from respective spline grooves by means of a plurality of projections protruding to a pressing device side formed in a part matching the respective ball spline grooves. SOLUTION: In a locking ring 45, projection parts 47, 47 and arc parts 48, 48 connecting the base end parts of the adjacent projection parts 47, 47 together in the circumference direction are alternately continued in the circumference direction so as to form a ring shape as a whole. The locking ring 45 is provided with elasticity in the diameter shrinking direction by resiliency of the respective parts 47, 48. The inside diameter of the locking ring 45 in a free condition is smaller than the outside diameter of a locking groove forming part in a part of an input shaft. In this way, respective arc parts 48, 48 constituting the locking ring 45 are locked in the locking grooves without any backlash by resiliency of the locking ring 45 itself, and under the locked condition, the respective projection parts 47, 47 are engaged with the opening parts of the respective groove parts, preventing the locking ring 45 from rotating with respect to the input shaft.

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 supports an input side disk (first disk) 2 concentrically with an input shaft 1 which is a rotating shaft, as disclosed in, for example, Japanese Utility Model Laid-Open Publication No. 62-71465. An output disk (second disk) 4 is fixed to an end of an output shaft 3 arranged concentrically with the input shaft 1. Inside the casing containing the toroidal-type continuously variable transmission, there is no intersection with the input shaft 1 and the output shaft 3 but in a twist position that is perpendicular to the direction of the center axis of these two shafts. Trunnions 6 and 6 that swing about certain pivots 5 and 5 are 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 respective displacements can be adjusted. The inclination angles of the shafts 7, 7 can be adjusted freely. Power rollers 8 are rotatably supported around the displacement shafts 7 supported by the trunnions 6 respectively. 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 cross section forms a concave surface obtained by rotating an arc about a point on the pivot 5. Then, the peripheral surfaces 8a, 8 of the power rollers 8, 8 formed on the spherical convex surface
a is in contact with the inner side surfaces 2a, 4a.

[0004] A loading device 9 of a loading cam type is provided between the input shaft 1 and the input disk 2, and the input disk 2 is directed toward the output disk 4 by this pressing device 9 so as to be elastic. It can be pressed freely. The pressing device 9 includes a cam plate 10 that rotates together with the input shaft 1, and a plurality (for example, four) of rollers 12, which are rotatably held by a holder 11. The cam plate 10
On one side surface (left side surface in FIGS. 7 and 8), 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. 7 and 8).
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 rotate. 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, 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. 8, each of these displacement shafts a and 8a comes into contact with a portion of the inner surface 2a of the input disk 2 near the outer periphery and a portion of the inner surface 4a of the output disk 4 near the center. Tilt 7,7. If the inclination angle of each of the displacement shafts 7, 7 is set between those in FIGS. 7 and 8, the input shaft 1 and the output shaft 3
, An intermediate speed ratio can be obtained.

FIGS. 9 to 10 show Japanese Utility Model Application No. 63-6929.
3 shows an example of a more specific toroidal-type continuously variable transmission described in the microfilm of No. 3 (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. 9) 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. The output side disk 4 is provided with an output gear 18 and a key 1.
The output side disk 4 and the output gear 18 rotate in synchronization with each other.

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. 9, and left and right directions in FIG. 10). 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. 10, the left and right directions are reversed). The eccentric direction is
The direction is substantially orthogonal to the axial direction of the input shaft 15 (the left-right direction in FIG. 9 and the front-back direction in FIG. 10). Therefore,
The power rollers 8 are supported so as to be slightly displaceable in the direction in which the input shaft 15 is disposed. As a result, the power rollers 8, 8 tend to be displaced in the axial direction of the input shaft 15 due to elastic deformation of the constituent members based on a large load applied to the constituent members in the state of transmission of the rotational force. In this case, the displacement can be absorbed without applying excessive 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. In addition, each of the above thrust needle bearings 2
7 and 27, while supporting the thrust load applied from the power rollers 8 and 8 to the outer rings 28 and 28 constituting the thrust ball bearings 26 and 26, respectively,
2 and these outer races 28, 28
Swinging around 1 is allowed.

Further, drive rods 29, 29 are provided at one end (the left end in FIG. 10) of each of the trunnions 6, 6, respectively.
And drive pistons 30, 30 are fixedly mounted on the outer peripheral surfaces of the intermediate portions of these drive rods 29, 29. And
These drive pistons 30, 30 are oil-tightly fitted in drive cylinders 31, 31, respectively.

In the case of the toroidal type continuously variable transmission configured as described above, the rotation of the input shaft 15 is transmitted to the input side disk 2 via the pressing device 9. Then, the rotation of the input side disk 2 is transmitted to the output side disk 4 via the pair of power rollers 8, 8, and further, the output side disk 4
Is taken out from the output gear 18. Input shaft 15
When changing the rotation speed ratio between the output gear 18 and
The pair of drive pistons 30, 30 are displaced in directions opposite to each other. The pair of trunnions 6 are displaced in opposite directions with the displacement of the driving pistons 30, 30. 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. 7 and 8 described above, the contact position between the peripheral surfaces 8a, 8a of the power rollers 8, 8 and the inner surfaces 2a, 4a changes, and the input shaft 15 The rotation speed ratio with the output gear 18 changes.

The input shaft 15 and the output gear 1 are
When transmitting the rotational force to the power rollers 8, the power rollers 8, 8 are displaced in the axial direction of the input shaft 15 based on the elastic deformation of the constituent members. Each of the displacement shafts 7 pivotally supporting the pivot 8 slightly rotates around the support shaft portions 21. As a result of this rotation, the outer ring 28 of each of the thrust ball bearings 26, 26,
The outer surface of the trunnion 6 and the inner 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 disks 2A and 2B and two output disks 4 and 4 are arranged in parallel with respect to the power transmission direction has also been conventionally known, for example, as described in JP-A-6-280957. Are known. Each of the structures shown in FIGS.
An output gear 18a is supported around an intermediate portion of the output gear 5 so as to freely rotate with respect to the input shaft 15, and the output disks 4 are mounted on both ends of a cylindrical portion provided at the center of the output gear 18a. Is 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. 11 to 12) has a rear surface (left side in FIGS. 11 to 12) directly on the loading nut 32 (in the case of the structure shown in FIG. 12) or large. The input shaft 15 is brought into contact with an elastic disc spring 33 in the case of the structure shown in FIG.
In the axial direction (the left-right direction in FIGS. 11 to 12). 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 34 so as to be displaceable in the axial direction. Then, the rear surface of the input side disk 2B (FIG. 11)
12 and the front surface of the cam plate 10 (the left surface of FIGS. 11 to 12).
And are provided in series with each other. Plate spring 3 of these
5 is the 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 36 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. 11, the output gear 18a is provided on a partition wall 37 provided inside the housing.
In addition, a pair of angular ball bearings 38, 38 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. 12, the displacement of the output gear 18a in the axial direction is free. As shown in FIGS. 11 to 12, the 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 and 2B facing the cam plate 10 on the input shaft 15 by the ball splines 34 and 34a so as to be freely 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 34, 34a installed for the above-described purpose are provided on the inner diameter side ball spline grooves 39 formed on the inner peripheral surfaces of the input side disks 2A, 2B and on the outer peripheral surface of the intermediate portion of the input shaft 15. The formed outer diameter side ball spline groove 40 and these two ball spline grooves 39, 4
A plurality of balls 4 provided so as to freely roll between 0
1 and 41. As for the ball spline 34 for supporting the input side disk 2B on the pressing device 9 side, a locking ring 43 is formed in a locking groove 42 formed on the inner peripheral surface of the input side disk 2B near the inner side surface 2a. Lock the
The plurality of balls 41 are connected to the input side disk 2.
A and 2B are restricted from being displaced toward the inner side surface 2a.
Then, the balls 41, 41 are prevented from falling out from between the inner diameter side and outer diameter side ball spline grooves 39, 40. In the structure shown in FIG. 11, the ball spline 34a for supporting the input disk 2A remote from the pressing device 9 is related to the locking groove 42a formed on the outer peripheral surface of the intermediate portion of the input shaft 15. The retaining ring 43a is locked to limit displacement of the plurality of balls 41, 41 toward the inner side surface 2a of the input side disk 2A.

Each of the ball splines 34, 34 as described above
The operation of assembling the ball spline 34 on the pressing device 9 side is performed as shown in FIGS. First, as shown in FIG. 13, the base end of the input shaft 15 (FIGS.
The cam plate 10 and the rollers 12, which constitute the pressing device 9, are assembled to the lower end of the pressing device 9. In this state, the plurality of balls 41, 41 are inserted into the outer diameter side ball spline grooves 40 formed near the base end of the intermediate portion of the input shaft 15.
Is lightly adhered with grease. Then, in this state, the input side disk 2B is put on the input shaft 15 near the base end of the input shaft 15 as shown in FIG. 14 while engaging the balls 41, 41 with the inner diameter side ball spline grooves 39. . The operation of locking the locking ring 43 in the locking groove 42 formed on the inner peripheral surface of the input side disk 2B is performed before fitting the input side disk 2B to the input shaft 15 or Is performed through a small diameter portion 44 formed at the intermediate portion of the input shaft 15 after the external fitting.

[0019]

The operation of bonding the balls 41, 41 to the outer-diameter-side ball spline groove 40 with grease is performed by engaging a locking ring 43 with a locking groove 42 formed on the inner peripheral surface of the input side disk 2B. It is necessary only for assembling with the 装着 attached. As described above, there is a work that is merely necessary for the assembling work and is not necessary from the original function of the toroidal-type continuously variable transmission. The work of externally fitting the input side disk 2B to the input shaft 15 is troublesome, and increases the manufacturing cost of the toroidal-type continuously variable transmission.

Moreover, the balls 41, 41, which have only been adhered to the outer diameter side ball spline grooves 40 by grease, easily fall off. If the ball spline 34 is assembled without noticing that it has fallen, the function of the ball spline 34 is impaired, or the load capacity of the ball spline 34 becomes insufficient, and the durability of the ball spline 34 becomes insufficient. Could be. Further, the dropped balls 41, 41
Is pushed into the pressing device 9, the pressing device 9
The operation of the toroidal-type continuously variable transmission is adversely affected, for example, the operation of the toroidal type continuously variable transmission is impaired.

The operation of locking the locking ring 43 in the locking groove 42 is performed after the input side disk 2B is fitted to the input shaft 15 outside.
If the operation is performed through the small-diameter portion 44 formed at the intermediate portion of the input shaft 15 (see Japanese Patent Application No. 9-90295 for details), the above-mentioned inconvenience can be solved. Rigidity decreases. That is, the small diameter portion 4
4, the cross-sectional area of the input shaft 15 is reduced, so that the torsional rigidity of the input shaft 15 is reduced, and a pair of input-side disks 2 supported at both ends of the input shaft 15 are formed.
A, 2B rotation synchronism falls. For this reason, it may be difficult to adopt a toroidal type continuously variable transmission for transmitting a large torque. The toroidal-type continuously variable transmission of the present invention has been invented in order to eliminate any of these disadvantages.

[0022]

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, the first disk has a displacement in the axial direction with respect to the rotation axis and is capable of rotating in synchronization with the rotation axis, and the rotation of the rotation shaft is performed in a state where the first disk and the inner surface face each other. Around the intermediate portion, a second disk that freely supports relative rotation with respect to the rotation axis, and a twist position that does not intersect with the rotation axis but is perpendicular to the direction of the center axis of the rotation axis. A trunnion that swings about a pivot shaft, a support shaft portion and a pivot shaft portion that are eccentric to each other, the support shaft portion of which is rotatably supported by the trunnion, and the pivot shaft portion of the trunnion. Inside A displacement shaft which projects from a state which is rotatably supported around the pivot shaft portion, the first,
A power roller sandwiched between the inner surfaces of the second two disks, provided between a part of the rotation shaft and the first disk, while pressing the first disk toward the second disk And a pressing device that rotationally drives the first disk. 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 these two ball spline grooves. A plurality of balls rotatably provided therebetween, and a locking ring for limiting the plurality of balls from being displaced toward the inner surface of the first disk.

In particular, in the toroidal type continuously variable transmission according to the present invention, the locking ring is provided so that at least the pressing device does not press the first disk on the outer peripheral surface of the intermediate portion of the rotating shaft. It is locked at a portion exposed on the inner side of one disk. A plurality of projections projecting toward the pressing device are formed in a portion of the locking ring in the circumferential direction that is aligned with each of the ball spline grooves. Each of the balls is prevented from falling off from each of the spline grooves.

[0024]

The toroidal-type continuously variable transmission of the present invention having the above-described structure has a rotational force between the first disk and the second disk based on the same operation as the above-mentioned conventional toroidal-type continuously variable transmission. By 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 according to the present invention, the ball is formed after the first disk is fitted onto the rotary shaft without providing a small diameter portion on the outer peripheral surface of the intermediate portion of the rotary shaft. The operation of inserting a plurality of balls constituting the spline between the inner and outer diameter ball spline grooves, and the operation of attaching a locking ring to the locking groove formed on the outer peripheral surface of the input shaft. You. 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. Further, it is possible to realize a toroidal-type continuously variable transmission capable of transmitting a large torque without sufficiently increasing the weight, by sufficiently securing the torsional rigidity of the rotating shaft.

[0026]

1 to 6 show an embodiment of the present invention. A feature of the present invention is a structure for facilitating the work of mounting the input disk 2B as the first disk around the input shaft 15 as the rotating shaft via the ball spline 34. It is in. 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 locking groove 46 for locking the locking ring 45 is formed in the intermediate portion of the input shaft 15 over the entire circumference so as to cross the outer diameter side ball spline groove 40. The position of the locking groove 46 in the axial direction is regulated so that the locking operation of the locking ring 45 can be performed even when the input side disk 2B is externally fitted to the input shaft 15. That is, as shown in FIGS. 1 and 2, the loading cam type pressing device 9 is most contracted, and this pressing device 9 is connected to the input side disk 2B.
Is formed in a portion exposed on the inner side surface 2a side (the upper side in FIGS. 1 to 3) of the input side disk 2B without pressing.

A locking ring 45 for locking in such a locking groove 46
Is formed into a shape as shown in FIG. 5 by bending an elastic wire such as spring steel. In other words, the locking ring 45 has convex portions 47, 47, each of which is U-shaped and protrudes in the axial direction, and circular arc portions 48, 48 connecting the base ends of the convex portions 47, 47 adjacent in the circumferential direction. Are alternately continued in the circumferential direction to form an entire ring. Such locking ring 45 gives elasticity in the direction of reducing the diameter by the elasticity of the above-described portions 47 and 48.
The inner diameter of the locking ring 45 in the free state is smaller than the outer diameter of a part of the input shaft 15 where the locking groove 46 is formed (both side edges of the locking groove 46). The outer diameter of the wire constituting the locking ring 45 is the same as or slightly smaller than the width of the locking groove 46. Further, the width of each of the convex portions 47 is equal to the outer diameter side ball spline groove 4.
The width of each of the grooves constituting the zero is equal to or slightly smaller than the width of the opening. Therefore, the locking ring 4
The arcuate portions 48, 48 constituting the lock 5 are locked by the elasticity of the locking ring 45 itself without rattling in the locking groove 46. In the locked state, the convex portions 47, 47 The engagement with the openings of the respective grooves prevents the locking ring 45 from rotating with respect to the input shaft 15.

With the locking ring 45 locked in the locking groove 46 as described above, each of the projections 47 projects toward the balls 41 forming the ball spline 34. Each ball 41, 41 constitutes this ball spline 34, both inner diameter side and outer diameter side spline grooves 3.
9 and 40 are prevented from falling off. That is, each of the convex portions 47 is in a state where the pressing device 9 is most contracted.
Although it is most exposed outside the space between the outer peripheral surface of the input shaft 15 and the inner peripheral surface of the input side disk 2B, even in this state,
The balls 41 are prevented from falling out of this space. For this reason, even when the pressing device 9 is in the most contracted state, the balls 41, 41 abutting on the tips of the respective convex portions 47, 47 are not exposed from the outer surface of the input side disk 2B or are temporarily exposed. However, only less than half the diameter should be exposed. However, as shown in FIG. 3, even when the pressing device 9 is in the widest position, there is a slight gap between the balls 41, 41 and the tips of the convex portions 47, 47. I do. The reason is that each of the balls 41, 4
1 strongly presses each of the convex portions 47, 47, and
This is to prevent the falling off from the locking groove 46.

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 34 are formed. The operation of inserting the balls 41, 41 between the inner and outer diameter ball spline grooves 39, 40, and the locking groove 4 formed on the outer peripheral surface of the input shaft 15
The work of attaching the locking ring 45 to the work 6 can be performed. That is, the operation of assembling the structure of the present invention as described above is performed as follows. This assembling work is performed by the input side disk 2B.
It is preferable that the inner side surface 2a be set upward because gravity acts in a direction to calm down each member.

A locking ring 43b is mounted in advance on a locking groove 42b provided on the outer peripheral surface of the intermediate portion of the input shaft 15 near the base end. In this state, the outer peripheral edge of the locking ring 43b does not protrude from the outer peripheral surface of the input shaft 15. Then, as shown in FIG. 6, the constituent members of the pressing device 9 and the input side disk 2B are externally fitted to the input shaft 15. At this time, the locking ring 45 is not yet mounted on the locking groove 46 formed on the outer peripheral surface of the input shaft 15. Then, the input side disk 2B is fitted to the input shaft 15 outside, and the inner and outer diameter side ball spline grooves 39, 4
0, the plurality of balls 41, 41 are placed between the two ball spline grooves 39, 40.
Insert Next, as shown in FIGS. 1 and 2, the locking ring 45 is locked in the locking groove 46 with the respective convex portions 47, 47 facing the respective balls 41, 41.

The toroidal-type continuously variable transmission of the present invention is constructed as described above and is assembled as described above.
Even if a small-diameter portion is not formed in 5, the extra work such as bonding the plurality of balls 41 to the outer-diameter-side ball spline groove 40 becomes unnecessary, and the assembling work becomes easy.

[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 input side disk etc. are not reduced without reducing the torsional rigidity of the rotary shaft such as the input shaft. The operation of combining the first disc with the first disc via a ball spline is facilitated. Therefore, the assembling work of the toroidal type continuously variable transmission incorporating the ball spline can be streamlined, and the torque that can be transmitted can be secured, 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 which an input shaft and an input side disk are combined via a ball spline and a pressing device is most contracted;

FIG. 2 is an enlarged sectional view of the lower part of FIG.

FIG. 3 is a view similar to FIG. 2, showing the pressing device in the most expanded state.

FIG. 4 is a side view showing the input shaft and the locking ring.

FIG. 5 is a perspective view of a locking ring.

FIG. 6 is a view similar to FIG. 1, showing a state before a ball is inserted;

FIG. 7 is a side view showing a basic configuration of a conventionally known toroidal type continuously variable transmission in a state of maximum deceleration.

FIG. 8 is a side view similarly showing a state at the time of maximum speed increase.

FIG. 9 is a sectional view showing a first example of a conventional specific structure.

FIG. 10 is a sectional view taken along line AA of FIG. 9;

FIG. 11 is a partial cross-sectional view showing a second example of a conventional specific structure.

FIG. 12 is a partial cross-sectional view showing the third example.

FIG. 13 is a sectional view showing a state in which a ball spline having a conventional structure is being assembled.

FIG. 14 is a sectional view showing a state in which the assembling is completed.

[Explanation of symbols]

 Reference Signs List 1 input shaft 2, 2A, 2B input side disk (first disk) 2a inner surface 3 output shaft 4 output side disk (second disk) 4a inner surface 5 pivot 6, 6A trunnion 7 displacement axis 8 power roller 8a peripheral 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 Outer ring 29 Drive rod 30 Drive piston 31 Drive cylinder 32 Loading nut 33 Disc spring 34, 34a Ball spline 35 Disc spring 36 Thrust needle bearing 37 Partition wall 38 Angular ball bearing 39 Inside diameter ball spline groove 4 Outer diameter side ball spline groove 41 ball 42, 42a, 42b engaging grooves 43 and 43a, 43 b retaining ring 44 the small diameter portion 45 retaining ring 46 engaging groove 47 protrusion 48 arcuate 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. Disk, around the intermediate portion of the rotating shaft with the first disk and the inner surface facing each other,
A second disk that freely supports relative rotation with respect to the rotation axis and a pivot axis that is not intersecting with the rotation axis but is in a twisted position that is perpendicular to the direction of the center axis of the rotation axis. A supporting shaft portion and a pivot shaft portion which are eccentric to each other, and the supporting shaft portion is rotatably supported by the trunnion, and the pivot shaft portion is projected from the inner surface of the trunnion. Displacement axis,
A power roller sandwiched between inner surfaces of the first and second disks while being rotatably supported around the pivot shaft; a part of the rotation shaft and the first disk; And a pressing device for rotating the first disk while pressing the first disk toward the second disk, wherein the ball spline is formed on an inner peripheral surface of the first disk. An inner-diameter-side ball spline groove, an outer-diameter-side ball spline groove formed on an outer peripheral surface of an intermediate portion of the rotating shaft, and a plurality of balls provided rotatably between the two ball spline grooves; In a toroidal-type continuously variable transmission, which comprises a plurality of balls for limiting displacement of the plurality of balls toward the inner side of the first disk, the locking ring is provided at an intermediate position of the rotating shaft. At least on the outer peripheral surface The pressing device is locked to a portion exposed on the inner surface side of the first disk without pressing the first disk, and each of the ball spline grooves is formed in a part of the locking ring in a circumferential direction. The part that matches
A plurality of protrusions protruding toward the pressing device are formed, and the respective protrusions prevent the balls from falling off from the spline grooves. transmission.