JPS605819B2 - Friction type transmission - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Application of the Invention] The present invention relates to a friction type transmission that uses rolling friction of cylindrical rollers to increase and decrease distance instead of meshing gears.

[Background of the invention]

As a conventional friction transmission that uses rolling friction,
As shown in Figures 1 and 2, there are many types in which a thin roller and an hourglass-shaped roller are sewn together. Generates pressing force.

In FIGS. 1 and 2, the grooves are deep in the center with respect to the direction of the pitch circle provided on the back surfaces of the sun loaves a, a' and the grooved plates b, b', and become continuous as they approach both ends; Using a plurality of grooves whose depth becomes zero at both ends and a ball c, the ball c forms a groove due to the deviation in the rotation angle of the grooved plates b, b' and the sun loaf a, a' caused by the input torque. Taking advantage of the movement in the left and right directions, press the sun loaves a and a' in the direction of the scales, and press the planetary rollers d.
The roller pressing force is generated by the wedge effect of the sun loaves a and a'.

However, since the friction transmission configured as described above uses barrel-shaped rollers and drum-shaped rollers, the roller diameter changes in all directions of the roller axis, and the roller end inevitably Slip occurs as the distance approaches .

This causes the following problems. [a} In order to prevent seizing due to slippage and damage to the roller surface, it is necessary to lower the Hertzian stress at the roller end, which limits the overall pressing force and therefore cannot increase the transmission capacity. [b' Due to the occurrence of slippage at the roller end and the problems mentioned above, the rolling conditions of each roller (
As shown in Fig. 3, in the relationship between the slip rate, Hertzian stress, and the coefficient of friction, the roller As it approaches the end face, the conditions of point B and point C are met, and the coefficient of friction decreases by 4.0, so the transmission capacity is limited.

[c- Due to the occurrence of slippage, heat generation on the roller surface increases, reducing efficiency and shortening the life of the roller. Skin Roller production (polishing, surface finishing) requires advanced technology.

Further, machining of the groove portion of the pressing force generating device also requires high technology, resulting in high cost. [Object of the invention] In view of the above points, the present invention has all rollers cylindrical,
Another object of the present invention is to provide a friction type transmission in which preload can be adjusted from the outside according to the required transmission torque.

[Summary of the invention]

In order to achieve the above object, the present invention has an input shaft 1 and an output shaft 4 disposed on the same axis, a cylindrical drive roller 2 fixed to the input shaft 1, and a cylindrical drive roller fixed to the output shaft 4. Between the ring 5 and the drive roller 2 and the idle roller 7, and the idle roller 7 and the preload roller 8, there are installed cylindrical rollers, each consisting of two preload rollers 8 and 9 for each idle roller 7. , 9, preload rollers 8, 9, and self-driving ring 5 are arranged in plural sets so as to be in contact with each other, and one preload roller 8 of the preload rollers 8, 9 is rotatably fixedly supported by the casing 3. , the other preloading roller 9 is provided movably along the inner peripheral surface of the driven ring 5.

[Embodiments of the invention]

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

In FIGS. 4 and 5, reference numeral 1 denotes an input shaft having a cylindrical drive roller 2 integrally fixed to its end, and this input shaft 1 is rotatably supported by a casing 3. Reference numeral 4 denotes an output shaft that is disposed facing the input shaft 1 on the same axis and to which a driven ring 5 is connected via an output shaft arm 6. The output shaft 4 is rotatably supported by the casing 3. ing.

Reference numeral 7 designates a plurality of cylindrical idle rollers interposed between the drive roller 2 and a fixed preload roller and a movable preload roller, which will be described later. are distributed evenly.

Reference numerals 8 and 9 denote a plurality of cylindrical fixed preload rollers and movable preload rollers that are arranged between the driven ring 5 and the idle roller 7 so as to support both the rollers 5 and 7, respectively; The former fixed preload roller 8 is rotatably supported on a support shaft integrally fixed to the gear case 3, and the latter movable preload roller 9 is supported on the end face side of the roller 9. The ring 5 is rotatably supported by a support shaft 12 that is integrally fixed to a preload plate 11 that is arranged on the holder, and moves along the inner circumferential surface of the ring 5 as the preload plate 11 rotates.

The preload plate 11 is integrally fixed to a hollow shaft 13 that is inserted into the outer circumferential side of the input shaft 1, and this hollow shaft 13 is connected to the input shaft by operating a handle from the outside via a gear mechanism (not shown) or the like. It is designed to rotate slightly regardless of the rotation of 1. Next, the operation of the friction type transmission according to the present invention will be explained. 0 Before starting, when the preload plate 11 is rotated in the direction of the arrow shown in FIG. 5 by operating the handle from the outside in the direction of the arrow shown in FIG. 9 moves slightly in the same direction along the inner peripheral surface of the driven ring 5 and is forcibly pressed between the driven ring 5 and the idle roller 7 as shown by the dotted line in FIG.

Therefore, the idle roller 7, driven ring 5, etc. are elastically deformed by the movement of the movable preload roller 9. Therefore, radial pressing forces are generated between the drive roller 2 and the idle roller 7, between the idle roller 7 and the preload rollers 8, 9, and between the preload rollers 8, 9 and the self-driving ring 5. do. When the input shaft 1 is rotated in this state, the drive roller 2 rotates, and the rotation is sequentially applied to the output shaft 4 via the idle roller 7, preload rollers 8, 9, self-driving ring 5, and output shaft arm 6. communicated. Furthermore, if a different pressing force is required during rotation, the degree of pressing of the movable preload roller 9 can be adjusted by rotating the preload plate 11 by operating the handle from the outside in the same manner as described above.

〔Effect of the invention〕

The friction type transmission of the present invention has a drive connected to an input shaft.

- A plurality of sets of cylindrical rollers, each consisting of two preload rollers per idle roller, are arranged between the roller and the self-moving ring connected to the output shaft so as to be in contact with each other, and Among the rollers, one preload roller is rotatably fixed and supported, and the other preload roller is rotatably supported.
In addition, since the driven ring is movably supported along the inner peripheral surface, the following effects can be obtained. 'a} Since the pressing force of each roller can be arbitrarily selected externally according to the load and a frictional force corresponding to the transmitted torque can be generated, slippage on the roller surface is almost eliminated and the life of the roller is increased. .

{b) Since all the rollers are made into simple cylindrical shapes, spherical polishing and spherical finishing can be eliminated, so manufacturing costs can be reduced.

In the embodiment of the present invention, the preload roller is placed between the idle roller and the driven ring, but the same effect can be obtained even if the preload roller is placed between the drive roller and the idle roller. In addition, although the reduction gear was explained in this example,
Of course, if the output is reversed, it can also be used as a speed increaser.

[Brief explanation of the drawing]

Figure 1 is a main sectional view of a conventional friction type transmission, and Figure 2 is a cross-sectional view of a conventional friction type transmission.
1-1 line sectional view in the figure, Figure 3 is a diagram showing the relationship between the friction coefficient, slip rate, and Hertzian stress in rolling friction transmission,
Fig. 4 is a front sectional view of the friction type transmission of the present invention, Fig. 5 is a perspective view showing the main parts of Fig. 1, and Fig. 6 is a front view of the main parts for explaining the principle of the invention. . 1... Input shaft, 2... Drive roller, 3... Gas case, 4... Output shaft, 5... Heshiki ring, 7
..... Idle roller, 8, 9 ..... Preload roller, 11 ..... Preload plate. Traditional map Sun Z chart 3 chart 4 S chart system 6 chart

Claims (1)

[Claims] 1 An input shaft 1 and an output shaft 4 are arranged on the same axis, and a cylindrical drive roller 2 and an output shaft 4 are fixed to the input shaft 1.
A pair of cylindrical rollers, each consisting of two preload rollers 8 and 9 for each idle roller 7, is connected between the driven ring 5 fixed to the drive roller 2, the idle roller 7, and the idle roller 7. A plurality of sets of preload rollers 8, 9 and preload rollers 8, 9 and driven ring 5 are arranged so as to be in contact with each other, and one of the preload rollers 8, 9 is rotatably attached to the casing 3. A friction type transmission characterized in that the other preloading roller 9 is fixedly supported and movable along the inner peripheral surface of the driven ring 5.