JP2010203602A - Continuously variable transmission using one-way planetary gear - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an inexpensive, small and lightweight continuously variable transmission positively transmitting driving force by a gear by continuously changing a radius and a circumferential length of a driving side rotor while having a constant pitch in the gear. <P>SOLUTION: The device transmits rotation by pulling a chain 14 by a plurality of planetary gears 7 arranged evenly around a driving shaft 6, and gear change is continuously carried out by controlling distances from the driving shaft 6, in other words, revolution radii of the respective planetary gears 7. By supporting the respective planetary gears 7 by a one-way clutch 10 to freely rotate in the forward direction, and oscillation caused by periodic normal and reverse rotations generated by sliding of a cam 5 wherein a lever 13 linked to the one-way clutch 10 is eccentric, periodic change is applied to rotation speed of a revolving planetary gear 7, and the rotation speed of the planetary gear 7 in a position of breaking off and re-engaging with the chain 14 is relatively lowered with respect to a moving speed of the chain 14. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

The present invention relates to a continuously variable transmission including a one-way clutch and a planetary gear.

A conventional continuously variable transmission generally has a method in which the radius of a rotating body is continuously changed, and the movement of the outer periphery thereof is transmitted to another rotating body directly or with a belt by a frictional force. Originally, in order to reliably transmit a driving force between independent members even at a low speed or a high load, it is necessary to engage uneven portions having a constant pitch like a gear. However, if unevenness is provided on the circumference of the rotating body, the circumferential length is defined as a multiple of the pitch of the unevenness, and the radius of the rotating body cannot be changed continuously. The device was not provided with irregularities on the circumference of the rotating body, but transmitted by frictional force.

The driving force transmission method by meshing gears with a constant pitch unevenness is simple and reliable, but it can only perform stepwise shifting, and even if the number of steps is increased, transmission of driving force is interrupted during shifting operation. There is no smooth acceleration. On the other hand, the transmission method using the frictional force with no pitch unevenness can change the speed steplessly, the transmission of the driving force is not interrupted even during the shifting operation, it can be smoothly accelerated, but it can be transmitted at low speed and high load It was difficult, complicated and heavy, and the loss due to friction was great.

An object of the present invention is to provide an inexpensive, small, and lightweight continuously variable transmission that can transmit continuously with a simple gear of a mechanism and can transmit a driving force reliably even at low speeds and high loads. is there. The target is mainly for luxury-oriented users with weak pedaling force, and bicycles for electric assist that are becoming popular recently, and by shifting the shift control in conjunction with the load of the driving force, it is also released from the shift operation during driving It aims to become the basis of the automatic continuously variable transmission.

The solving means will be described below. The basis of the present invention is a mechanism for transmitting a driving force by attaching a gear to each of a drive shaft and an output shaft and spanning a chain. First, instead of fixing one large gear to the drive shaft as a means to change the rotation radius on the drive side in a stepless manner for shifting, a plurality of small planetary gears are arranged around the drive shaft. By controlling the distance of the gear from the drive shaft, the rotation radius of the drive side rotating body can be changed steplessly by a method in which the gear meshes. Next, if the planetary gear is supported by the one-way clutch so as to be able to rotate only in the forward direction as a means to cope with the change in the spacing between the planetary gears due to the change in the revolution radius of the planetary gear, one planetary gear is the reference. Thus, the other planetary gears can freely rotate in the forward direction, and the chain can be sequentially fed to cope with changes in the spacing between the planetary gears. However, in order to continue the rotation, each planetary gear needs to be temporarily detached from the chain below the output gear side on the revolution track centered on the drive shaft and meshed with the chain again above. When the planetary gear is away from the chain, it solves the fundamental problem of the difference between the multiple of the pitch and the steplessly changing circumference, that is, the meshing of the gear with a constant pitch irregularity and the continuously variable transmission. There is a need to. Specifically, when the planetary gear is detached from the chain, it is difficult for it to come off the chain if torque is applied. Additional mechanism is required. The greatest feature of the present invention is a mechanism that periodically changes the rotation speed of the planetary gear by rotating the insulator, which is linked to the planetary gear only in one direction, with the cam in the normal and reverse directions. This mechanism solves this problem by generating a relative speed difference between the rotational speed of the planetary gear and the moving speed of the chain at the position of separation and engagement with the chain.

First, in order to explain the positional relationship of each member, the drive shaft is arranged from the front of the observer toward the back, and the drive shaft and the rotating plate fixed to the drive shaft rotate together in the clockwise direction to rotate. Three planetary gears supported on the plate so as to rotate in the clockwise direction revolve around the drive shaft in the clockwise direction together with the rotating plate, pull the chain and move it to the required position on the left side of the drive shaft. It is assumed that rotation is transmitted to the arranged output gear. Here, autorotation refers to rotation around the axis of the rotating body itself, and revolution refers to rotation of the rotating body itself around an axis outside the rotating body. Hereinafter, it demonstrates along a claim.

According to a first aspect of the present invention, an output shaft is rotatably mounted on the main body frame, an output gear is fixed to the output shaft, a disc cam is mounted at a required position in the right direction of the output gear of the main body frame, The drive shaft is rotatably mounted at a position eccentric to the left from the center of the disk cam, the arm angle control plate is mounted on the drive shaft so as to be capable of relative rotation control, and the arm angle control plate is rotated relative to the main body frame. A control mechanism is provided, a rotary plate is fixed to the drive shaft, and three arm shafts are provided at equal distances from the drive shaft on the rotary plate in parallel with the drive shaft and at equal intervals. One end of the arm is rotatably mounted around the axis, one point on each arm and the point on the opposite arm angle control plate are connected by an arm angle control link, and the other end of the arm is parallel to the drive shaft A planetary gear shaft is provided, and the planetary gear can freely rotate on the planetary gear shaft. Attach the inner race of the one-way clutch to the planetary gear hub so that it can rotate clockwise with respect to the outer race, and fix the action point at one end of the insulator to the outer race of the one-way clutch. The arm and the insulator are connected by a cam follower spring so that the force point portion at the other end slides on the outer periphery of the disc cam, and the output gear and at least two planetary gears are engaged by a chain. This is the means with the smallest number of parts, although the change in the revolution radius of the planetary gear is limited to the range in which the insulator and the cam can slide.

Further, as a modification of the above, the action point portion of one end of the insulator is not fixed to the outer race of the one-way clutch, but is attached to the arm shaft so as to be rotatable around the axis, and the first race is attached to the outer race of the one-way clutch. One end of the lever interlocking link can be fixed, and the other end of the first lever interlocking link and one point on the insulator can be connected by the second lever interlocking link. In this modification, an insulator interlocking link is interposed in the middle, and the rotation of the insulator is linked to the planetary gear by a pantograph. The principle of associating the planetary gear with the lever via the one-way clutch mechanism is the same, but the change in the revolution radius of the planetary gear is not limited by the position of the cam and lever due to the pantograph made by the interlocking link, so the number of parts is Although it increases, there is an advantage that a larger gear ratio can be obtained. Further, the pantograph does not need to be parallel, and the necessary rotation can be generated by the shape of the four-bar link. Further, instead of linking with a link, rotation may be linked with a gear or a chain.

According to a second aspect of the present invention, the same mechanism as that provided around the drive shaft in the first aspect is provided on the output shaft instead of the output gear, such as a cam, an insulator, and a planetary gear. Is controlled to be inversely proportional. This is advantageous in that a large gear ratio can be obtained although the number of parts increases because the change in revolution radius of the drive side and the output side is inversely proportional.

According to a third aspect of the present invention, the main body frame is provided with a crankshaft instead of the cam, and the power point portion at one end of the lever and the crankshaft are connected by the crank. This is obtained by replacing the sliding pair of the insulator and the cam in the means of claim 1 with a rotating crank. Similarly, the length of the crank has the disadvantage of limiting the change in the revolution radius of the planetary gear, which is slightly inferior to the cam system, but is a method with fewer parts, reliable operation and less friction. Further, a modification in which the first and second lever interlocking links are interposed between the planetary gear and the lever, and a mechanism provided around the drive shaft as a means of the fourth aspect as in the second aspect is a modification in which the output shaft is provided with a mechanism. Is possible as well.

According to a fifth aspect of the present invention, the length of the crank of the third and fourth aspects can be freely controlled. Normally, a crank is a single link member that has one end as its center and the other end around its periphery, but the crank that can be expanded and contracted here refers to a crank whose length can be controlled to expand and contract. The length is a measure to limit the change in the revolution radius of the planetary gear. The modification of claim 1, wherein the rotation of the lever produced by the crank is linked by the pantograph. Specifically, the second lever interlocking link is connected to and extended from one crank that has connected the power point portion of the crankshaft and the lever in claim 3, and one virtual having a length at both ends thereof. The length is controlled by changing the connecting angle of the crank. Actually, since the lever connects the connecting portion of the two cranks and the arm shaft, the lever is controlled in conjunction with the arm angle. If the drive shaft and planetary gear shaft linked with the rotating plate and the arm are also regarded as one virtual crank that can be expanded and contracted, the quadrilateral made there becomes a four-bar rotation dual crank mechanism, and a pair of links that can be expanded and contracted. The main body frame linked in (1) is a base link, and the insulator can be regarded as an idle link that rotates and rotates.

According to a sixth aspect of the present invention, the one-way clutch mechanism is further provided with a claw release guide. When the counterclockwise rotation of the insulator exceeds a certain angle, the pawls supported by the outer race ride on the pawl guide and forcibly disengage from the inner race pawl wheel, and the one-way clutch stops functioning. In addition, the planetary gear can rotate in both directions, and the meshing with the chain is smoother. If the rotation angle returns to a certain angle or less, the pawls come off the guides and the one-way clutch function is restored.

According to the seventh aspect of the invention, the control of the revolution radius of the planetary gear is linked to the load of the drive shaft, and an automatic continuously variable transmission that can be driven with a constant driving force without the need for a shifting operation can be realized.

According to the eighth aspect of the present invention, the planetary gear shaft is slightly rotated with a straight line passing through the center of the planetary gear orthogonal to the drive shaft as a rotation shaft, and the planetary gear shaft is angled with respect to the drive shaft. In the basic mechanism, all the planetary gears are in the same plane, so they can only approach to their diameter, but this makes adjacent planetary gears closer to each other, with their teeth shifting in the extension direction of the drive shaft. Can be widened. At this time, the tooth surface has an opposite angle with respect to the planetary gear shaft, so that it has a shape like a helical gear. In the meshing part, the angle of the planetary gear shaft cancels the angle of the planetary gear shaft. The tooth surface becomes quasi-parallel to the pin of the chain and the meshing is stabilized.

The operation of the above solution will be described below. The above solution basically consists of two mechanisms. One is a plurality of planetary gears supported around the drive shaft so as to be rotatable in the clockwise direction. The distance from the drive shaft, that is, the revolution radius of the planetary gear, is controlled by a control mechanism, whereby the radius and the circumferential length of the drive side rotating body are changed, and this is a mechanism that is the basis of continuously variable transmission. As an example of the control method, it is realized by rotating an arm angle control plate attached to the drive shaft so as to be relatively rotatable, but the revolution radius of the planetary gear is controlled by the drive shaft. Any mechanism can be used as long as the distance between the planetary gears can be controlled, which is basically a well-known mechanism and will not be described in detail. In addition, it is possible to make an automatic continuously variable transmission by linking the control method of the revolution radius of the planetary gear to the load of the drive shaft, and further, the driver can control the load linkage coefficient after linking. You can also As the revolution radius changes, the spacing between the planetary gears also changes. However, the planetary gears are supported so as to rotate freely in the clockwise direction, so it is impossible to drive or stop while the chain is engaged. Without changing the revolution radius.

The other one is a lever which is a major feature of the present invention and revolves around the drive shaft together with the planetary gear while rotating forward and backward by a cam or a crank, and the rotation of the planetary gear through a one-way clutch. It is a mechanism that acts as a forced feed and a free return on the rotation of the. Since the cam or crankshaft is eccentric to the right of the drive shaft, the rotation speed of the planetary gear on the revolution orbit is the fastest in the right direction around the drive shaft, the slowest in the left direction, and in the upward direction. During acceleration, the vehicle is decelerating downward. As a result, a plurality of planetary gears mesh with the same chain, but only the planetary gear with a high relative rotation speed located in the right direction of the drive shaft pulls the chain and transmits the driving force. Along with the rotation of the drive shaft, when the planetary gear transmitting the driving force decelerates the rotation speed and moves downward from the right direction, the next planetary gear increases the rotation speed. Then, it moves from the upper direction to the right to take over the role of transmitting the driving force, and this is repeated to transmit the driving force. Since the planet gear having the fastest relative rotation speed determines the movement speed of the chain, the rotation speed of the planet gears at other positions is relatively slower than the movement speed of the chain. As a result, the planetary gear is free to rotate and freely disengages from the chain while passing over the chain below the drive shaft, while the chain approaches and contacts the planetary gear while passing over the planetary gear at the upper left. Then, while freely rotating in the clockwise direction, meshing is performed at a phase-matching position. This mechanism solves the problem of meshing the planetary gear and the chain in free phase and in phase.

As described above, by controlling the revolution radius of the planetary gear with a combination of the above two mechanisms, it is possible to change the speed steplessly. Further, the control of the shift is linked to the load of the driving force, specifically the accompanying chain tension, etc. If it does, it will become an automatic continuously variable transmission which can always drive with a fixed driving force. The method of detecting the load and controlling the revolution radius may be mechanical or electric, and by changing the spring tension, etc., and manually adjusting the interlocking coefficient to the load during operation, the load on the drive side Can be freely selected, but is basically a well-known mechanism and will not be described in detail.

The present invention is not limited to the above method as long as the present invention is based on the principle described above. The following supplements alternative methods and more desirable mechanisms.

As for the control method of the revolution radius of the planetary gear, the arm angle is controlled by rotating the arm angle control plate relative to the rotating plate, but in addition to the combination of the arm shaft and the rotating plate, the driving shaft and Any mechanism may be used as long as the distance between the planetary gear shafts is variable, and a mechanism may be used in which the rotating shaft of the planetary gear slides on the rotating plate until it antagonizes with the slide spring together with the slider supporting the planetary gear shaft. There are various methods such as placing a planetary gear between a pair of conical wheels facing each other and adjusting the interval between the conical wheels. Also, an arm angle control spring is attached between the rotating plate and each arm, and the planetary gear supported at the tip of the arm is pulled by the load of the chain, and the arm moves until the load balances with the repulsive force of the arm angle control spring. An automatic continuously variable transmission can be obtained by rotating in a counterclockwise direction and using a mechanism in which the planetary gear approaches the drive shaft. At this time, if the arm angle control plates are used together in a freely rotating state, the respective arms perform the same operation, and if they are not used together, individual operations are performed. The arm angle control spring that connects the arm and the rotating plate is represented by a coil spring centered on the arm axis in the drawing, but the load changes as the repulsive force is proportional to the distance between the planetary gear shaft and the drive shaft. However, it is sufficient if the force applied to the drive shaft can be maintained almost constant, and other mechanisms may be used. Further, the repulsive force may be constant, but a wider range of requirements can be met by adopting a structure that can be changed stepwise or continuously. The repulsive force can be changed at a low cost by the method of stopping, but it is also possible to change the repulsive force by using a wire etc. from outside this mechanism during operation, so that the load can be freely selected during operation. The power can be either manual or electric.

Regarding the control of the arm angle, there is a load fluctuation on the road, and the human pedaling force applied to the crank of the bicycle is not constant. Therefore, an absorber can be attached to the arm in order to prevent a sudden change in the revolution radius. In addition to the method in which the revolution radius of the planetary gear is linked to the load of the drive shaft and the angle of the arm is uniformly changed by the rotation of the arm angle control plate, each link is made independent and the arm of the previous arm is A mechanism that limits the range of inclination of the next arm via a stopper can be provided with stoppers in both the radius reduction and expansion directions, and the movement of the next arm is constant based on the previous arm. This is a method of preventing sudden fluctuation by setting a width limit.

The one-way clutch mechanism may be of any type, but here, it is assumed that the one-way clutch mechanism is a ratchet that is simple and can transmit a large force. Consists of a combination of a coaxial inner race and outer race. A claw wheel is formed on the outer circumference of the inner race, and the claw is supported on the inner side of the outer race so that it can swing freely. It is what is being pressed. The one-way clutches of all the planetary gears meshed with the chain are not in the locked position.When a load is applied, the one-way clutch closest to the lock is locked and the planetary gear pulls the chain. Tell the driving force. Normally, due to the rotation of the lever, it is gradually locked during the revolution from the upper direction to the right direction of the drive shaft, and then gradually unlocked from there toward the lower direction of the drive shaft. In order to change the rotation speed of the planetary gear, the minimum required rotation angle of the lever at the required position created by the cam or crank is the half pitch of the planetary gear teeth to match the phase with the chain, and the ratchet More than the sum of the maximum backlash. Further, the planetary gear hub and the inner race of the one-way clutch, the outer race of the one-way clutch and the action point portion of the lever can be integrated. It is also possible to use the teeth of the planetary gear as it is as a one-way clutch claw wheel, and the one-way clutch may be interposed as a mechanism and does not need to be an independent member.

About a lever and a cam, the sliding friction of a lever and a cam can be reduced by mounting | wearing the sliding surface with one or several rollers rotatably. In addition, the cam can be asymmetrical so that the required behavior can be obtained. However, the cam can be made to have a simple circular shape, and a sliding ring can be applied to the outer periphery of the cam. It can also be reduced. Also, the eccentric direction of the cam is determined by the behavior of the insulator and is not limited to the right direction. The cam is not fixed to the main body frame, and the eccentric direction is changed in conjunction with the change in the revolution radius of the planetary gear. The relationship between the insulator and the cam may be a follow-up by a spring or a positive cam. Further, the shape of the surface in contact with the insulator cam is also determined by its behavior and is not limited to a flat surface.

The number of planetary gears is not limited to three. The planetary gears may be arranged in such a manner that the levers are alternately arranged in two rows so as to contact the cam, or the planetary gear shaft is tilted with respect to the drive shaft. If the number of gears is increased, the number of parts increases, but more stable driving is possible, and the shape of connecting the planetary gears is a polygon, and the revolution radius also changes, so a chain tensioner is necessary.
Further, a complementary member can be arranged between the planetary gears to make the polygonal shape closer to a circle.
In order to guide the chain smoothly to the planetary gear when the planetary gear is engaged with the chain, a chain guide is provided on the main body frame, or a chain guide disk having a diameter larger than that of the planetary gear and having an open end is attached to both sides of the planetary gear. Can also be arranged. Note that the planetary gear shaft does not necessarily have to be coaxial with the shaft that supports the action point portion of the lever so as to be rotatable about the axis. If the planetary gear shaft is arranged closer to the end than the supporting shaft, the planetary gear itself Can be swung in the revolving radial direction, and in addition to rotation, the chain can be fed by movement in the revolving radial direction. There is also a method in which the planetary gear shaft is simply provided at the center of the insulator, but as an example, the insulator itself can be integrated with the planetary gear shaft. In addition, since the chain feed is not constant due to changes in the position of the planetary gear and the rotation speed, the drive shaft and the rotating plate are not fixed, and a shock absorber such as a spring can be interposed to equalize the load on the drive shaft. .

It is desirable that a member for supporting the one-way clutch, such as a planetary gear shaft, is provided with a claw release guide for removing the one-way clutch claw. This means that when the lever rotates counterclockwise to a certain angle or more, the claws of the one-way clutch mounted on the outer race ride on this guide and are forcibly removed from the inner race. When the rotation is greater than the angle, the planetary gear is rotatable in both directions. This is because the difference in speed created by the insulator is canceled out by the reduction in the spacing between the planetary gears and smooth meshing does not function only when the planetary gears mesh with the chain while the revolution radius of the planetary gears is shrinking. It is an additional mechanism. As a simple structure, there is also a method in which the planetary gear is attached to the planetary gear shaft via a one-way clutch, and the guide for releasing the claw is released and operated by forward and reverse rotation of the lever at a certain angle.

By changing the output gear to several parallel gears with different radii, or by providing an existing transmission mechanism on the output shaft side, such as providing an internal transmission on the output shaft, a wider shift range can be realized, Also, even if this mechanism is also placed at the position of the output gear, the two mechanisms are engaged with a chain, and the revolution radius of each planetary gear is controlled to be inversely proportional, a wider speed change range can be realized.

As described above, the continuously variable transmission using the one-way planetary gear according to the present invention has a simple structure in which the chain and the gear mesh with each other, and can continuously transmit the driving force even at low speeds and high loads by shifting continuously. it can. If this is applied to a bicycle, it will be a bicycle that can always be driven with an optimal load without major modifications, simply by supplying it as a drive-side gear unit compatible with a chain wheel. Further, the rear wheel free wheel is not required.

For the purpose of explaining the principle, in the drawing, the shape of parts and the distance between parts are partially simplified and exaggerated, and well-known techniques are omitted. In FIG. 1, the main body frame 1 that supports the output shaft 2 and the main body frame 1 that supports the drive shaft 6 and the cam 5 are a continuous and integral frame. As a basic configuration, a chain tensioner 4 is attached to the main body frame 1 while being swingable and tensioned counterclockwise by a spring or the like, and an output shaft 2 is rotatably attached to the main body frame 1. The output gear 3 is fixed, the cam 5 is fixed to the required position in the right direction of the output gear 3 of the main body frame 1, and the drive shaft 6 is rotatably mounted at a position eccentric to the left from the center of the cam 5. The arm angle control plate 21 is mounted on the drive shaft 6 so as to be capable of relative rotation control, and the rotation plate 18 is fixed to the drive shaft 6. An arm shaft 19 is provided in parallel, and one end of the arm 20 is rotatably mounted around each of the shafts. A point on the arm angle control plate 21 opposite to one point on the arm 20 is connected by an arm angle control link 22. The other end of the arm 20 A planetary gear shaft 9 is provided in parallel with the moving shaft 6, and a planetary gear 7 is rotatably mounted on each of them, and the inner race 11 of the one-way clutch 10 is fixed to the planetary gear hub 8 in a clockwise rotation direction. An action point portion of one end of the lever 13 is fixed to the outer race 12 of the one-way clutch 10, one point on the lever 13 and one point on the arm 20 are connected by a cam follower spring 24, and the chain 14 is connected to the planetary gear 7 and the output gear 3. Hang over. Although omitted in FIG. 1, an arm angle control mechanism as shown in FIG. 11 is provided between the arm angle control plate 21 and the rotary plate 18, and the planetary gear shaft 9 has a claw engagement device as shown in FIG. 9. A guide 31 is provided.

The operation will be described below with reference to FIG. In the above configuration, when a driving force is applied to the driving shaft 6 in the clockwise direction, the planetary gear 7 revolves around the driving shaft 6 and the rotating plate 18 and pulls the meshed chain 14 to output the output gear 3. To transmit the driving force. Here, when the arm angle control plate 21 that normally rotates integrally with the rotating plate 18 is rotated relative to the rotating plate 18, the arm 20 is rotated around the axis of the arm shaft 19 by the arm angle control link 22. Then, the distance between the drive shaft 6 and the planetary gear 7, that is, the revolution radius of the planetary gear 7 changes, and the driving force is transmitted while changing the speed steplessly. The lever 13 revolves around the drive shaft 6 along with the planetary gear 7. However, since the cam 5 is eccentric to the right from the drive shaft 6, the right lever 13 approaches the cam 5 and rotates clockwise. The planetary gear 7 rotates in the clockwise direction via the one-way clutch 10, and the chain 14 is pulled at a combined speed of the rotation and the revolution around the drive shaft 6. The lower left and upper left insulators 13 move away from the cam 5 and rotate counterclockwise to rotate the outer race 12 of the one-way clutch 10 counterclockwise. As a result, no torque is applied to the lower left planetary gear 7, and the planetary gear 7 smoothly disengages from the chain 14. The upper left planetary gear 7 approaches the chain 14 and pushes teeth against the relatively fast chain 14. It is meshed at a position where the pitch is matched while freely rotating. With the above operation, it continuously rotates, shifts steplessly, and transmits driving force.

Other figures will be described below. FIG. 3 shows the positional relationship among the arm angle control plate 21, the arm angle control link 22, and the arm 20, and since the mechanism for relative rotation is well known and omitted, FIG. 11 shows an example of the mechanism. The crown angle gears 36 and 37 are fixed to the arm angle control plate 21 and the rotary plate 18, respectively. Both crown gears 38 are rotatably supported in the middle, and the arm angle control plate crown gear 36 is both crowns. The gear 38 is linked with a fixed pinion gear 39 whose position is fixed and rotatably supported. A rotating plate crown gear 37 is a movable pinion gear 40 that is movable and rotatably supported. It is linked to. If the moving pinion gear 40 is moved around the drive shaft 6 in this state, the rotating plate 18 and the arm angle control plate 21 rotate relative to each other. FIG. 4 is a front view of the case where the cam 5 is replaced with the crank 15 and one end of the insulator 13 and the crankshaft 41 are connected by the crank 15. When actually applied to a bicycle, the drive shaft 6 penetrates in the front direction. Therefore, the crankshaft 41 has a diameter for taking the drive shaft 6 into the crankshaft 41. 5 and 6 show the crank 15 and the cam 5, respectively. The first and second lever interlocking links 16 and 17 are interposed between the planetary gear 7 and the lever 13, that is, the rotation generated in the lever 13 is represented by a pantograph. This is a mechanism for transmitting and amplifying, and although the number of parts increases, it shows that the change of the revolution radius can be increased without being limited by the sliding of the lever 13 and the cam 5 and the length of the crank 15. FIG. 7 shows a method for realizing the change in the revolution radius with the slider 25. Since the sliding direction is slightly inclined with respect to the radial direction from the driving shaft 6, the driving load becomes a force in the sliding direction and the slider spring. Equilibrium with 26 repulsive forces. FIG. 8 is an example of an additional mechanism to the arm 20, and the upper part is a partial view in which the front disk is omitted when the chain guide disk 32 is attached, and the lower part suppresses a sudden movement by the absorber 27. What is shown on the right is an example of a mechanism in which the position of the arm 20 limits the movement of the next arm 20 in conjunction with the stopper 28. In FIG. 4 and subsequent figures, the arm angle control plate 21 is not used, and an arm angle control spring 23 is provided on the arm 20 so that the angle automatically varies in proportion to the load of the drive shaft 6. However, there is no necessity for mutual function for the purpose of simplifying the drawing. However, even when the arm angle control plate 21 is used, the arm angle control spring 23 has a function of helping the rotation of the arm angle control plate 21 by canceling the rotational force of the arm 20 by the driving force. The chain 14 is partially omitted. In FIG. 9, the claw release guide 31 is fixed to the planetary gear shaft 9, and the planetary gear 7 is reengaged with the chain 14 at the upper left position of the drive shaft 6. The outer race 12 fixed to the outer race 12 is greatly rotated in the counterclockwise direction, and the claw 30 of the one-way clutch 10 rides on the claw release guide 31 and is forcibly removed from the claw wheel 44 of the inner race 11, The planetary gear 7 fixed to the race 11 is rotatable in both directions. Therefore, at this position, the planetary gear 7 follows the chain 14 and meshes regardless of the relative speed difference between the planetary gear 7 and the chain 14. Thereafter, as the planetary gear 7 revolves from the upper side to the right side of the drive shaft 6, the lever 13 rotates in the clockwise direction, and the pawls 30 come off the pawls 31 and come into contact with the pawl wheel 44 of the inner race 11. And return to the original function. The nail hooking guide 31 may have other forms as long as it has the above function. FIG. 10 is a principle diagram when the buffer shaft 33 is interposed between the key 34 and the rotary plate 18 in the key groove 35 without fixing the drive shaft 6 and the rotary plate 18. FIG. 12 shows that the distance between the planetary gears can be further reduced by giving the planetary gear shaft 9 a slight angle with respect to the drive shaft 6. It has a helical gear shape and meshes with the pin of the chain 14 in a pseudo parallel manner. Further, the engagement can be made smooth by making the pin of the chain 14 into a spindle shape instead of a cylindrical shape. FIG. 13 shows an example in which the rotating shaft of the lever and the planetary gear shaft are not coaxial, and the lever and the planetary gear shaft are integrated. FIG. 14 shows an example of a mechanism for controlling the revolution radius of the planetary gear 7 by adjusting the gap between the conical wheels 45 opposed to each other by the transmission lever 46.

Front view showing the best embodiment Plan view Front view showing relationship between arm angle control plate and arm The top view which shows embodiment which replaced the cam with the crank Front view showing an embodiment in which an interlocking link is added to the crank The top view which shows embodiment which added the interlocking link to the insulator The front view which shows embodiment which performs the revolution radius control of a planetary gear with a slider Front view showing an example of an additional mechanism to the arm The partial top view which shows embodiment which provided the nail hook removal guide Front view showing an embodiment in which a cushioning material is provided between the drive shaft and the rotating plate Front view of a mechanism example for rotating the arm angle control plate relative to the rotating plate Front view showing an embodiment in which the planetary gear shaft has an angle. Front view showing an embodiment in which an insulator is integrated with a planetary gear shaft The top view which shows embodiment which controls a revolution radius by the clearance gap adjustment of an opposing conical wheel

DESCRIPTION OF SYMBOLS 1 Main body frame 2 Output shaft 3 Output gear 4 Chain tensioner 5 Cam 6 Drive shaft 7 Planetary gear 8 Planetary gear hub 9 Planetary gear shaft 10 One-way clutch 11 Inner race 12 Outer race 13 Insulator 14 Chain 15 Crank 16 First insulator interlocking link 17 Second lever interlocking link 18 Rotating plate 19 Arm shaft 20 Arm 21 Arm angle control plate 22 Arm angle control link 23 Arm angle control spring 24 Cam follow-up spring 25 Slider 26 Slider spring 27 Absorber 28 Stopper 29 Roller 30 Claw 31 Claw release guide 32 Chain guide disk 33 Buffer material 34 Key 35 Key groove 36 Arm angle control plate Crown gear 37 Rotating plate crown gear 38 Both crown gears 39 Fixed pinion gear 40 Moving pinion gear 41 Crankshaft 42 Rotating ring 3 leverage point shaft 44 the ratchet wheel 45 the conical wheel 46 shift lever

Claims (8)

A main body frame serving as a base; a cam mounted on the main body frame; an output gear rotatably supported with respect to the main body frame; a drive shaft rotatably supported with respect to the main body frame; On the other hand, a plurality of planetary gears that can be controlled to rotate and rotate in a radial direction on a plane orthogonal to the drive shaft, and each planetary gear is rotated in one direction via a one-way clutch mechanism. A continuously variable transmission using a one-way planetary gear, comprising a lever that is supported so as to be linked, and whose end swings to be linked to the cam, and a chain that engages the output gear and the planetary gear. . A main body frame serving as a base; an output shaft and a drive shaft that are rotatably supported with respect to the main body frame; and two cams attached to the main body frame corresponding to each of the output shaft and the drive shaft; , A plurality of planetary gears that can be controlled to move in a radial direction on a plane perpendicular to the respective axes with respect to the output shaft and the drive shaft, and are rotatably supported, and a one-way clutch for each of the planetary gears. The rotation in one direction is supported through a mechanism, and the swing of the end portion is linked to the cam corresponding to either the output shaft or the drive shaft that supports each associated planetary gear. A continuously variable transmission using a one-way planetary gear, comprising: a lever arranged to support the planetary gear supported by the output shaft; and a chain engaged with the planetary gear supported by the drive shaft. A main body frame serving as a base, a crankshaft provided on the main body frame, an output gear rotatably supported on the main body frame, a drive shaft rotatably supported on the main body frame, and the drive shaft On the other hand, a plurality of planetary gears that can be controlled to rotate and rotate in a radial direction on a plane orthogonal to the drive shaft, and each planetary gear is rotated in one direction via a one-way clutch mechanism. A continuously variable transmission using a one-way planetary gear comprising: a lever supported so as to be linked; a crank connecting the end of each lever and the crankshaft; and a chain engaged with the output gear and the planetary gear. . A main body frame serving as a base, an output shaft and a drive shaft rotatably supported on the main body frame, and two crankshafts provided on the main body frame corresponding to each of the output shaft and the drive shaft; A plurality of planetary gears supported so as to be able to move and rotate in a generally radial direction on a plane orthogonal to the respective axes with respect to the drive shaft and the output shaft, and a one-way clutch mechanism for each of the planetary gears And a crankshaft corresponding to an output shaft or a drive shaft for supporting each planetary gear to which the lever is linked, and an end portion of each of the levers. A continuously variable transmission using a one-way planetary gear, comprising: a connecting crank; the planetary gear supported by the output shaft; and a chain engaged with the planetary gear supported by the drive shaft. The continuously variable transmission using a one-way planetary gear according to claim 3 or 4, wherein the crank can be extended and contracted by an expansion and contraction control mechanism. 6. A continuously variable transmission using a one-way planetary gear according to claim 1, wherein a one-way clutch mechanism is provided with a claw release guide. The continuously variable transmission using a one-way planetary gear according to any one of claims 1 to 6, wherein movement control of the position of the planetary gear with respect to the drive shaft is linked to a load of the drive force. 8. The continuously variable transmission using a one-way planetary gear according to claim 1, wherein the planetary gear shaft has an angle with respect to the drive shaft, with a straight line passing through the center of the planetary gear orthogonal to the drive shaft as a rotation shaft.

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