JP2002048206A - Half-toroidal type none-stage transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a half-toroidal type non-stage transmission which is not only superior in processability and simple to manufacture, but also enables reduction in weight. SOLUTION: In a half-toroidal type non-stage transmission, which by the inclined revolution of a power roller 9 arranged in between input discs 4, 5 and output discs 6, 7 that are positioned to face each other, is constituted of the gear ratio between input discs and output discs changes without stages, output discs 6, 7 consisting of two output discs that are positioned back to back and a power transmission gear 20 is put between the two output discs and fixed by such a tightening device as a bolt 24 and a nut 25 and the like.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a half toroidal type continuously variable transmission used as a transmission for an automobile or a transmission for various industrial machines.

[0002]

2. Description of the Related Art In recent years, toroidal-type continuously variable transmissions have been used as transmissions for automobiles or transmissions for various industrial machines. In this toroidal-type continuously variable transmission, for example, as disclosed in Japanese Patent Application Laid-Open No. H11-63139, two pairs of disks are provided, and these two disks are arranged along the axial direction. The sets of mutually adjacent output disks are integrated. Further, a power transmission gear is fixed to an outer peripheral edge of the integrated output disk.

The output disk is carburized to increase the thickness of the carburized tissue layer, and the gear is carburized to reduce the thickness of the carburized tissue layer, and the output disk and the gear are welded and integrated. It is.

According to the above configuration, the length of the variator in the axial direction can be reduced by integrating the output disks. Further, since the loading force acting on the output disk is offset, there is an advantage that the thickness of the disk can be reduced.

[0005]

However, when the output disks are integrated, processing becomes difficult because both surfaces are toroidal surfaces. Further, since the required heat treatment characteristics (depth of the carburized hardened layer) are different between the disk and the gear, it is difficult to manufacture a completely integrated type. Actually, as described above, they are separately manufactured, carburized, and then joined by welding. Further, it is necessary to separate the welded portion from the toroidal surface in order to prevent a problem such as a decrease in hardness due to deformation due to heat or tempering.

[0006] Furthermore, if the carbon concentration increases due to carburization, welding cracks and the like become a problem and it becomes difficult to join by welding. Therefore, it is necessary to remove the carburized layer at the time of welding. It causes cost increase such as shortening of service life.

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and has as its object to be easy to process, easy to manufacture and light in weight, and suitable for disks and gears respectively. It is an object of the present invention to provide a half toroidal type continuously variable transmission which can easily perform heat treatment.

[0008]

In order to achieve the above object, the present invention is directed to a first aspect of the present invention wherein both power disks are tilted by interposing a power roller between an input disk and an output disk disposed opposite to each other. In a half-toroidal type continuously variable transmission configured such that a speed ratio between the output disks varies steplessly, the output disks are arranged in a back-to-back arrangement.
And a power transmission gear interposed between the two output disks and fixed.

A second aspect of the present invention is characterized in that the two disks and the power transmission gear of the first aspect are restrained at least in a rotational direction.

According to the above configuration, the output disk and the power transmission gear can be separately processed and subjected to optimal heat treatment, and then both can be combined. Further, since the two disks are constantly pressed against each other from both sides by the loading force, there is no need to restrain the two disks and the power transmission gear in the axial direction. It only has to be restrained.

[0011]

Embodiments of the present invention will be described below with reference to the drawings.

FIGS. 1 and 2 show a first embodiment. FIG. 1 is a longitudinal sectional side view of a double-cavity half-toroidal type continuously variable transmission, and FIG. is there. As shown in FIG. 1, a power transmission shaft 1 as a main shaft
, A front side cavity 2 and a rear side cavity 3 are coaxially arranged. These cavities 2 and 3 have a pair of input disks 4 and 5 and a pair of output disks 6 and 7, and are provided between the input disk 4 and the output disk 6 and between the input disk 5 and the output disk 7. Power rollers 8, 9 that transmit power by friction are rotatably contacted with each other.

Input disk 4 in front side cavity 2
Is rotationally engaged with the power transmission shaft 1 by a ball spline 10 and is movable in the axial direction. The input disk 5 of the rear cavity 3 is integrally connected to the power transmission shaft 1 and is prevented from coming off by a loading nut 11. Further, the output disk 6 of the front side cavity 2 and the output disk 7 of the rear side cavity 3 are coupled in a back-to-back state to a fitting cylinder 13 rotatably fitted to the power transmission shaft 1.

Further, a loading cam 14 for pressing the input disks 4, 5 against the output disks 6, 7 via the power rollers 8, 9 is fitted on the input side of the power transmission shaft 1. A roller 15 is provided between the loading cam 14 and the input disk 4 of the front variator 2.

A flange 16 is provided at an end of the power transmission shaft 1 which penetrates the loading cam 14 and protrudes toward the input side, and a concave portion 17 is provided on the loading cam 14 facing the flange 16. ing. An annular gap 18 is provided between the flange 16 and the recess 17. A preload mechanism 19 for applying a preload to both input disks 4 and 5 toward the corresponding output disks 6 and 7 is provided inside the annular gap 18. That is, the preload mechanism 19
Are arranged at right angles to the axial direction of the power transmission shaft 1.

The two output disks 6 and 7 are configured as shown in FIG. That is, the output disks 6, 7 are arranged back to back, and the toroidal surfaces 6a, 7
The rear surfaces 6b and 7b opposite to the side a are gradually thinned toward the axial center, thereby reducing the weight of the output disks 6 and 7.

The back surfaces 6b, 7 of the output disks 6, 7
A power transmission gear 20 is interposed on the outer peripheral portion between the positions b. The power transmission gear 20 has a ring shape having a substantially T-shaped cross section, and has an outer peripheral portion 2 fitted to the outer periphery of the output disks 6 and 7.
The inner peripheral surface at 0a and the outer peripheral surfaces of the output disks 6 and 7 are spigot-fitted (X in the drawing indicates a spigot portion) for centering. Further, a tooth portion 21 is provided on the outer peripheral surface of the outer peripheral portion 20a, and the inner peripheral portion 20b is provided on the rear surfaces 6b, 7b.
It is interposed between.

Further, a thin portion 22 is provided on the outer peripheral edge of the toroidal surfaces 6a, 7a of the output disks 6, 7 by a step. The thin portion 22 is provided with a bolt hole 23 which faces each other and also penetrates the inner peripheral portion 20b of the power transmission gear 20. A bolt 24 is inserted into the bolt hole 23 from one output disk 6 side, and a nut 25 is screwed into the bolt 24 on the other output disk 7 side. By tightening the nut 25, the output disks 6, 7 and the power transmission gear 20 are restrained in the axial direction and the rotation direction by the bolt 24 and the nut 25. The fastening portions between the bolts 24 and the nuts 25 are provided at, for example, four locations on the circumference of the output disks 6 and 7 at equal intervals.

In the first embodiment, the bolt 24 is inserted into the bolt hole 23 and fastened and fixed by the nut 25. However, a rivet may be inserted into the bolt hole 23 and fixed by rivets.

FIG. 3 shows a first modification of the first embodiment.
The inner peripheral portion 20b of the power transmission gear 20 is formed in a disk shape, and the inner peripheral edge portion 20c is made thick to be interposed between the back surfaces 6b and 7b of the output disks 6 and 7, and the first embodiment. It has the same effect as the form.

FIG. 4 shows a second modification of the first embodiment.
Protruding portions 6c, 7c are provided on the inner peripheral edges of the back surfaces 6b, 7b of the output disks 6 and 7, and have the same effects as in the first embodiment.

FIG. 5 shows a second embodiment, in which the same components as those in the first embodiment have the same reference numerals and description thereof will be omitted.

L-shaped steps 27 facing each other are formed on the outer peripheral portions of the back surfaces 6b and 7b of the output disks 6 and 7, respectively. Further, spline grooves 28 are provided on the outer peripheral surfaces of the output disks 6 and 7. A spline groove 29 that meshes with the spline groove 28 is provided inside the outer peripheral portion 20 a of the power transmission gear 20. Therefore, the output disks 6, 7 and the power transmission gear 20 are restricted in the rotation direction. The two output disks 6, 7
Are always pressed together from both sides by the loading force, the two output disks 6, 7 and the power transmission gear 20 do not need to be restrained in the axial direction, but are restrained at least in the rotational direction as described above. Just do it.

Further, the inner peripheral portion 20b of the power transmission gear 20
Are convex portions 3 that engage with the step portions 27 of the output disks 6 and 7.
0 is provided. The outer peripheral surface of the convex portion 30 and the inner peripheral surface of the step portion 27 of the output disks 6 and 7 are spigot-fitted (X in the drawing indicates the spigot portion) for centering.

FIG. 6 shows a first modification of the second embodiment.
The inner peripheral portion 20b of the power transmission gear 20 is formed in a disk shape, and the inner peripheral edge portion 20c is made thick to be interposed between the back surfaces 6b and 7b of the output disks 6 and 7, and the second embodiment It has the same effect as the form.

FIG. 7 shows a second modification of the second embodiment.
Protrusions 6c, 7c are provided on the inner peripheral edges of the back surfaces 6b, 7b of the output disks 6 and 7, and have the same effects as in the second embodiment.

FIG. 8 shows a third embodiment, in which the same components as those in the first embodiment have the same reference numerals and description thereof will be omitted.

The inner peripheral surface of the outer peripheral portion 20a fitted to the outer periphery of the output disks 6, 7 and the outer peripheral surface of the output disks 6, 7 are spigot-fitted for centering (in the figure, X indicates the spigot portion). Have been. The back surface 6b of the output disks 6, 7,
On the outer peripheral portion of 7b, convex portions 31 facing each other in the radial direction are formed. In addition, concave portions 32 that engage with the convex portions 31 are provided on both side surfaces of the inner peripheral portion 20 b of the power transmission gear 20. Therefore, the output disk 6,
7 and the power transmission gear 20 are restricted in the rotation direction. Since the two output disks 6, 7 are constantly pressed against each other from both sides by the loading force, the two output disks 6, 7 and the power transmission gear 20 do not need to be restrained in the axial direction. As long as it is restricted at least in the rotation direction.

FIG. 9 shows a modification of the third embodiment, in which the inner peripheral portion 20b of the power transmission gear 20 is formed in a disk shape, and the inner peripheral edge portion 20c is made thick to form the output disks 6 and 7, and And between the back surfaces 6b and 7b of the third embodiment, and has the same effect as the third embodiment.

FIG. 10 shows a second modification of the third embodiment, in which convex portions 6c, 7c which are in contact with each other are provided on the inner peripheral edges of the back surfaces 6b, 7b of the output disks 6 and 7, respectively. There is an effect similar to that of the embodiment.

FIGS. 11 (a) and 11 (b) show a fourth embodiment, in which the same components as those in the first embodiment have the same reference numerals and description thereof will be omitted.

The inner peripheral surface of the outer peripheral portion 20a fitted to the outer periphery of the output disks 6, 7 and the outer peripheral surface of the output disks 6, 7 are spigot-fitted for centering. Have been. Further, at least one or more, for example, four engaging projections 33 are provided on the outer peripheral surfaces of the output disks 6 and 7 at 90 ° intervals in the circumferential direction as shown in FIG. An engagement recess 34 that engages with the engagement protrusion 33 is provided inside the outer peripheral portion 20 a of the power transmission gear 20.

Therefore, the output disks 6, 7 and the power transmission gear 20 are restricted in the rotation direction. Since the two output disks 6, 7 are constantly pressed against each other from both sides by the loading force, the two output disks 6, 7 and the power transmission gear 20 do not need to be restrained in the axial direction. As long as it is restricted at least in the rotation direction.

FIGS. 12A and 12B show a first modification of the fourth embodiment, in which the inner peripheral portion 20b of the power transmission gear 20 is formed in a disk shape and the inner peripheral edge portion 20c is made thicker. This is interposed between the back surfaces 6b and 7b of the output disks 6 and 7, and has the same effect as in the fourth embodiment.

FIG. 13 shows a second modification of the fourth embodiment, in which projections 6c and 7c are provided on the inner peripheral edges of the back surfaces 6b and 7b of the output disks 6 and 7 so as to contact each other. There is an effect similar to that of the embodiment.

FIG. 14 shows a fifth embodiment. The same components as those in the first embodiment are denoted by the same reference numerals and description thereof is omitted.

A spline groove 35 is provided on the outer peripheral surfaces of the output disks 6 and 7 on the side of the toroidal surfaces 6a and 7a. A spline groove 36 meshing with the spline groove 35 is provided on an outer inner peripheral surface of the outer peripheral portion 20 a of the power transmission gear 20. Therefore, the output disk 6,
7 and the power transmission gear 20 are restricted in the rotation direction. Since the two output disks 6, 7 are constantly pressed against each other from both sides by the loading force, the two output disks 6, 7 and the power transmission gear 20 do not need to be restrained in the axial direction. As long as it is restricted at least in the rotation direction.

Further, the outer peripheral surfaces of the output disks 6 and 7 on the side of the rear surfaces 6b and 7b and the inner inner peripheral surface of the outer peripheral portion 20a of the power transmission gear 20 are spigot-fitted (X in the figure) for centering. Indicates the spigot part). Therefore, the spline engagement portion and the spigot portion are provided adjacent to each other.

FIG. 15 shows a first modification of the fifth embodiment, in which convex portions 6c, 7c are provided on the inner peripheral edges of the back surfaces 6b, 7b of the output disks 6 and 7, so that they contact each other. There is an effect similar to that of the embodiment.

FIG. 16 shows a second modification of the fifth embodiment, in which the inner peripheral portion 20b of the power transmission gear 20 is formed in a disk shape, and the inner peripheral edge portion 20c is made thicker, and the output disks 6 and 7 are formed. And between the rear surfaces 6b and 7b, which have the same effects as in the fifth embodiment.

[0041]

As described above, according to the present invention, the power transmission gear is sandwiched and fastened between the two output disks arranged back to back, so that the workability is excellent and the manufacture is simple. The weight can be reduced.

In general, a disc is carburized more deeply than usual in order to improve the rolling life of the traction surface and the fatigue crack life, and if the power transmission gear is generally soft and only the surface is hardened, the teeth may be damaged. Although it shows strong characteristics, it becomes harder to the deep part of the gear as a unit as in the past, and it becomes weak against shock input etc.However, since the present invention is a separate disk and gear, There is an effect that heat treatment suitable for each gear can be easily performed.

[Brief description of the drawings]

FIG. 1 is a vertical sectional side view of a half toroidal type continuously variable transmission showing a first embodiment of the present invention.

FIG. 2 is a longitudinal sectional side view showing a coupling structure of the output disk and the power transmission gear of the embodiment.

FIG. 3 is a vertical sectional side view showing a first modification of the coupling structure of the output disk and the power transmission gear of the embodiment.

FIG. 4 is a vertical sectional side view showing a modified example 2 of the coupling structure of the output disk and the power transmission gear of the embodiment.

FIG. 5 is a longitudinal sectional side view showing a coupling structure of an output disk and a power transmission gear according to a second embodiment of the present invention.

FIG. 6 is a vertical sectional side view showing a first modification of the coupling structure of the output disk and the power transmission gear of the embodiment.

FIG. 7 is a vertical sectional side view showing a modified example 2 of the coupling structure between the output disk and the power transmission gear of the embodiment.

FIG. 8 is a longitudinal sectional side view showing a coupling structure of an output disk and a power transmission gear according to a third embodiment of the present invention.

FIG. 9 is a vertical sectional side view showing Modification Example 1 of the coupling structure of the output disk and the power transmission gear of the embodiment.

FIG. 10 is a vertical sectional side view showing a modification 2 of the coupling structure between the output disk and the power transmission gear of the embodiment.

11A and 11B show a coupling structure of an output disk and a power transmission gear according to a fourth embodiment of the present invention, where FIG. 11A is a longitudinal side view, and FIG. 11B is a side view.

FIG. 12 shows a first modification of the coupling structure between the output disk and the power transmission gear of the embodiment, where (a) is a longitudinal side view,
(B) is a side view.

FIG. 13 shows a second modification of the coupling structure between the output disk and the power transmission gear of the embodiment, where (a) is a longitudinal side view,
(B) is a side view.

FIG. 14 is a longitudinal sectional side view showing a coupling structure of an output disk and a power transmission gear according to a fifth embodiment of the present invention.

FIG. 15 is a vertical sectional side view showing a first modification of the coupling structure of the output disk and the power transmission gear of the embodiment.

FIG. 16 is a vertical cross-sectional side view showing a modified example 2 of the coupling structure of the output disk and the power transmission gear of the embodiment.

[Explanation of symbols]

 4, 5 input disk 6, 7 output disk 9 power roller 20 power transmission gear

Claims (2)

[Claims] 1. A half-toroidal type continuously variable transmission in which a speed ratio between two disks is steplessly changed by tilting of a power roller interposed between an input disk and an output disk disposed opposite to each other. A half toroidal type continuously variable transmission, wherein the output disk comprises two output disks arranged back to back, and a power transmission gear is sandwiched and fixed between the two output disks. 2. The half toroidal type continuously variable transmission according to claim 1, wherein the two disks and the power transmission gear are restrained at least in a rotational direction.