JPS59183163A - Reduction gear - Google Patents

Abstract

PURPOSE:To enable large ratio of speed reduction to be set, by providing endless cam grooves, formed meandering in a curve of a periodic function respectively, on each facing side of two rotary discs oppositely arranged to each other and interposing balls, held by a holding member on an output shaft, between the both cam grooves. CONSTITUTION:A rotor 5 is fixed to one end of an input rotary shaft 3 rotatably supported through a bearing 4 in a case 1 provided in a sationary condition. Then a rotary disc 8 facing to this rotor 5 is supported on the input rotary shaft 3 through a bearing 18 by a supporting cylidner 17 integrally formed with the rotary disc 8. Endless cam grooves 7,9, formed meandering in a sinusoidal shape at a prescribed pitch in the peripheral direction with respect to a circular line 6 being as the center, are provided on oppositely facing sides of the both rotary discs 5, 8, and said both cam grooves 7, 9 are connected to each other through plural balls 10. Then these balls 10 are held so as to be movable in the radial direction in a slit 13 extended in the radial direction of a holding member 11 fixed to one end of an output rotary shaft 14.

Description

[Detailed Description of the Invention] [Technical Field of the Invention] The present invention relates to a reducer C1, which is designed to provide a large reduction ratio while reducing the overall size. related.

I: BACKGROUND OF THE INVENTION AND PROBLEMS THEREOF] For example, among devices using a motor as a power source, there are many devices in which a load C is transmitted via a speed reducer that rotates the motor.

By the way, various reduction gears have been proposed for this kind of use, but the most common one is a combination of a small gear and a large gear. It is a gear-type speed reducer in which the rotation of the large gear meshed with the small gear is transmitted to the output rotating shaft (two-way).

However, gear type reducers have the following problems. That is, now, the number of teeth of the small gear Z1 * the number of teeth of the canine gear Z2 + the pitch circle diameter of the small gear 'l'Dt - the pitch circle diameter of the large gear 7D.

Then, the reduction ratio X of this reducer is z, n2 Z, D.

becomes. Therefore, to increase the reduction ratio Xi, should the pitch circle diameter D1χ of the small gear be decreased?

Pitch circle diameter Dz’ of large gear? It needs to be bigger.

However, since there is a minimum number of gear teeth (2 is a limit),
In order to set a large reduction ratio XF, it is necessary to increase the pitch circle diameter of the large gear, and as a result, the entire reduction gear inevitably becomes larger. In addition, in the case of a gear type reduction gear, the excitation force is transmitted through one or two teeth of the small gear and the large gear that are in contact with each other. Therefore, C-, which transmits the necessary dynamic force, is.

It is necessary to set each tooth to a size that can withstand the transmission of that force. Therefore, from this point of view as well, if an attempt was made to set the reduction ratio x2 larger, there was a problem in that the overall size would inevitably increase.

[Purpose of the invention]

The present invention was made partly in view of these circumstances,
The purpose is to provide a speed reducer r that is compact, provides efficient power transmission characteristics, and provides a large reduction ratio.

[Summary of the invention]

According to the present invention, an input rotation shaft and an output rotation shaft are provided. The input rotating shaft (- is coaxial) (- is connected to a first rotating plate, and a second rotating plate is provided opposite to this first rotating shaft in the axial direction ζ.

□ First and second cam grooves are provided at the ends. A rolling element is inserted between the first cam groove and the second cam groove and at position 1 where both cam grooves intersect, and this rolling element is attached to the holding member (-
Therefore, the radial direction ζ is freely cuttable (: held. And,
The holding member is connected to the output rotation shaft (Y). On the other hand, a support device is provided which supports the rotation point via a rotary element that can rotate on its own axis but cannot revolve.

〔Effect of the invention〕

With the above configuration, a large reduction ratio can be set by appropriately selecting the number of grooves in the opening direction of the first and second cam grooves and the radius ratio of the inner and outer rings of the support device for reasons described later. Therefore, the overall size can be reduced. In addition, all rolling elements and rotating elements of support devices (
Two power transmission functions at the same time? Since it can be made to exert its full potential, it is possible to obtain a device with high power transmission efficiency.

[Embodiments of the invention]

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

In FIG. 1, I is a case provided in a stationary state, and inside this case 1, a circular room 2 is formed.

Therefore, in the room 2 of the case 1, one end side of the input rotating shaft 3 penetrates the wall of the case I, and the penetrating part is the bearing 4 (:
Therefore, it is supported and rotatably inserted.The end of the input rotating shaft 3 located at the 813-ya 2nd circle (- indicates the shape of a disc (the two formed rotary plates 5 are fixed coaxially). As shown in Fig. 2, on the right side of the rotating plate 5, there is a circular line 6 drawn based on the rotational center line of the input rotating shaft 3.
An endless cam groove 7 is formed which curves in a sinusoidal V-shape at a predetermined pitch in the circumferential direction.

On the other hand, on the right side of the rotating plate 5 (on the two opposite sides,
An annular rotary plate 8 is coaxially arranged with a predetermined distance l\i]k'A between the rotary plate 5 and the rotary plate 5.

An input rotation shaft 3 is provided on the surface of the rotation plate 8 facing the rotation plate 5.
The center line is a circular line drawn with the same diameter ζ1 as the circular line 6 drawn with the rotation center line of An endless cam groove 9 is formed.Between the cam grooves 7 and 9, and at a position where both cam grooves 7.9 intersect, there is a rolling element, which is partially fitted into both cam grooves. That is, spheres 10 are inserted respectively between the rotating plates 5 and 8.The above-mentioned spheres 1o in a non-contact state are inserted between the rotary plates 5 and 8, and the spheres 1o are inserted perpendicularly to the center line of rotation of the input rotating shaft 3. direction,
In other words, the holding member ZZ that holds the moving target C in the radial direction
has been assigned. This holding member II is, for example, a third
1 (two indications) [: disc l1l - slit 13'll of a width that allows the front sphere 10 to be inserted into the center part of the holding member II (2 is the output rotation axis I).
One end of the output shaft 13 is coaxially connected to the input rotating shaft 3, and the other end of the output rotating shaft 13 passes through the hole I5 in the center of the rotating plate 8 and through the wall of the case I. A bearing I6 that rotatably supports the output rotation shaft 145 is mounted between the wall of the case I and the output rotation shaft I4.

Thus, the outer circumferential edge of the one-rotation plate 8 is connected to a support tube Z7 that bypasses the outer circumferential edge of the rotor plate 5 and extends to the outer surface of the input rotation shaft 3 (one opposing position). A bearing I8 is installed between I2 and the input rotating shaft 3. This bearing Z8 consists of a circular ring I9 fixed to the outer periphery of the input rotating shaft 3, an outer ring 20 fixed to the support cylinder I7, , and a plurality of spheres 21 installed between these inner and outer rings.Then, each sphere 2Z17j is similar to the cage of a rolling bearing (type 2, :5), and case I (type 2). Therefore, each sphere 2I is mounted so that it can rotate on its own axis but cannot revolve around it.

Next (2) The operation of the high speed machine constructed as above (- will be explained.

First, when the input rotating shaft 3 is rotated, the rotary plate 8 rotates in the opposite direction since each of the spheres 2z of the bearing 18 is supported to be able to rotate on its axis but not to revolve around it. On the other hand, when the rotary plate 5 rotates with the rotation of the input rotary shaft 3, the intersection position of the cam grooves 7 and 9 moves in the circumferential direction C2, and accordingly, the sphere 10 also moves in the circumferential direction C2. This movement 1 is transmitted to the output rotation axis I4.

This relationship will be explained in more detail as follows. Now, as shown in FIG. 4(a), the center of rotation of the rotating plate 5°8 is 7s, and the center line of the cam groove 7.9 is also 7s.
．． 9. For convenience of explanation, it is assumed that the tops of the cam grooves 7.9 are exactly at the intersection point. In this bird alignment C2, the sphere 10 is located exactly at the position indicated by A. Then, a line B connecting A and 8 is set as a reference line.

In such a state C, there is no rotational force on the input rotating shaft 3? As shown, the rotary plate 5 is rotated by θ and c in the right direction in the diagram from the position of the second reference line B. Due to this rotation, the cam groove 7 also changes by θ. - As mentioned above, the rotating plate 8 is supported by the input rotating shaft 3 via the bearing 1B5, and this bearing I8
Since the sphere 2I is rotatable but not able to revolve, the input rotation axis 3? When rotated clockwise by θ1, the rotary plate 8 rotates counterclockwise by θ from the position of the reference line B, and the cam groove 9 also moves to the left by θ accordingly. Here, since the sphere 10 interposed at the position where the cam groove 2 and the cam groove 9 intersect is held in a movable position only in the radial direction by the holding member II, as described above (-the cam groove 7 and As the intersection position of both cam grooves changes as a result of the transition with C'-9, the cams follow this transition and move to the position indicated by C:A' in 4-(b).Now move each cam to the The angle θS with the top of °9, θ, the number of ridges in the circumferential direction of the cam groove 7 is 1, that is, the frequency k"1m that of the cam groove 9?I'
Z4 and 8th position LC unit TΦ, cosZ3 ・01 = cos Z 4L' +1
04-...(l) The following relationship holds true. Then, if we convert this into a regular hexagon, Z, ・θ, = 2.・θ4 ...(2). ' 10,000 Rotating plate 5 has rotated by θ1 from reference line B, which means that the circle of bearing 18 @I9 has rotated by θ88 as shown in Figure 5 (2). The fact that the outer ring 20 of the bearing I8 has rotated by θ to the left from 1 is equal to C. Now, V'3f?tiAI
The radius r of the orbital surface 3Z of 9.

If the radius of the raceway surface 32 of the outer ring 20 is ir, then the following relationship holds true: r, .theta.1-r2 .theta.2 (3) with respect to the reference line B. Also, here, if the angle between the reference line B and the digit 1 of the sphere 10 is l1Ii, then θ, +θ, = θ, +θ4 − (4) θ, = θ,
+θ, . . . (5) is satisfied.

Since the output rotating shaft I4 is connected to the holding member II that holds the sphere ro, the reduction ratio X of this reducer is θ1 and θ.
. This is the ratio of Therefore, if we calculate the reduction ratio X using 2 to 5, we get C as follows.

However, β□, β, are.

It is. Therefore, for example, r,=8°rl ==
91 'ZrB -9+ I4 II O, the reduction ratio X becomes Zr2.

In this way, the frequency of each cam groove and the above-mentioned rrrr
＊'1 Selection Q (also known as C) Therefore, the reduction ratio can be improved and it can be set up over a wide range (two squares).In addition, all the rolling elements contribute to power transmission at the same time, so a large amount of transmitted power can be secured. Therefore, a large reduction ratio can be obtained with a small size, and a reduction gear that transmits power to the sky can be obtained.

Note that the present invention is not limited to the above-mentioned embodiments. For example, the rotating plate 8 may be placed on the outer side of the input rotating shaft. Further, the spherical body 2I may be replaced with a cylinder or leek, and furthermore, the bearing I8 can be replaced with a toothed type bearing.

[Brief explanation of drawings]

Fig. 1 is a partially cutaway side view of a reduction gear according to an embodiment of the present invention, Fig. 2 is a front view of a rotary plate in the reduction gear, and Fig. 3 is a holding part in the reduction gear. A perspective view of the member;
FIGS. 4 and 5 are diagrams for explaining the operation of the reduction gear. 3...Input rotating shaft, 5.8...Rotating plate, 7,9...
・Endless cam blade, 10... Sphere, II... Holding member. I4...Output rotating shaft, 1B...Bearing. Out - Jindai Hatato Benri Dozu Etakehiko Figure 1

Claims (1)

[Claims] An input rotating shaft, an output rotating shaft, a first rotating plate coaxially connected to the input rotating shaft, and a second rotating plate provided axially opposite to the first rotating plate. The rotating plate, and the opposing surfaces of the second rotating plate and the first rotating plate are provided with the above opposing surfaces.
2. A circular line of the same diameter drawn coaxially with C1 has a center ≦Y and each reaches f4 tjt Endless first and second cam grooves formed in a winding direction, and these first cam grooves. between the second cam groove and the position where both cam grooves overlap (: The inserted rolling element and this rolling element are held in a radially movable position (= connected to the output rotating shaft) between the holding member C, the input rotation shaft and the second rotation plate, and the rotor plate of the air 2, which is divided into two parts, is connected to the input rotation axis C through a rotating element that is rotatable on its own axis and cannot revolve around the input rotation axis C. What is claimed is: 1. A speed reducer characterized by comprising: a support device for holding a rotational axis;