JPH03272351A - Continuously variable automatic transmission - Google Patents

Abstract

PURPOSE:To perform automatic speed change when a load is fluctuated by reducing the effective radius of a drive sprocket through compression of a spring togetherwith a claw holding plate by means of a component of force exerted in the direction of the center of a drive shaft, in a drive sprocket in the vicinity of the maximum point of drive force. CONSTITUTION:When a load exerted on a rear wheel is increased and tension exerted on a chain 32 is also increased, the component of force by means of which a spring 46 is compressed is increased, and the center of a drive sprocket 11 itself is moved to a position C2. In this case, since the center of a drive shaft itself is still located in C1, the effective diameter of a drive sprocket 11 is decreased as shown by R2, a step-up ratio R2/r of a gear is decreased to a value lower than R1/r when a drive force is low, and easy drive is practicable even when a load is high. Since a relation between the load and a gear ratio is decided by the strength of the spring 46, selection is made such that the effective diameter R2 is minimized when a drive force is maximized.

Description

Detailed Description of the Invention [Industrial Application Field] The present invention is applicable to a power transmission system, such as a bicycle drive device, in which the driving force is approximately constant and the load fluctuates greatly. This invention relates to a device that can automatically and steplessly change the speed between the two speeds depending on the magnitude of the driving force.

[Prior Art] Transmission devices mainly used for bicycles have been put into practical use that switch chains between gears with a plurality of fixed transmission ratios, but they are difficult to operate and can only be changed in stages. I can't. Furthermore, although continuously variable transmission devices have been proposed in the past, many of them have complicated structures and are not suitable for bicycles.

In addition, in a power transmission system where the driving force on the driving side is almost constant, and the driving force and speed required by the driven side vary, such as a drive system that connects the engine and wheels of a small car, multiple transmissions are used. A device that changes speed between gears with a fixed speed ratio has been put into practical use, but it is cumbersome to operate manually and the speed can only be changed in stages.

[Problems to be Solved by the Invention] An object of the present invention is to provide an automatic transmission device that has a simple structure and can steplessly and automatically change gears when the load fluctuates. .

[Means for Solving the Problems] In order to solve the above problems, the present invention includes a plurality of sets of power transmission arms and spring holders extending radially from a drive shaft, and a plurality of sets of power transmission arms and spring holders that are slidable in the radial direction inside them. A power transmission device consisting of a left and right pair of a claw holding plate, a spring that drives the claw holding plate outward from the shaft, and a stopper that prevents the claw holding plate from deviating from the outer end of the power transmission arm and the spring holder. An annular drive sprocket installed in the space of the arm and spring holder, sprocket teeth provided on the outer periphery of the drive sprocket, pinion teeth provided on the inner periphery, and the pawl retainer so as to be able to be held against the pinion teeth. A claw provided on a plate, a wave sprocket rotatably mounted on a driven shaft located at a distance from the driving shaft, a chain suspended between the driving sprocket and the driven sprocket, and a chain in operation. It is equipped with a tension pulley to tighten the tension.

In addition, in the second embodiment, a plurality of sets of arch-shaped elastic power transmission members each having one end fixed to a hub attached to the drive shaft and the other end extending in the radial direction, and a pawl retaining plate attached to the tip thereof, are used. , a pawl plate pivoted inside the pawl holding plate, a spring that drives the pawl plate in a radially outward direction, gear teeth provided on the outer periphery of the annular gear body, and binion teeth provided on the inner periphery of the annular gear body. A driving gear assembled so that the pawl plate of the pawl holding plate at the tip of the arch-shaped elastic power transmission member can engage with the pinion surface is directly connected to a driven shaft provided at a position away from the driving shaft. and a driven gear arranged so as to maintain a predetermined distance without directly meshing with the gear teeth provided on the outer periphery of the driving gear, meshing with the gear teeth provided on the outer periphery of the driving gear and the gear teeth on the outer periphery of the driven gear, The gear teeth installed on the outer periphery of the annular gear body of the drive gear are movable in a direction perpendicular to the line connecting the drive shaft and driven shaft to maintain meshing even when the center of the gear teeth deviates from the drive shaft. The vehicle is equipped with a continuously variable automatic transmission consisting of a transmission vehicle and a transmission vehicle.

In the third embodiment, a plurality of sets of arch-shaped power transmission members are provided, and one end of each power transmission member is attached to a hub attached to a drive shaft so as to be rotatable in a plane perpendicular to the hub axis; The other end of the power transmission member is equipped with a pawl holding plate rotatably pivoted so that the ratchet located at the tip always engages with the pinion teeth in a normal state. A ratchet ffl and a spring that biases it toward the binion teeth are housed in the recess that accommodates the ratchet teeth, and a ratchet tooth deviation prevention fitting is provided, and the arch-shaped power transmission member is determined by the distance between the center of the hub shaft and the ratchet teeth. A spring is driven to counteract the rotation when the actual rotation radius is reduced, and a pinion is provided on the inner periphery of the gear body of the ring rod when the load on the driven gear is small. and a spring for returning the arch-shaped power transmission member so that the effective radius of rotation by the distal end ratchet teeth of the plurality of power transmission members in contact with the teeth are approximately equal.

[Action] When the load applied to the driven sprocket becomes large, a large force is applied to the drive sprocket via the chain, and the force acting toward the center of the drive shaft on the drive sprocket near the maximum driving force causes the claw retaining plate to At the same time, the spring is compressed to reduce the effective radius of the drive sprocket. The rotation of the power transmission arm, which is integrated with the drive shaft, is transmitted to the pinion teeth of the drive sprocket by the pawl on the pawl holding plate, but as the drive sprocket becomes eccentric and the rotation speed becomes slower than the rotation speed of the power transmission arm, the rotation speed is sequentially transmitted to the pinion teeth and the pawl. This causes slippage and is absorbed.

In the second embodiment, when the load applied to the driven shaft increases, a large force is applied to the drive shaft, and the force acting toward the center of the drive shaft on the drive sprocket near the maximum driving force causes the pawl retaining plate to Compressing the spring reduces the effective radius of the drive sprocket. The rotation of the power transmission arm, which is integrated with the drive shaft, is transmitted to the pinion teeth of the drive sprocket by the pawl on the pawl holding plate, but as the drive sprocket becomes eccentric and the rotation speed becomes slower than the rotation speed of the power transmission arm, the rotation speed is sequentially transmitted to the pinion teeth and the pawl. This causes slippage and is absorbed.

[Embodiments] <First Embodiment> FIG. 1 is a diagram showing the basic configuration of a first embodiment of a continuously variable transmission device of the present invention for a power transmission device for a bicycle.

A shown by a solid line in the same figure shows the relationship between the gears and the chain when the pedals are not driven, and b shown by the broken line in the same figure shows the relationship between the gears and the chain when the driving force is the largest.

In FIG. 1, 11 is a driving sprocket, 12 is a crank for driving the driving sprocket, and a pair of pedals 13 are provided. The crank is rotatably attached to a chain stay 31 that constitutes a part of the bicycle body about an axis c1.

The driven sprocket 21 is attached to the rear wheel of the bicycle, and is pivoted on the rear two shafts c3 of the chainstee 31. A chain 32 is used to transmit power from the driving sprocket 11 to the driven sprocket.

The drive sprocket 11, which forms the central part of the present invention, is not directly connected to the crankshaft, as will be described later.
Since they are connected via a spring device, the center of the drive sprocket 11 moves between 01 and 02 depending on the driving force. Therefore, the position of the chain 32 also moves according to the strength of the driving force, as illustrated in a and b, and the length between them also changes. A tensile pulley device 24 tensions the chain so that it does not slacken during operation, since if the chain becomes loose it may come off the sprocket.

The tension pulley device 24 includes an arm 26 pivoted on the shaft c3, a tension pulley 25 pivoted on the other end, and a spring device that applies a counterclockwise force to the arm 26 to tension the chain. It can be configured by

The tensilon pulley device 24 uses an arm 27 that runs a chain between two pulleys 28 and 29 in an S-shape, as shown in FIG. It is possible to use a type that is loaded and tensioned with a spring.

FIG. 3 is a diagram for explaining the basic operating principle of the present invention. When the driving force is small, the rotation center of the drive sprocket 11 is the drive shaft C1, as shown in FIG.
As is clear from the same figure (C), the gear ratio is close to R1/r and the speed increasing ratio is large.

However, when the load on the rear wheel increases and the tension on the chain to drive it also increases, as shown in FIG. In this direction, the component of the force toward the center of the drive shaft increases, and the center of the drive sprocket 11 itself moves to the position C2.

In this case, since the center of the drive shaft itself is still at CI, the effective diameter of the drive sprocket 11 is
) becomes smaller as shown by R2, and therefore the same figure (
As can be understood from C), the gear speed increasing ratio R2/r is
This is smaller than R1/r when the driving force is small, and it is possible to easily drive even a large load.

The relationship between the load and gear ratio described above is determined by the strength of the compression force of the spring 46, so the effective diameter of the drive sprocket 11 becomes Choose to be the minimum.

By the way, in the present invention, as is clear from the above explanation of the operation related to FIGS. 1 and 3, when the driving force increases, the center of the drive sprocket 11 becomes eccentric downwardly and rearward with respect to the center of the pedal shaft. do. Furthermore, as the pedal shaft rotates, the driving sprocket 11 also rotates, and as it rotates, the pawls 48 of the pawl holding plate 47 inside each power transmission arm 44 and the pinions on the inside of the driving sprocket rotate as the pedal shaft rotates. The contact with the tja 49 moves and does not remain in a fixed position. Therefore, special structural measures are required in order to transmit the driving force from the pedal to the inner diameter portion of the drive sprocket through the power transmission arm while allowing such positional fluctuations.

Figure 4 is a diagram for explaining one embodiment of a structure for transmitting driving force from the pedal to the inner diameter portion of the drive sprocket through the power transmission arm, and Figure 5 is an enlarged view of one power transmission arm. FIG.

4 and 5, reference numeral 41 denotes a drive shaft, and a pedal crank (not shown) is provided coaxially with the center CI of the drive shaft. From the hub 42 of the drive shaft to the radiation wand,
A plurality of drive arm devices ft43 each having a pair of power transmission arms 44 and spring holders 45 are provided at equal angles.

In the embodiment shown in FIG. 4, the number of drive arm devices 43 is five, but the number is not limited to this.

If the number of drive arm devices is too small, the transmission of driving force from the drive sprocket to the drive arm device will be concentrated,
Excessive stress may be applied, and the movement of the drive sprocket 11 may not be smooth. On the other hand, a large number of drive arm devices complicates the structure and increases manufacturing costs. Therefore, it is desirable to design with smooth operation and mechanical force distribution in mind.

The power transmission arm 44 and the spring holder 45 are arranged in parallel and are configured to hold a spring 46 therein. For this reason, it is desirable that the inside of the spring holder be molded into a shape that matches the outer shape of the spring. Normally, circular coil springs are easily available and have good performance characteristics, so if this is used, the inner shape of the spring holder should also be an arc with an inner diameter slightly larger than the outer diameter of the spring. This is desirable.

However, it is of course possible to use springs of other shapes, in which case the inner shape of the spring holder would also be adapted to the outer shape of the spring.

The propulsive force applied by the pedal is transmitted to the power transmission arm 44 via the crankshaft 41, and is transmitted to the power transmission arm 44 via the crankshaft 41, and is transmitted to the claw holding plate 47 and the claw 48.
Through this, pinion teeth 49 provided inside the drive sprocket are pushed to generate rotational force.

When the propulsive force is small, the force applied to the chain is small, and therefore the force applied to the drive sprocket is also small, so the rate at which the drive sprocket pushes the spring and causes its center to deviate from the crankshaft is small. If the deviation is extremely small in such a state, the claw holding plate 47 of each drive arm device will
At a position approximately equidistant from the center during rotation of the crankshaft, a pawl 48 pushes against a pinion tooth 49 on the inner periphery of the drive sprocket 11, with the pawl located at or near the same tooth. In other words, the angular velocity of the drive arm device 43 and the angular velocity of each part of the drive sprocket become equal.

When the propulsive force increases, if a force toward the center of rotation of the crankshaft is applied to the drive sprocket near the point of application where the driving force is maximum, this is where the force is most transmitted from the power transmission arm to the chain. Become dominant.

On the other hand, the vector sum of the backward bowing force due to the reaction of the force applied to the chain and the force acting to reduce the effective radius of the drive sprocket as shown in Figure 3 (b), R2, is applied to the drive sprocket. In FIG. 3C, the center of the drive sprocket is displaced to the position indicated by 02. This reduces the effective radius of the drive sprocket, but conversely, the radius portion facing it becomes effectively large.

However, in this part, the force 4 applied to the chain is small and it does not engage with the sprocket teeth on the outside of the drive sprocket, so it is not affected by the difference in chain speed due to the difference in effective radius. Even though the circumferential speed of the sprocket itself is constant in each part, there is a component that moves away from the center of the drive arm device, so the relative speed is greater at the position of the pawl on the pawl holding plate than on the drive side. Become. Therefore, the angular velocity of the drive arm device and the angular velocity of the drive sprocket are partially different. When the driving force is large, the speed of the lower portion of the drive sprocket is greater than the speed of the pawl of the pawl retaining plate, so that the pawl changes its relative position while sliding on the pinion teeth. However, as the pawl approaches the point of application of the driving force, it becomes less likely that the pawl will slip on the pinion teeth, and near the point of application, the pawl will engage with the pinion teeth on the inner circumference of the drive sprocket and transmit the driving force. will contribute to this.

The driving sprocket is preferably made of steel, and the sprocket teeth and pinion teeth are treated by induction hardening or the like.

6 is a partial sectional view taken in the direction shown by line 6-6 in FIG. 5, and FIG. 7 is a partial sectional view taken in the direction shown by line 7-7 in FIG. Claw holding plate 47 to be attached
FIG.

In this embodiment, the pawl holding plate 47 is U-shaped and rotatably supports one side of the pawl 48 at its bottom, and applies an outward force using means such as a spring so that the pawl 48 can come into contact with the pinion teeth 49. be able to do so. In other embodiments, the pawl retaining plate 47 includes:
It may be composed of a flat plate with a large thickness. Although not shown, it is desirable to provide stopper means for the pawls, springs, and other means to prevent the pawls from easily falling off during tasseling and disassembly. - For example, the pawl is the pawl retaining plate 47
The means for achieving this is a structure in which the spring is pivoted to the U-shaped bottom of the spring, and the spring is inserted into a groove provided in the bottom.

The claw holding plate 47 disposed at the tip of the spring 46 is
As the drive arm device 43 rotates, it reciprocates in the axial and radial directions inside the drive arm device,
Moreover, since a strong driving force is transmitted, it is necessary to devise measures to enable smooth movement.

For this reason, the power transmission arm 4 constituting the drive arm device 43
4 and the inside of the spring holder 45 are finished flat,
A space is provided between the nail holding plate 47 and the outside thereof, and steel balls 61, 62, 63 are arranged as in the illustrated example. Recesses 64 for accommodating steel balls are provided at required locations on the pawl holding plate 47 to support the balls and reduce the above-mentioned spacing. This part can be designed as a pole bearing with linear motion.

Further, a stopper 67 shown in FIG. 6 is provided to prevent the claw holding plate from falling off the tip of the drive arm device. The stopper 67 is dimensioned to prevent the claw retaining plate from being pulled out beyond the tip of the drive arm device, and to allow the chain to freely move in and out of the drive arm device.

In FIG. 7, there is one pawl, but a plurality of pawls may be provided in order to reduce the load of transmitted force. In this case, multiple pawls with the above structure can be installed in parallel, but instead, multiple pawls corresponding to the multiple teeth on the pinion surface are provided integrally, so that these pawls simultaneously engage the pinion. It may be spring loaded so that it can engage and slide over multiple teeth of the tooth.

Although not shown in the side view of FIG. 4, a sixth An annular member as shown at 68 in the figure can be fixed by means such as screws. A disc-shaped member may be used instead of the annular member.

In the present invention, the limit of the speed change ratio is determined by the movement range of the drive sprocket, and therefore the achievable speed change range is limited, but it is possible to cover a practically sufficient range.

Furthermore, by making the width of the gear teeth on the drive sprocket slightly narrower than normal, smooth engagement between the drive sprocket and the chain can be achieved even at the maximum gear ratio. Instead of making the width of the gear teeth slightly narrower than usual, we also make the diameter of the chain rollers slightly smaller than usual.
A similar effect is obtained with l'.

<Second Embodiment> FIG. 8 is a diagram showing the principle basic configuration of a second embodiment of the present invention, and shows a state where the load on the driven shaft is small.

In FIG. 8, reference numeral 10 denotes a frame of the continuously variable transmission, on which the shaft of the driving sprocket of the driving gear 11, the driven gear 12, and the shafts and bearings of the arm 14 on which the transmission gear 3 is mounted are mounted. , used as a base for assembling each component of the transmission.

The shape of the frame is simply shown as a rectangular plate-like structure in the figure for simplicity, but if normal transmission of power of the assembled device is possible.

There are no particular restrictions on the shape. In order to increase the mechanical strength and reduce the weight of the frame itself, it is possible to have a lightweight structure, for example, by welding materials such as pipes.

FIG. 9 shows a top view of the apparatus of FIG. 8, with identical parts designated by the same reference numerals. 8 and 9, a shaft hole 141 is provided at one end of the arm 14 of the transmission gear 13, and a hollow shaft 1 is provided around the shaft 121 of the driven gear 12.
22 via a spacer 123.

A flange 124 is screwed to the tip of the hollow shaft 122 to allow the arm 14 to rotate smoothly in a plane perpendicular to the center line of the shaft 122, and to prevent axial movement. , a shaft 131 is provided via a ball bearing 132, and a transmission gear 13 is mounted on this shaft. The transmitting gear 13 meshes with the driven gear 12, and the distance between the axes of the transmitting gear and the driven gear is selected so that satellite movement is possible by rotation of the arm 4 about the shaft 121.

The inner diameter of the hollow shaft 122 is selected to be larger than the outer diameter of the shaft 121 to prevent loss of conductive force due to N friction.

The transmission gear 13 needs to mesh with the driven gear 12 and at the same time always mesh with the drive gear 11, respectively.

As explained below, when each gear is arranged as shown in FIG. 8, the arm 14 of the transmission gear 13 is in the position shown, and the rotation direction of each wheel is as shown by the arrow shown in the figure. Then, when the load on the driven gear 12 becomes large, the transmission gear 13 automatically drives the transmission gear diagonally downward and to the right in the figure, and always enables meshing. However, when the arm 14 of the transmission gear 13 moves counterclockwise due to a sudden change in load, there is a risk that the engagement between the drive gear 11 and the transmission gear 13 will be interrupted. For this reason, it is desirable to apply a bias tension to the arm 14 with a spring or to provide a damper so as to apply a clockwise rotational force.

The driven gear 12 rotates around its shaft 121, but the drive gear 11 is not directly connected to the shaft 111, and the teeth of a drive sprocket provided on the inner periphery of the drive gear 11, that is, on the center side, are It is driven by an eccentric drive wheel 15 rotated by 111.

The driving gear 11 rotates counterclockwise as shown by an arrow 111, and accordingly the transmission gear 13 rotates clockwise as shown by an arrow 13a, so that the driven gear 12 rotates counterclockwise. shall be.

While the load on the driven gear is small, the center of rotation of the drive gear 11 is approximately equal to the center of the shaft 111. On the contrary, when the load is maximum, the center of rotation of the driving gear 11 is not the center of the shaft 111, but moves away from the center of the driven gear, as shown in FIG. Along with this, the transmission gear 13 has a driving force applied to the center of rotation of the eccentric drive wheel due to the tension of the spring acting on the arm 14, and the drive gear 1 moves according to the driving force.
The center of 1 moves.

FIG. 11 is a diagram showing details of the eccentric drive wheel 15 and the drive sprocket of the drive gear 11.

A hub 151 is directly connected to the shaft 111, and fixes one end of a plurality of sets of arch-shaped elastic power transmission members. A claw holding plate is attached to the tip of the arch-shaped elastic power transmission member so as to be rotatable by a predetermined angle around a shaft.

One end of the claw plate is attached to the inside of the claw holding plate by a shaft so that the other end of the claw plate can rotate. A spring is installed between the pawl holding plate and the pawl plate in order to drive the other end of the pawl plate in a radially outward direction of the arch-shaped elastic power transmission member.

The annular drive gear 11 has gear teeth provided on the outer periphery of the main body and pinion teeth provided on the inner periphery of the main body. The pawl plate of the pawl holding plate at the tip of the arch-shaped elastic power transmission member is assembled so as to be engageable with the pinion teeth.

When the load on the shaft of the driven gear 12 is small, the shaft 1
The distance from the center of 11 to the tip of the nail plate is approximately the same in all of the plurality of arch-shaped elastic power transmission members.

Third Embodiment> FIG. 12 is a diagram showing the configuration of a third embodiment of the present invention. In this embodiment, the same combination of gears as in the second embodiment is used, but the structures of the eccentric drive wheel 15 and the drive sprocket of the drive gear 11 are changed in order to increase the driving force.

The eccentric drive wheel 115 includes a hub 112 attached to a drive shaft 111 with a plurality of hub axles 114 equidistant from and at equal angles from the axle center 113. The hub axis is parallel to the drive axis.

The arch-shaped power transmission member 116 is mounted on one end of the plurality of hub shafts by a bearing 117 so as to be rotatable in a plane perpendicular to the shaft.

At the other end of the power transmission member, there is a claw holding plate 11 pivoted on the tip thereof.
8 will be provided. Inside the pawl holding plate, ratchet teeth 119 are housed in recesses 120 that accommodate the ratchet teeth and springs 121 that bias the ratchet teeth toward the pinion teeth.

As a result, the ratchet teeth 119 are constantly pushed by the spring 121 in a direction approaching the pinion teeth, but a deviation prevention fitting 122 is provided to prevent the ratchet m from protruding excessively from the pawl holding plate and falling off.

The arch-shaped power transmission member is displaced by a spring 123 installed between the hub and the power transmission member so that the tip of the power transmission member is at the maximum rotation radius position.

When the load on the driven gear is small, the annular gear body 130
The ratchets tA at the tips of the plurality of arch-shaped power transmission members that are in contact with the binion surface 131 provided on the inner periphery of the ratchets tA are located at positions such that the effective radius of rotation is approximately equal and the radius of rotation is maximum. .

When the load on the driven gear increases, the eccentric drive wheel becomes eccentric so that the effective rotation radius determined by the distance between the center of the hub shaft and the ratchet teeth is reduced at the position where it meshes with the transmission gear.

When the load is maximum, the eccentricity is greatest.

At this time, the radius on the line connecting the center of the shaft and the position where it meshes with both transmission wheels is the minimum, and the radius on the opposite side is the maximum.

As a result of this change in the effective radius, at a position where the radius becomes smaller, the arch-shaped power transmission member is rotated so that the effective radius becomes smaller by /h against the spring 123 installed between the hub and the power transmission member. On the other hand, in the portion where the radius increases, the arch-shaped power transmission member is driven by the spring, and the effective radius of rotation increases.

This change in effective radius occurs with the rotation of the hub equipped with the arched power transmission member, and the portion where the radius is small causes the pinion teeth to be driven by the ratchet surface at the tip of the power transmission member, and the portion where the radius is large Because the effective radius is large in this part, and therefore the peripheral speed of the tip ratchet tooth part of the power transmission member is large,
It advances over the teeth until it matches the speed of the pinion surface on the inner circumference of the eccentric drive wheel.

[Effects of the Invention] As is clear from the above description, the present invention automatically adjusts the effective radius of the drive sprocket according to the size of the drive load without operating a special transmission device. Even on steep slopes, the effective driving force is increased, although the speed is slower on uphill slopes, and the speed is increased on slopes and flat areas, making it possible to travel easily.

In addition, although the first embodiment has been described as a bicycle drive device, it is also suitable for use in driving a variable load while automatically changing the speed steplessly using a drive source with a substantially constant output.
-Can be applied to boat fishing. The second embodiment can be used as a power transmission device with a relatively small driving force to drive a variable load while automatically changing speed steplessly.

Since the third embodiment uses an arch-shaped power transmission member, it is suitable for use as a power transmission device with a large driving force and for driving a variable load while automatically changing the speed steplessly.

[Brief explanation of drawings]

FIG. 1 is a configuration diagram for explaining the operating principle of the present invention,
Figure 2 shows a tensilon pulley with a chain running in an S-shape between two boars to load and tension it, and Figure 3 shows the driving force applied from the pedal to the inner diameter of the drive sprocket through the power transmission arm. FIG. 4 is a diagram for explaining an example of a structure for transmitting driving force from a pedal to an inner diameter portion of a drive sprocket through a power transmission arm. Figure 5 is an enlarged view of one power transmission arm, and Figure 6 is an enlarged view of one power transmission arm.
FIG. 7 is a partial cross-sectional view taken in the direction indicated by line 6-6 in the figure.
6 is a partial cross-sectional view taken along the line 7-7 in FIG. 5. FIG. Fig. 8 is a configuration diagram for explaining the operating principle of the second embodiment of the present invention, Fig. 9 is a top view of the second embodiment, and Figs. FIG. 12 is a diagram showing a third embodiment of the present invention. 11... Drive sprocket, 12--Fist crank, 13e*e pedal, 21...-m
Dynamic sprocket, 24--Tension pulley device, 25.28.29...Tensilon pulley 26.27
11... Tensilon arm, 28. 29- Tensilon pulley 31- Chain stay, 32... Chain, 32b... Chain position when the driving force is large, 41. @Φ drive shaft, 42.・・Drive shaft hub, 43・・O drive arm device, 44・・Power transmission arm, 45・11 @ Spring holder 46・・Spring, 47・Fist/claw holding plate, 48・Claw, 49・・・Pinion tooth, 61, 62, 63・・・W4 ball, 64111
1φ bowl housing recess, 67@fist/claw holding plate stopper 68...φ ring-shaped or disc-shaped member. 28.29... Tensilon pulley 31... Chain stay, 32... Chain, 32bφ... Chain position when driving force is large, 41-... Drive shaft, 42... Drive shaft hub, 43... ... Drive arm device, 44-... Power transmission arm, 4511... Spring holder 46... Spring, 47... Claw holding plate, 48... Claw, 49@- Fist pinion tooth, 61.62. 63φ・Ball made by Steel Corporation, 64・Ball accommodating recess, 67・Fist/claw holding plate stopper 680−・Annular or disk-shaped member. (a) (b) Figure 3 Figure 1 Figure 4 Figure 5 Figure 81! I Figure 6 Figure 10 Figure 7

Claims (1)

[Claims] 1. A plurality of sets of power transmission arms and spring holders that extend radially from the drive shaft, a pawl holding plate that is slidable in the radial direction inside these, and a pawl holding plate that extends radially outward from the shaft. a spring that is driven by a spring; a stopper for preventing the claw retaining plate from deviating from the outer ends of the power transmission arm and the spring holder; a drive sprocket, chain sprocket teeth provided on the outer periphery of the drive sprocket, and pinion teeth provided on the inner periphery of the drive sprocket;
A pawl provided on the pawl holding plate so as to be able to engage with the pinion teeth, a driven sprocket rotatably mounted on a driven shaft provided at a position remote from the driving shaft, a driving sprocket, and a driven sprocket. A continuously variable automatic transmission consisting of a chain suspended between the chain and a tension pulley for tensioning the chain during operation. 2. One end is fixed to the hub attached to the drive shaft, and the other end consists of multiple sets of arch-shaped elastic power transmission members extending in the radial direction, a pawl holding plate fixed to the tip, and a shaft inside the pawl holding plate. The attached pawl plate, the spring that drives the pawl plate in the radial outward direction, the gear teeth provided on the outer periphery of the annular gear body, the pinion teeth provided on the inner periphery, and the arch-shaped elasticity with respect to the pinion teeth. A driving gear assembled so that the pawl plate of the pawl holding plate at the tip of the power transmission member can be engaged, and a gear provided on the outer periphery of the driving gear and directly connected to a driven shaft provided at a position away from the driving shaft. The driven gear is arranged so as to maintain a predetermined distance without directly meshing with the teeth, and the driven gear meshes with the gear teeth provided on the outer periphery of the driving gear and the gear teeth on the outer periphery of the driven gear. A stepless automatic transmission consisting of a transmission gear mounted so that it can move in a direction perpendicular to the line connecting the drive shaft and driven shaft so as to maintain meshing even when the center of the gear teeth deviates from the drive shaft. gearbox. 3. A plurality of sets of arch-shaped power transmission members are provided, one end of each power transmission member is attached to the hub attached to the drive shaft so that it can rotate in a plane perpendicular to the hub axis, and the other end of the power transmission member is is equipped with a pawl holding plate rotatably pivoted so that the ratchet located at the tip always engages with the pinion teeth in a normal state, and the pawl holding plate has a recess for storing the ratchet teeth. The ratchet teeth and the spring that biases them toward the pinion teeth are housed inside, and a fitting to prevent ratchet teeth from slipping is provided. a spring that is driven to oppose the rotation when the driven gear is rotated as shown in FIG. 3. The continuously variable automatic transmission according to item 2, further comprising a spring that returns the arch-shaped power transmitting member so that the effective rotation radius of the ratchet teeth at the distal end thereof is approximately equal.