JP7678543B2 - Power transmission device and rotary drive device using the same - Google Patents

Description

The present invention relates to a power transmission device that transmits rotational motion from a drive source to an output rotor, and a rotary drive device that uses the same.

As an example of this type of power transmission device, Patent Documents 1 and 2 describe a power transmission device in which a connecting pin is provided at the peripheral end of a rotating disk rotated by a drive source, which is movable in the radial direction of the rotating disk, this connecting pin and a gear box are connected and pivoted by a connecting rod, alternating plate gears are formed on the upper and lower inner surfaces of the gear box, an output rotating shaft equipped with gears that mesh with these plate gears is supported through the gear box, and this output rotating shaft is configured to rotate in only one direction by the piston movement of the gear box.

With this type of power transmission device, the connecting pin can be moved in the radial direction of the rotating disk to transmit the rotational motion from the drive source to the output rotating shaft with infinitely variable speed.

The applicant has also proposed a power transmission device in which load fluctuations are not directly transmitted to a drive source (Patent Document 3). This power transmission device is rotatable around an output rotating shaft as a fulcrum, and is equipped with four arms connected to the output rotating shaft via one-way clutches as one-way rotation mechanisms, four tension coil springs as elastic bodies that bias the four arms in the power transmission direction of the one-way clutches, a drive rotating shaft that is parallel to the output rotating shaft and rotates by a drive source, and four pins that are connected parallel to the drive rotating shaft so as to rotate together with the drive rotating shaft and can abut against the tips of the four arms.

JP 2000-110912 A JP 2006-161999 A Patent No. 5945584

However, in the power transmission devices described in Patent Documents 1 and 2, the drive source and the output rotating shaft are mechanically connected without play by a connecting rod, a plate gear, and a gear, so that the torque fluctuation of the load applied to the output rotating shaft is directly transmitted back to the drive source, and the drive source is significantly affected by the load fluctuation. For this reason, it is necessary to use a drive source that has output torque characteristics large enough to absorb such load fluctuations on the output side, or to change the torque transmitted to the output rotating shaft in response to the load fluctuations by operating a speed change mechanism provided midway.

In addition, the power transmission device proposed by the applicant and described in Patent Document 3 has the disadvantage that the four one-way clutches are always in operation when rotated by the drive source, resulting in a low lifespan of the one-way clutches and a low durability of the power transmission device.

The present invention aims to eliminate the above-mentioned disadvantages of the conventional technology, and its purpose is to provide a power transmission device that can be driven directly or indirectly and in which load fluctuations are not directly transmitted to the drive source, and a rotary drive device using the same.

Another object of the present invention is to provide a power transmission device and a rotary drive device using the same that can automatically obtain a continuously variable speed function without manual operation and can improve durability.

According to the present invention, there is provided a drive shaft rotated by a drive source, a rotating arm having one end attached to the drive shaft via a one-way rotation mechanism and rotating together with the drive shaft, an output rotor provided on a support shaft on the same axis as the drive shaft, a plurality of rotating shafts parallel to the drive shaft and evenly provided on the outer periphery of the output rotor, a plurality of pivot arms that can rotate about each of the plurality of rotating shafts as a fulcrum and are provided on the plurality of rotating shafts via a plurality of one-way rotation mechanisms, and whose tip end can abut against the other end of the pivot arm, a plurality of elastic bodies that bias the plurality of pivot arms in the power transmission direction of the one-way rotation mechanism, and a plurality of first biasing members provided on the plurality of rotating shafts, A power transmission device is provided that is configured such that, when a load equal to or greater than a predetermined value is applied to the output rotor, each of the multiple rotating arms is pushed back in a direction opposing the biasing force of each of the multiple elastic bodies by the pressure of the rotating arm when the tip of the rotating arm abuts against the output rotor, storing elastic energy in the elastic body, and when the tip of the rotating arm is released from the abutment, the biasing force of the stored elastic energy of each of the multiple elastic bodies rotates in the power transmission direction of the one-way rotation mechanism, and the power of the rotation is transmitted to the output rotor via the multiple first gears and second gears.

As a result, when the load on the output rotor increases, the energy stored in the elastic body is released to generate output torque due to the hybrid effect of the drive source and the elastic body, making it possible to realize a power transmission device in which load fluctuations are not directly transmitted to the drive source. Also, when the load on the output rotor increases and the rotation of the pivot arm caused by the elastic body slows down, the tip of the pivot arm abuts against the next pivot arm before the pivot arm returns, and the torque automatically increases, making it possible to automatically obtain a continuously variable speed function without manual operation. Furthermore, because the one-way clutch does not operate until the load on the output rotor becomes large to a certain extent, the one-way clutch has a long life and the durability of the power transmission device can be improved.

The angular interval at which the multiple pins are attached to the drive shaft is preferably 360/N degrees (where N is the number of pins). This allows the multiple pins to come into contact with the tips of the multiple arms at equal time intervals, resulting in a stable rotation output.

It is preferable that the device further includes an elastic force adjustment mechanism that can variably adjust the elastic force of the multiple elastic bodies. By adjusting the elastic force of the elastic bodies, the energy input from the drive source to the power transmission device can be adjusted. This makes it possible to adjust the maximum output value and the threshold value at which the gear shift function operates.

It is preferable that each of the multiple elastic bodies has at least one tension coil spring. This allows for easy installation and allows for a constant elastic force to be applied to the arm.

It is preferable that the device further includes a number of stoppers that limit the rotation of each of the multiple pivot arms to a predetermined range.

According to the present invention, a rotary drive device using the above-mentioned power transmission device is provided.

According to the present invention, when the load on the output rotor becomes greater than a predetermined value, each of the arms is pushed back in a direction opposing the biasing force of each of the elastic bodies by the pressure of the tip when the tip of the rotating arm abuts, storing elastic energy in the elastic body, and when the tip of the rotating arm is released from the abutment, the biasing force of the stored elastic energy of each of the elastic bodies rotates in the power transmission direction of the one-way rotation mechanism, thereby realizing a power transmission device in which load fluctuations are not directly transmitted to the drive source. In addition, a continuously variable speed function can be obtained automatically without manual operation. Furthermore, since the one-way clutch does not operate until the load on the output rotor becomes large to a certain extent (pre-tension force of the elastic body), the one-way clutch has a long life and the durability of the power transmission device can be improved.

In addition, the power transmission device according to the present invention is compact and can be attached to a tire wheel, etc., and can easily be configured as a rotary drive device in which load fluctuations are not directly transmitted to the drive source.

1 is a perspective view showing a schematic configuration of a power transmission device according to an embodiment of the present invention; FIG. 2 is an exploded perspective view showing a schematic configuration of the power transmission device shown in FIG. 1 . FIG. 2 is a perspective view for explaining the operation of the power transmission device of FIG. 1 . FIG. 2 is a diagram for explaining the relationship between the input and load and the output of the power transmission device of FIG. 1 . FIG. 2 is a diagram illustrating a first application example of the power transmission device of FIG. 1 . FIG. 2 is a diagram illustrating a second application example of the power transmission device of FIG. 1 . FIG. 2 is a diagram illustrating a third application example of the power transmission device of FIG. 1 .

The following describes an embodiment of a power transmission device (continuously variable transmission) according to the present invention. Figure 1 shows a schematic configuration of a power transmission device 100 according to the present invention, and Figure 2 is an exploded perspective view showing the configuration of the power transmission device 100. Figure 3 shows the state of the power transmission device 100 when the tip of the rotating arm 12 is released from contact.

As shown in FIG. 1, the power transmission device 100 of this embodiment includes a drive rotating shaft 10 rotated by a drive source, a one-way clutch 11 as a one-way rotation mechanism, a rotating arm 12 having one end attached to the drive rotating shaft 10 via the one-way clutch 11 and rotating together with the drive rotating shaft 10, a support shaft 20 arranged on the same axis as the drive rotating shaft 10, an output rotating body (disk member) 30 provided on the support shaft 20, four rotating shafts 40a, 40b, 40c, and 40d evenly provided on the outer periphery of the output rotating body 30, and a plurality of one-way rotation mechanisms, each of which rotates through four one-way clutches 50a, 50b, 50c, and 50d. a, 40b, 40c and 40d, and four pivot arms 60a, 60b, 60c and 60d whose tips can abut against the other end of the pivot arm 12; four elastic bodies 70a, 70b, 70c and 70d that bias the four pivot arms 60a, 60b, 60c and 60d in the power transmission direction of the one-way clutches 50a, 50b, 50c and 50d, respectively; four first gears 80a, 80b, 80c and 80d that are respectively provided on the four rotation shafts 40a, 40b, 40c and 40d; and a second gear 90 that is provided on the output rotor 30 and can mesh with the four first gears 80a, 80b, 80c and 80d.

The drive shaft 10 is connected to a motor as a drive source (via a variable speed gear if necessary) and is arranged on the same axis as the support shaft 20. This drive shaft 10 is driven by a motor that rotates at a constant speed and rotates at a predetermined rotational speed. In other words, when a variable speed gear is used, the rotation of the motor is transmitted to the gear and the speed is changed as necessary to rotate the drive shaft 10. Note that instead of a motor, a Stirling engine or the like may be used as a drive source.

The one-way clutch 11 converts the rotation of the rotating arm 12 into one-way rotational motion, and its outer periphery is connected to one end 12a of the rotating arm 12, with the drive rotating shaft 10 attached to its center.

The rotating arm 12 is formed from, for example, a material having a square bar shape, with one end 12a fixed to the one-way clutch 11 and the other end 12b being a free end. The other end 12b of the rotating arm 12 is provided with an abutment portion 13 for abutting against the tip ends of the pivot arms 60a, 60b, 60c, and 60d. The abutment portion 13 is a freely rotatable rotating roller.

The support shaft 20 is connected to a driving load (e.g., wheels, etc.), and is supported by a support (frame, chassis, frame, etc.) (not shown) via a fixed or reverse rotation-preventing one-way clutch, and is arranged coaxially with the drive rotating shaft 10. The support shaft 20 is provided with an output rotating body 30 and a second gear 90.

The output rotor 30 is composed of a pair of disks 30a and 30b and spacers 31a, 31b, 31c, and 31d. Four rotating shafts 40a, 40b, 40c, and 40d are evenly arranged on the outer periphery of the output rotor 30. In addition, one end of the spacers 31a, 31b, 31c, and 31d serve as elastic body fixing parts 32a, 32b, 32c, and 32d, and one end of each of the four elastic bodies 70a, 70b, 70c, and 70d is fixed through the disk 30a. In addition, four stoppers 33a, 33b, 33c, and 33d that limit the rotation of each of the rotating arms 60a, 60b, 60c, and 60d to a predetermined range are provided on the surface of the disk 30a. Stoppers 33a, 33b, 33c, and 33d are, for example, rod-shaped members arranged parallel to rotation shafts 40a, 40b, 40c, and 40d.

The rotating shafts 40a, 40b, 40c, and 40d are evenly spaced (at 90 degree intervals) on the outer periphery of the output rotor 30. The rotating shafts 40a, 40b, 40c, and 40d are provided with rotating arms 60a, 60b, 60c, and 60d, and first gears 80a, 80b, 80c, and 80d, respectively. For example, the rotating arms 60a, 60b, 60c, and 60d are provided on the ends of the outer rotating shafts 40a, 40b, 40c, and 40d of the disk 30a, and the first gears 80a, 80b, 80c, and 80d are configured to be located between a pair of disks 30a and 30b.

The one-way clutches 50a, 50b, 50c, and 50d convert the rotation of the pivot arms 60a, 60b, 60c, and 60d into one-way rotational motion, and are connected at their outer periphery to one end of the pivot arms 60a, 60b, 60c, and 60d, with the rotating shafts 40a, 40b, 40c, and 40d attached to their centers.

The pivot arms 60a, 60b, 60c, and 60d are formed, for example, from a round bar or square bar material, with one end fixed to the one-way clutches 50a, 50b, 50c, and 50d, respectively, and the other end being a free end. The other ends of the pivot arms 60a, 60b, 60c, and 60d are connected to one ends of the elastic bodies 70a, 70b, 70c, and 70d. The counterclockwise rotation of the pivot arms 60a, 60b, 60c, and 60d is limited to a predetermined range by the stoppers 33a, 33b, 33c, and 33d. The mounting angle interval of the pivot arms 60a, 60b, 60c, and 60d is 360/4 = 90 degrees. That is, the pivot arm 13 is configured to abut against the pivot arms 60a, 60b, 60c, and 60d, respectively, every time the drive rotation shaft 10 rotates 90 degrees.

The elastic bodies 70a, 70b, 70c, and 70d are, for example, tension coil springs. As elastic bodies that urge the pivot arms 60a, 60b, 60c, and 60d in the power transmission direction of the one-way clutches 50a, 50b, 50c, and 50d, one end of each of the elastic bodies is connected to the pivot arms 60a, 60b, 60c, and 60d, and the other end is connected to the elastic body fixing parts 32a, 32b, 32c, and 32d.

The first gears 80a, 80b, 80c, and 80d are attached to the rotating shafts 40a, 40b, 40c, and 40d, respectively, and rotate together with the rotating shafts 40a, 40b, 40c, and 40d. Each of the four first gears 80a, 80b, 80c, and 80d can be meshed with the second gear 90. Each of the first gears 80a, 80b, 80c, and 80d is configured to rotate together with the output rotor 30 when rotating together with the rotating shafts 40a, 40b, 40c, and 40d while meshing with the second gear 90.

The second gear 90 is provided on the support shaft 20 and is configured to rotate together with the support shaft 20. It is also capable of meshing with each of the four first gears 80a, 80b, 80c, and 80d.

Next, the operation of the power transmission device 100 in this embodiment will be described. Figure 3 shows the operating state of the power transmission device 100. Figure 3 shows the state where the rotating arm 12 starts to contact the pivot arm 60a (indicated by the two-dot dashed line in the figure), but the load applied to the output rotor 30 increases, causing the rotating arm 12 to move away from the contact.

As shown in Figure 3, when the drive shaft 10 rotates in the direction of the arrow by the drive of a power source such as a motor, the rotating arm 12 also rotates, and when the load on the output rotor 30 is smaller than the tension of one elastic body, the abutment 13 provided on the other end 12b of the rotating arm 12 abuts against the pivot arm 60a, and rotational energy is output from the output rotor 30 (direct drive). When the load on the output rotor 30 increases during this rotation, the abutment 13 of the rotating arm 12 presses against the tip of the pivot arm 60a, causing the pivot arm 60a to rotate clockwise. This rotation causes the one-way clutch 50a to spin freely, so no power is transmitted and the elastic body 70a is only pulled. When the driving shaft 10 rotates further and the abutment portion 13 separates from the tip of the rotating arm 60a, the rotating arm 60a is biased by the biasing force of the elastic body 70a to rotate counterclockwise and stops rotating at a position where it abuts against the stopper 33a. This rotation actually rotates the one-way clutch 50a, and the power is transmitted to the output rotor 30 via the first gear 80a, and the power is output. When the driving shaft 10 rotates further and the abutment portion 13 of the rotating arm 12 presses the tip of the rotating arm 60b, the rotating arm 60b performs the same operation as the rotating arm 60a described above. When the driving shaft 10 rotates further and the abutment portion 13 of the rotating arm 12 presses the tip of the rotating arm 60c, the rotating arm 60c performs the same operation as the rotating arm 60a described above. When the drive shaft 10 rotates further and the abutment portion 13 of the rotating arm 12 presses against the tip of the rotating arm 60d, the rotating arm 60d performs the same operation as the rotating arm 60a described above. In this way, the rotational movement of the drive shaft 10 causes the rotating arms 60a, 60b, 60c, and 60d to rotate alternately, causing the output rotor 30 to rotate and output power (indirect drive).

In this way, as the drive shaft 10 rotates, the abutment portion 13 of the rotating arm 12 abuts against the tips of the rotating arms 60a, 60b, 60c, and 60d in sequence, pressing the rotating arms 60a, 60b, 60c, and 60d in a clockwise direction to rotate them in sequence. This clockwise rotation causes the one-way clutches 50a, 50b, 50c, and 50d to rotate freely, so no power is transmitted. However, this rotation pulls the elastic bodies 70a, 70b, 70c, and 70d, respectively, and elastic energy is accumulated to urge the rotating arms 60a, 60b, 60c, and 60d in a counterclockwise direction. When the load applied to the output rotor 30 becomes greater than a predetermined value (the tension of one elastic body), when the abutment portion 14 of the rotating arm 13 is released from contact with the tip portions of the rotating arms 60a, 60b, 60c, and 60d, the force of the stored elastic energy in each of the elastic bodies 70a, 70b, 70c, and 70d causes the rotating arms 60a, 60b, 60c, and 60d to rotate counterclockwise, and the one-way clutches 50a, 50b, 50c, and 50d are driven to rotate counterclockwise (the power transmission direction), thereby transmitting power and outputting the rotational motion through the output rotor 30. In this case, when the contact portion 14 of the rotating arm 13 starts to contact the tip of each of the rotating arms 60a, 60b, 60c, and 60d, the tension of each of the elastic bodies 70a, 70b, 70c, and 70d is small, but the tension thereafter gradually increases, so that stable driving can be achieved without applying a large load to the drive source in an instant. On the other hand, when the contact portion 13 of the rotating arm 12 is released from contact with the tip of the rotating arms 60a, 60b, 60c, and 60d, the rotating arms 60a, 60b, 60c, and 60d are repelled, so that a larger output torque can be obtained.

That is, in the power transmission device 100, the force of the driving source is divided and stored in a plurality of elastic bodies 70a, 70b, 70c, and 70d. The timing of releasing the stored force automatically changes depending on the load applied to the output rotor 30. Also, when the load applied to the output rotor 30 becomes greater than a predetermined value (tension of four elastic bodies), the rotation of the rotating arm 12 causes the rotating arms 60b, 60c, and 60d to move out of contact like the rotating arm 60a, causing the driving shaft 10 to rotate freely, and the load applied to the output rotor 30 is not directly transmitted to the driving source, and energy is stored in the elastic bodies 70a, 70b, 70c, and 70d. When the load applied to the output rotor 30 becomes less than a predetermined value, the energy stored in the elastic bodies 70a, 70b, 70c, and 70d is released, causing the output rotor 30 to rotate and generating output torque.

Figure 4 shows the relationship between the input, load and output of the power transmission device 100. In Figure 4, the input of the drive rotating shaft 10 is constant, the horizontal axis is the rotation speed and torque, and the vertical axis (for (C) to (E) in the figure) is the load. (A) in the figure shows the input of the drive rotating shaft 10 (i.e., the rotation speed of the output of the power source), and (B) shows the output (rotation speed and torque) of the output rotating body 30 when the load applied to the output rotating body 30 is smaller than the tension of one elastic body. In this case, the input of the drive rotating shaft 10 becomes the output of the output rotating body 30 as it is, and no speed change effect occurs. (C) to (E) show the output of the output rotating body 30 when the load applied to the output rotating body 30 is larger than the tension of one elastic body. In this case, the output of the output rotating body 30 and the input of the drive rotating shaft 10 are different, and a speed change effect occurs. In addition, the rotation speed and torque of the output rotating body 30 change depending on the magnitude of the load. That is, when the load on the output rotor 30 increases, the rotation of the pivot arm by the elastic body slows down, and before the pivot arm returns, the pivot arm 13 abuts against another pivot arm, and energy is stored in the multiple elastic bodies and released all at once, so the greater the number of elastic bodies, the greater the stored energy and the greater the torque that is instantly output. Also, as shown in FIG. 4, when the load on the output rotor 30 is small, the rotation speed of the output rotor 30 is high. When the load on the output rotor 30 is large, the rotation speed of the output rotor 30 is low.

As described above, the power transmission device 100 includes the drive rotating shaft 10, the one-way clutch 11, the rotating arm 12, the support shaft 20 arranged on the same axis as the drive rotating shaft 10, the output rotor 30, the four rotating shafts 40a, 40b, 40c, and 40d, the four one-way clutches 50a, 50b, 50c, and 50d, the four pivot arms 60a, 60b, 60c, and 60d, the four elastic bodies 70a, 70b, 70c, and 70d, the four first gears 80a, 80b, 80c, and 80d, and the second gear 90.

This allows the rotation of the drive shaft 10 to directly or indirectly drive the output rotor 30, and realizes a power transmission device 100 in which load fluctuations are not directly transmitted to the drive source. In addition, a continuously variable speed function can be obtained automatically without manual operation. Furthermore, since the one-way clutches 50a, 50b, 50c, and 50d do not operate until the load on the output rotor 30 becomes large to a certain extent (pre-tension force of the elastic body), the one-way clutches 50a, 50b, 50c, and 50d have a long life, and the durability of the power transmission device can be improved.

Hereinafter, an example of the configuration of a rotary drive device using the power transmission device 100 according to the present invention will be described. Figure 5 shows a schematic configuration of a two-wheeled vehicle (bicycle or motorcycle) 100A using the power transmission device 100. In the figure, the drive wheel of the two-wheeled vehicle 100A is shown. As shown in Figure 5, the power transmission device 100 is mounted in the drive wheel of the two-wheeled vehicle 100A, and its outer periphery is covered with a tire. The drive rotation shaft 10 of the power transmission device 100 is rotated by a chain, gear, or the like. In addition, the drive rotation shaft 10 is rotatably mounted on a frame. The support shaft 20A is mounted on the frame via a one-way clutch that prevents reverse rotation. In this case, the rotational power of the drive rotation shaft 10 is transmitted and output by the rotation of the power transmission device 100 and the tire.

Figure 6 shows a schematic configuration of an automobile 100B using a power transmission device 100. As shown in Figure 6, the power transmission device 100 is attached to a flywheel and is configured to transmit rotational output from an output rotor 30 to a rotating shaft of a drive wheel via a chain, gears, etc. Note that the power transmission device 100 itself may be used as the flywheel.

Figure 7 shows a schematic configuration of a drill 100C using a power transmission device 100. As shown in Figure 7, the power transmission device 100 is attached to a flywheel and is configured to transmit rotational output from the output rotor 30 to the rotating shaft of the drill via a chain, gears, etc. Note that the power transmission device 100 itself may be used as the flywheel.

The power transmission device 100 described above may have an elastic force adjustment mechanism that adjusts the tension (elastic force) of the elastic bodies 70a, 70b, 70c, and 70d. For example, the elastic body fixing parts 32a, 32b, 32c, and 32d adjust the tension (elastic force) of the elastic bodies 70a, 70b, 70c, and 70d by rotating or displacing. This elastic force adjustment mechanism adjusts the tension (elastic force) of the elastic bodies 70a, 70b, 70c, and 70d, thereby adjusting the energy input from the drive source to the power transmission device 100. This makes it possible to adjust the maximum output value and the threshold value at which the shift function operates.

In addition, in the power transmission device 100 described above, the elastic bodies 70a, 70b, 70c, and 70d are tension coil springs, but the present invention is not limited to this. For example, they may be made of a material such as rubber.

In addition, in the above-mentioned power transmission device 100, an example having four pivot arms 60a, 60b, 60c, and 60d has been described, but the present invention is not limited to this. Any number of pivot arms may be provided.

In addition, in the above-mentioned power transmission device 100, an example was described in which the output rotor 30 uses a pair of disks 30a and 30b, but the present invention is not limited to this. For example, a single disk may be used.

Furthermore, although the examples of the two-wheeled vehicle 100A, the four-wheeled automobile 100B, and the drill 100C have been described as application examples of the power transmission device 100 described above, the present invention is not limited to these. For example, it may be used in rotating devices with large load fluctuations, such as elevators and mixers.

The above-described embodiments are illustrative of the present invention and are not limiting, and the present invention can be implemented in various other modified and altered forms. Therefore, the scope of the present invention is defined only by the claims and their equivalents.

The power transmission device of the present invention is ideal for objects where the required torque changes irregularly and constantly, and can be used to transmit power in vehicles, elevators, escalators, drills, mixers, etc.

10 Drive rotating shaft 11, 50a, 50b, 50c, 50d One-way clutch 12 Rotating arm 13 Contact portion 20, 20A Support shaft 30 Output rotating body (disk member)
31a, 31b, 31c, 31d Spacer 32a, 32b, 32c, 32d Elastic body fixing portion 40a, 40b, 40c, 40d Rotating shaft 60a, 60b, 60c, 60d Rotating arm 70a, 70b, 70c, 70d Elastic body 80a, 80b, 80c, 80d First gear 90 Second gear 80 Stopper 100 Power transmission device 100A Two-wheeled vehicle (rotary drive device)
100B Automobile (rotary drive device)
100C Drill (rotary drive device)

Claims (6)

A drive rotation shaft that is rotated by a drive source;
a rotating arm having one end attached to the drive rotating shaft via a one-way rotating mechanism and configured to rotate together with the drive rotating shaft;
an output rotor provided on a support shaft coaxial with the drive rotor;
A plurality of rotation shafts are parallel to the drive rotation shaft and are evenly provided on the outer periphery of the output rotor;
a plurality of rotating arms each of which is rotatable about a fulcrum of the plurality of rotating shafts, and which are provided on the plurality of rotating shafts via a plurality of one-way rotating mechanisms, and each of which has a tip end that can abut against the other end of the rotating arm;
a plurality of elastic bodies each biasing the plurality of pivot arms in a power transmission direction of the plurality of unidirectional rotation mechanisms;
a plurality of first gears provided on the plurality of rotation shafts, respectively;
a second gear provided on the output rotor and capable of meshing with the plurality of first gears,
a power transmission device configured such that, when a load equal to or greater than a predetermined value is applied to the output rotor, when the tip of the rotating arm abuts against the output rotor, the rotating arm is pushed back in a direction opposing the biasing force of each of the elastic bodies by the pressure of the rotating arm, storing elastic energy in the elastic body, and when the tip of the rotating arm is released from contact, the rotating arm is driven to rotate in the power transmission direction of the multiple one-way rotation mechanisms by the biasing force of each of the multiple elastic bodies due to the stored elastic energy , and the power due to the rotational drive is transmitted to the output rotor via the multiple first gears and the second gear. The power transmission device according to claim 1, characterized in that the mounting angle interval of the multiple rotating shafts relative to the drive rotating shaft is 360/N degrees (where N is the number of rotating shafts). The power transmission device according to claim 1 or 2, further comprising an elastic force adjustment mechanism capable of variably adjusting the elastic force of the multiple elastic bodies. The power transmission device according to any one of claims 1 to 3, characterized in that each of the multiple elastic bodies comprises at least one tension coil spring. The power transmission device according to any one of claims 1 to 4, further comprising a plurality of stoppers that limit the rotation of each of the plurality of pivot arms to a predetermined range. A rotary drive device using the power transmission device according to any one of claims 1 to 5.

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