JPH07117138B2 - Continuously variable transmission - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (Object of the Invention) The present invention provides a mechanical continuously variable transmission capable of continuously shifting gears with a simple mechanism by meshing transmission.

(Industrial field of application) The present invention can be applied to bicycles and the like that require downsizing and weight reduction, and heavy machinery such as production machines, automobiles, ships, etc., as well as wind power, tidal power, wave power, etc. The present invention relates to a continuously variable transmission that can be effectively used for energy extraction power generation equipment from intense nature.

(Prior Art) U.S. Pat. Nos. 4810235 and 4832660 are known as conventional continuously variable transmissions for the purpose of simplicity and weight reduction, except for friction drive type (Traction Drive) and belt pulley type continuously variable transmissions. First
It is disclosed in gazettes such as 4878883 and 4961719.
Each of these is a transmission mechanism in which several pulley segments or several small-diameter sprockets are arranged concentrically on the driving side or the driven side in belt or chain winding transmission, and the diameter of this similar circle is expanded or contracted. belongs to.

(Problems to be solved by the invention) However, because of the structure, these problems include the problem that the fluctuation range of the gear ratio, that is, the gear ratio cannot be increased, and at the same time, the pulsation in the rotational angular velocity on the output side is inevitable. There is. For example, in the case of No. 4810235 in which six pulley segments are arranged, this pulsation is caused by rotation of the dimensional difference between the height of a regular triangle formed by the shaft center and the two pulley segments and the length of one side thereof. It acts as the radius of the circle.

That is, this means that a pulsation with a numerical value of Sine 60 degrees, 1: 0, and 86602 occurs in the entire shift range. Although the pulsation width can be temporarily reduced by increasing the number of these elements to 8 or 10, the limit to reduce the diameter in inverse proportion to this is restricted due to the structure, and thus the gear ratio is reduced.

(Means for Solving Problems) According to the present invention, a plurality of cams whose phases are formed in the equiangular angular direction are provided on the input shaft, and the same number of discs as these cams are provided with slits each having a diameter line corresponding to the cam diameter. And fit each cam within the radius of each slit. An operation frame for rotatably holding an annular ring in which these discs are rotatably mounted is provided, and the operation frame is pivotally supported concentrically with the output shaft. As a result, the circular ring is set so that it can be moved up and down in a circular arc line passing through the input shaft. Further, a one-side clutch having ratchet teeth provided on the outer circumference of each disk is loaded in the annulus, and a meshing transmission is constituted by the outer circumference of the annulus and the chain wound around sprockets fixed to the output shaft.

(Operation) With the above-described structure, the present invention transmits the pressing force of the friction component force due to the rolling of the input shaft cam to both inner walls of the disc slit, and the continuous action causes the disc to reciprocally rotate at a predetermined angle. Further, the action of the one-sided clutch and the alternate rotation of the plurality of discs cause the annulus to rotate continuously. Rotation is transmitted to the output shaft by the chain wound around the sprocket on the outer circumference of the ring and the sprocket on the output shaft. In addition, the gear shifting is performed by the elevating and lowering adjusting means of the operation frame
The reciprocal rotation angle of the disk is expanded or reduced by converting the relative position with the cam within the radius area of the disk slit. By this operation, the speed can be changed steplessly.

Further, by providing a non-circular cam on the input shaft, it is possible to obtain the correctness by which the rotation free of pulsation can be transmitted to the output shaft. or,
Furthermore, when a circular cam is installed on the input shaft and it is used for a bicycle, etc., the load is reduced near the top and bottom dead center in pedal leg force drive, and it is possible to accelerate effectively in the effective drive range, so ergonomic leg force is optimal. Available for

(Embodiment) First, the operating frame, the ring, and the assembled state of the disk therein will be described with reference to the drawings in FIGS. 1 to 4. 13 in Fig. 1
Numerals 14 and 14 are plate-like supports, and 13 on the front surface is an internal part, which is broken except for both legs.

The input shaft 1 is provided with integrally formed non-circular cams 3 and 4, and the input shaft is attached to both supports by bearings at a position equal to the distance from the center of the disk to the output shaft center. The thickness of these non-circular cams is set equal to the width of sliders 7 and 8 which will be described later.

The circular plates 5 and 6 have the same size and shape, and are provided with wide slits having a diameter line passing through the center, and wide windows are opened on the left and right sides and above and below them. Their purpose is to reduce the inertial loss by making it as light as possible. Also, Fig. 1 and 2
As shown in the figure, the ratchet teeth 5T that act as a one-way clutch are provided on the outer circumference of the disc, and the shoulders on both sides of these teeth are closely fitted to the rotary wheel with a collar that holds the disc rotatably and fit inside the ring. Has been done. These rotating wheels 23, 24, 25, 23B, 24
B, 25B, 23C, 24C and 25C are cut to have a small diameter in the center as shown in FIG. 2 and are not in contact with the ratchet teeth 5T. Further, these rotating wheels are axially attached to the annular ring 22 through a bearing having a small diameter and are arranged at equal intervals as shown in FIG.

It should be noted that the disk 6 is the same in all, including these related members, one-side clutch, slider in the disk slit, linear bearing, etc., which will be described later, and is arranged in parallel with the related parts of the disk 5. .

The circular ring 22 is rotatably fitted and held by an angular contact bearing 21 provided on the inner circumference of the large-diameter circular holes of the operation frames 15 and 16. At the same time, the operating frames 15 and 16 have seven studs.
20a, 20b, 20c ... 20g and these fastening screws are fixed in parallel to each other. Further, a sprocket 18 is fixed at the center of the cross-section of the outer circumference of the ring, and a chain 30 is wound around the sprocket 19 and a small-diameter sprocket 19 fixed to the output shaft 2.

A combination of operation frames 15 and 16 along both inner walls of the supports 13 and 14 is pivotally supported by a sleeve 17 fixed to the support that also serves as a bearing of the output shaft and a sleeve of the rear surface support 14, and is used in the conversion operation described later. The center of the disk can be moved up and down in an arc shape that passes through the input axis.

On the other hand, the clutch mechanism is, as shown in FIG. 1, rotating wheels 23, 23B and 23C located at three equal positions of the ring, a ratchet pawl that is adjacent to each of these wheels, and is wound around these rotating wheels. It is composed of a working ring. It should be noted that these are all the same shape parts, all the ratchet pawls are all directed in the clockwise direction, and at the same time, all related parts of the disk 6 are also the same and are parallel to the disk 5. Therefore, the rotary wheel 23 and the ratchet pawl 27 related to the disc 5 will be described as a representative.

As shown in FIGS. 3 and 4, the operating ring 26 acting on the ratchet pawl is wound around the small diameter portion of the rotary wheel 23, and the head of the ratchet pawl 27 adjacent to and axially attached to the circular ring is in the horizontal U-shape. The two linear arms that are continuously and integrally formed are fitted and inserted from both ends of the cut end of the operating ring. The material of this operating ring is formed of nylon-based engineering plastic that has a certain elasticity and is excellent in wear resistance and self-lubrication.

In response to the rotation of the disc, these rotate the rotating wheel 23 in the clockwise direction while the disc rotates counterclockwise as shown in FIG. 3, so that both arms of the operating ring have a ratchet claw horizontal U-shape. Within a wide range, the width is X in the figure, and the small diameter part of the rotary wheel and the operating ring slide lightly and press the ratchet pawl head against the inner wall of the ring. Therefore, the ratchet claw and the tooth 5T are kept isolated. Further, as shown in FIG. 4, when the disc starts to rotate in the clockwise direction, the rotary wheel 23 is rotated counterclockwise so that both arms of the operating ring push the ratchet pawl head in the disc direction at the same time. The arm is sharply reduced to the inner width of the U-shaped side of the nail head, that is, the Y-width in the figure. Therefore, the friction between the small diameter portion of the rotating wheel and the operating ring sharply increases and the nail is strong and surely ratchet teeth.
Bite into 5T. This action causes the disc and the annulus to be integrated so that the annulus rotates simultaneously in the clockwise direction. When reversing again, the nail and the tooth are separated as shown in FIG. Also, these ratchet pawls and actuating rings are attached to the rotary wheels 23, 23B, and 23C respectively, and three sets are provided on each disc, and at the same time, three ratchet pawls work. To facilitate this simultaneous action, the number of ratchet teeth on the disc is set to a multiple of three. This function has the effect of making the transmission strength and durability from the disk to the ring triple that of one claw.

Next, a description will be given of a device component that converts the action of rotation of the non-circular cam into the rolling motion of the bearing that removes the friction of the friction component force applied to the disc slit. As shown in FIG. 1 and FIG. 5, linear bearings 9 and 10 (needle rollers with a flat cage) are closely attached to the left and right inner walls of the disk slit by channel type sliders 7 and 8. In addition, 11 sliders at the upper end and 12 thin steel plate bridges at the lower end of these sliders are screwed and fixed from both front and back surfaces, and both sliders are connected in parallel. Further, as shown in FIG. 5, the sliders 7B and 7C are inserted in the narrow grooves provided in the longitudinal direction inside the channels of both sliders. These sliders are made of the same material as the above-mentioned operating ring 26 and are formed in a gentle corrugation in the thickness direction of the disc, so they are elastically mounted with appropriate strength, and always descend by the weight of the slider and linear bearing. Is prevented by a sliding friction as weak as possible.

Also, the width of both sliders facing each other from the diameter of the non-circular cam is
It is set by adding a very small clearance of 0.002 mm or less, and the cam always contacts one of the left and right sliders while the input shaft is rotating. In addition, 9H in FIG. 5 is a shaft of a needle roller of a linear bearing and is inserted in the cage. Further, opposing projections 29L and 29R are provided at the lower part of the disk slit to function during a gear shift operation described later to limit the descending position of the slider. It should be noted that when going up, it can be stopped at the outer edge of the slit.

A wire for gear shift operation, which will be described later, is fixed to the mutual fixing stud 20a of the operation frame, and the upward side of this is a double hook provided with a double groove groove axially attached to the right leg of both supports as shown in FIG. The 28U end is fixed at a position where it is wound around the pulley 35 in a clockwise direction by half a turn in a clockwise direction, and the downward wire 28D is wound around the pulley 36 axially attached to the lower portions of both support legs and then wound in a tension mode. This one end is fixed to a position where the main hanging pulley 35 is wound a half turn counterclockwise. Further, an operating lever 37 is fixed to the two-hanging pulley, and the pulley is kept in an appropriate friction state at the contact surface with both supports, and is adjusted so that manual operation can be freely performed if necessary. ing.

Next, the operation and action, and the gear shift operation will be described with reference to FIG.

When the input shaft 1 starts to rotate clockwise from the posture shown in FIG. 1, the cam 3 pushes the slider 7 to push the disc 5 clockwise, and at the same time, the cam 4 pushes the left slider of the disc 6 to push. Turn this disc counterclockwise. At the same time, the slider 7 rolls the near bearing 9, and the cam 3 rolls on the slider contact surface. Therefore, the linear bearing 9 and the slider 7 descend and rotate the disk 5, and when the slider 5 reaches the position shown by the dotted line in FIG. 6, the lower end of the slider simultaneously contacts the projections 29L and 29R. During this rotation, the rotating wheels 23, 23B, 23C and their respective ratchet pawls maintain the posture shown in FIG. 4, and the disc 5 and the ring 22 are united and both rotate clockwise. Further, during this period, the disc 6 is rotated counterclockwise, and therefore the rotating wheel is rotated clockwise, so that these ratchet pawls maintain the posture shown in FIG. 3 and are kept isolated from the ratchet teeth. And the ring are idled in an insulated state.

Further, while the cam 3 passes through the dead point of the dotted line posture of FIG. 6 and reaches the solid line position, it acts on the disk in the opposite manner to the above, that is, the cam 3 moves the disk 5 counterclockwise, 4 rotates the disc 6 clockwise. Therefore, while the cam 3 raises the slider, and the cam 4 lowers the slider at the same time, the three ratchet pawls of the disc 6 keep the posture shown in FIG. 4 and continuously transmit the ring clockwise. Rotate.

In this way, the disks 5 and 6 alternately repeat the reciprocating rotation, and the circular ring 22 is continuously rotated clockwise, so that the sprockets 18 and 19 are rotated.
Also, the rotation is transmitted to the output shaft 2 by the chain 30 wound around them.

Therefore, since all the rotational force components acting on the discs of both the non-circular cams can be removed by the rolling of the linear bearing and the accompanying lifting and lowering of the slider, wear, heat generation, and energy loss can be completely prevented. . Next, the shift operation will be described.

Now, if the lever 37 of FIG. 10 is raised in the counterclockwise direction, the fixed pulley 35 will rotate around it and the wire 28D will be wound therein, and 28U will be returned at the same time, and the operation frames 15 and 16 will be based on the output shaft center. And the input shaft is moved toward the outer circumference of the disc slit. Therefore, since the working contact points of both cams on the slider are moved to a position where the disc radius is large, the discs 5, 6
The reciprocating rotation angle of is gradually reduced, so that high torque and low speed rotation is transmitted to the output shaft. When the lever 37 is further raised to the upright position in the figure, the minimum speed is reached. On the contrary, when the lever is lowered, the wire 28U is wound by the pulley 35, 28D is returned, the operation frame is raised, and the input shaft is moved in the slit toward the center of the disk. Therefore, the contact points of the two cams on the slider are moved to the positions where the disc radius is small, so that the reciprocating rotation angle of the discs 5 and 6 is enlarged, so that high speed rotation is transmitted to the output shaft. Further, when the lever 37 is tilted to the limit, the input shaft comes closest to the center of the disk, and the reciprocal rotation angle of the disk becomes maximum, so that the maximum speed is transmitted to the output shaft at a constant speed of the input shaft. If these gear shifting operations are performed while the input shaft is stopped, for example, during a gear shifting operation from a low speed to a high speed range, the slider is lowered for a predetermined amount, but the aforementioned protrusions 29L, 2
The 9R secures a limited descent position, and in the opposite case, it is stopped at the outside of the slit. Next, the constant proportionality in the rotation of the input shaft and the disc and the correctness of the constant velocity accuracy will be described with reference to FIG. Rotation of the non-circular cam 3 causes
The point of action on the slider always acts continuously on the same radius R of the disk, and while the cam rotates 180 degrees from the solid line position to the dotted line position, the disk is rotated by an α angle, and this cam As shown in the figure, the transmission rotation angles to the disk for every 20 degrees are completely equal, and therefore the transmission rotation from the input shaft to the output shaft can be performed in a fixed proportion. Therefore, constant speed rotation accuracy can be exhibited at any given shift position during the entire shift range. The reason for this is that the point of action of the non-circular cam on the disc slit is always the same radius R
To act on.

In addition, since this non-circular cam is symmetric, it can be reassembled by reversing 3 and 4 when damage or the like occurs during long-term operation, and can be used for double the life by exchanging the right half circle and the left half circle. There is also an effect.

Next, a case will be described in which the input shaft is a circular cam shaft and is used for input driving of a bicycle or the like. As shown in FIG. 7, when the non-circular cam and the circular cam 31 are overlapped with each other, they have substantially similar shapes, but a minus zone 34 is formed in the lower half left and right, and a plus zone 33 is generated in the upper half left and right. However, when this continuously variable transmission is used for input drive, the circular cam can function more effectively in terms of ergonomics. That is,
The rotation angle of the output shaft transmitted from the action of the non-circular cam and the circular cam on the disc is as shown in the linear graph analyzed in FIG. 9. When comparing the circular cam shown by the solid line and the non-circular cam shown by the dotted line, In the circular cam in the vicinity of the left and right dead centers in FIG. 6, the rotational speed of the circular disk is reduced. But to compensate for these declines
The best acceleration is near 90 and 270 degrees. Also, the whole is upward.

Therefore, using the input shaft as the pedal crankshaft of the bicycle, the upper and lower dead points of the pedal are matched with the both dead points of the cam, and the effective drive range where the pedal is easily depressed is matched with the acceleration range of the cam, which is the difficult drive range of the pedal. It can output low speed and high torque when passing up and down, and can reasonably demonstrate the drive function from an ergonomic point of view.

As shown in FIG. 8, when this circular cam is provided on the input shaft, a thin bearing 32 can be press-fitted into the cam 31 and the outer periphery of the bearing can be directly brought into close contact with the disc slit to exert a pressing force component.

Therefore, the former slider, linear bearing, slider,
Also, since the protrusions in the slit are unnecessary, the manufacturing cost can be reduced.

FIG. 11 shows the transmission of the present invention incorporated in a conventional bicycle.
An input shaft integrally formed with the circular cam into which the above-mentioned bearing is press-fitted is directly mounted on a bearing of the vehicle body frame as a pedal crankshaft. The operation frame is the first
The disc slit is installed in a posture different from that shown in the figure, and the disc slit is inverted upside down, and the cam acts in the lower radius of the slit.

(Note that the embodiment in which the non-circular cam shown in FIG. 1 is provided on the input shaft is hereinafter referred to as the former.) The reason for incorporating in this way is simply to make it as high as possible above the road surface and to avoid contamination by dust. Therefore, the function,
The rotation direction and the like are exactly the same as the former. However, the only difference is that the shifting of the operating frame is reversed.

The operation frame 39 is pivotally supported by a sleeve fitted to the rear axle of the bicycle as shown in the figure, and a sliding stud 42b fixed to the chain stay of the frame and a sliding holder 42 having a U-shaped cross section at the foremost edge. It is held parallel to the bicycle frame. Further, the entire periphery of this operation frame except the front edge is also sealed so as to also serve as a chain cover. Further, the sprocket for the rear wheel has the smallest number of teeth.

Further, the sliding holder 42 is fastened to the down tube 49 of the frame to ensure the parallel holding of the operation frame, and the upper extension is fixed to the top tube 46. Also, the same operation wire as the former is fixed to the stud 20a of this operation frame, and the wire 50U pulled upward is hung on the pulley 46 axially mounted in the middle of the slide holder and further the top tube 46
The 50U end is fixed at a position where it is wound in a clockwise direction for more than half a turn on a two-ply pulley 43 which is axially attached to a fixed table. The wire 50D on the opposite side is wound around a pulley 45 which is attached to the lower end of the slide holder and is pulled upward and fixed to the down tube 49.
The 50D end is fixed at a position where it is hung on 44 and wound around the above-mentioned two-ply pulley 43 by more than half a turn in the counterclockwise direction. An operating lever 47 is fixed to the two-ply pulley 43, and is adjusted so as to maintain an appropriate frictional state with the mount of the pulley.

Next, driving and shifting operation will be described.

Now, when you straddle the saddle to start running and tilt the operating lever 47 forward, the operating frame connected by wires
The 39 is raised and slows down so you can easily pedal. If the pedal is rotated 90 degrees from the posture shown in FIG. 11, the cam and the disk have the positional relationship shown in FIG. still,
In the figure, 22 'is the inner circle of the ring, and since one clutch in the ring is completely the same as the former, the explanation is omitted.

At this time, pedal crank 41R is directly below, left crank 41L
Is right above, and the area around this is the difficult drive range where it is most difficult to exert leg strength. However, since the cams 31 and 38 are set so as to come to the dead center position at the same time, as mentioned above in the graph of FIG. It will be easier to pass.
This effect works similarly to the commonly known Oval Gear (OVAL) effect.

Further, at the next 180-degree pedal rotation, 41L is switched right down and 41R is switched right up, while the cam 38 rotates the disk 6 and thus drives the ring by the Z angle. That is, one rotation of both pedals causes the circular ring to be transmitted and rotated by twice the Z angle, and the rear wheel sprocket is simultaneously driven by the circular ring sprocket and the chain.

In particular, at the time of starting, the rear wheels can be driven with a low speed and a high torque in this way, so that a very easy and reliable starting can be performed. Once you start running, you can accelerate easily, and now when you gradually pull the operating lever 47 forward, the wire 50D is caught in the pulley 43, 50U is returned from the pulley and the operation frame 39 descends. If it is adjusted to a certain position in the high speed range, it will be as shown in FIG. At this time, the input shaft 40 approaches the center of the disc, and the relative position where the cams 31 and 38 come into contact with the inner walls of the disc slit is changed. The disk 5b is rotated by the W angle by the cam 31 that has acted up to the above, and at the same time, the circular ring is transmitted in the clockwise direction by the same angle. In the next 180 degree pedal drive, the disk 6b is rotated by W angle by the cam 38, and at the same time, the disk 6b is continuously rotated by the same angle to rotate the ring clockwise. That is, one rotation of the pedal rotates the double ring of the W angle.

Further, as shown in the figure, the cam 38 has passed the dead center and is in the initial stage of disk drive, but the cam 31 is at the end of drive before the dead center. In this way, in the high speed range, the time difference 51A, 51B when passing the dead center of both cams
However, due to the overlapping of the drive relays to the disk, the rotation can be continued more smoothly, and the load reduction effect when the pedal passes vertically is the same as in the previous period. That is, one of the discs having a higher rotational speed drives the annulus.

Now, when the lever 47 is pulled to the maximum speed position, the operating frame is further lowered, the input shaft is closest to the center of the disc, and the disc rotation angle by the cam is increased more than the W angle. At this maximum speed position, the W angle is about 120 degrees. However,
When a higher output rotation is required, the output rotation angle can be further expanded by making the input shaft from a stronger material, setting the diameter smaller, and increasing the eccentric dimension between the input shaft and the cam.

Even if the vehicle is suddenly stopped due to a traffic signal or a railroad crossing while running at a high speed operation position, the pedal lever can be stopped in the direction shown in FIG. In this case, the left and right pedals can be reversed.

In this way, the shift operation can be freely performed regardless of whether the vehicle is running or stopped, and for example, a fall accident due to meandering due to insufficient acceleration when crossing a railroad crossing can be prevented. In addition, the driving effect of low speed and high torque can be exhibited even on a steep climb.

Furthermore, the former can be strengthened according to the purpose of application to production machines and heavy equipment. For example, three non-circular cams can be installed on the input shaft and the phase can be set every 120 degrees to install three discs, or four cams can be installed on the input shaft at 90-degree phases and four discs can be installed. Further, it is possible to easily set the thickness of the ratchet teeth, the claws, etc. to a sufficient strength depending on the installation volume.

If it is necessary to further reduce the distance between the input shaft and the output shaft, it is possible to easily solve the problem by using both of the sprockets 18 and 19 as gears for gear transmission.

Further, the present invention can be constructed in a flat shape as a whole, and by carefully selecting the material of each member, it is easy to reduce the size and weight, and it is possible to provide the bicycle at a relatively low cost.

[Brief description of drawings]

FIG. 1 is a side view showing a fracture of an essential part of an embodiment of the present invention, and FIG.
1 is a sectional view taken along the line A-B in FIG. 1, FIGS. 3 and 4 are explanatory views of the action of a ratchet pawl and an operating ring, and FIG. 5 is a sectional view taken along the line C-D in FIG. Fig. 7 is an exploded view for explaining the rotation action of the disc by the non-circular cam. Fig. 7 is an explanatory diagram for comparing the circular cam and the non-circular cam. Fig. 8 is a side view seen from the axial cross section where the bearing is press-fitted into the circular cam. Fig. 9 is a contrast line graph showing the rotational angular velocity from the disc to the output shaft by the circular cam and the non-circular cam,
FIG. 10 is a side view of the gear shift operating device for the operating wire in FIG. 1, FIG. 11 is a side view of the present invention incorporated into a bicycle, and FIG.
FIG. 13 is a diagram for explaining the action of the cam and the disc during low speed transmission, and FIG. 13 is a diagram for explaining the action of the cam and the disc during high speed transmission. 1 ... Input shaft, 2 ... Output shaft, 3, 4 ... Non-circular cam, 5, 6
… Disk, 7, 8… Slider, 9, 10… Linear bearing, 13, 14… Support, 15, 16… Operating frame, 22… Ring, 27
... ratchet claw, 30 ... chain, 28U, 28D ... operation wire, 31, 38 ... circular cam, 5b, 6b ... disk, 39 ... operation frame, 50
U, 50D ... operation wire, 41R, 41L ... pedal crank,
42 ... Sliding holder, 43 ... Two pulleys, 40 ... Input shaft.

Claims (5)

[Claims] 1. A plurality of circles provided with a circular ring rotatably fitted in an operating frame which is pivotally supported by a support concentrically with an output shaft, and a diametrically linear slit rotatably mounted in the circular ring. A plate, a clutch provided between the disc and the ring, and an input shaft provided with a plurality of cams are axially crossed at right angles within the radius of the disc slit, and each cam is attached to the inner wall of each slit. A continuously variable transmission formed by meshing transmission of a sprocket fixed to the outer circumference of the annular ring and the output shaft by facing each other and a chain or a gear. 2. The continuously variable transmission according to claim 1, wherein the cam of the input shaft is a non-circular cam (3). 3. The continuously variable transmission according to claim 1, wherein the cam of the input shaft is a circular cam (31). 4. A disk having ratchet teeth on its outer circumference, a rotary wheel having an operating ring provided with arms at both cut edges and closely rotating with the disk, and a head having a horizontal U-shape. The continuously variable clutch according to claim 1, further comprising a one-way clutch formed by axially coupling the formed ratchet pawl to an annular ring and inserting both arms of the operating ring into a lateral U-shape of the ratchet pawl head. transmission. 5. A ratchet tooth having a plurality of sets of a rotary wheel and a ratchet pawl attached to the operating ring according to claim 4, which are axially equiangularly set on a ring and set to a multiple of the number of sets. The continuously variable transmission according to claim 1, further comprising a one-way clutch including a disc provided.