JP3059709B2 - winch - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a winch for reducing the rotation of a motor to rotate a winding drum and winding a wire around the winding drum.

[0002]

2. Description of the Related Art A winch for winding a wire around a winding drum is mounted on, for example, a truck bed of a truck. The winch rotates the take-up drum by reducing the rotation of a hydraulic motor or an electric motor with a reduction gear. The winding drum
In order to be able to pull and wind the wire with strong force,
The rotation of the motor is considerably reduced by the reduction gear.

A worm gear having a large reduction ratio is used as a winch reduction gear. In a winch using a worm gear, a worm wheel is connected to a winding drum, and a motor is connected to the worm. The winch of this structure has a feature that it can be manufactured at low cost.

[0004]

However, a winch using a worm gear as the reduction gear has a drawback that the output of the motor cannot be transmitted to the winding drum efficiently. This is because the worm gear slides the tooth surface of the worm against the tooth surface provided on the outer periphery of the worm wheel to rotate the worm wheel, so that power transmission efficiency is poor. Furthermore, winches that use worm gears as reduction gears are:
There is also a disadvantage that it is difficult to design the outer circumference small. that is,
This is because a worm wheel having a large outer diameter is used to increase the reduction ratio.

Further, in a winch using a worm gear, the winding drum cannot be idle when the wire is fed, and the motor needs to be reversed when the wire is fed. This is because the worm gear can rotate the worm wheel with the worm, but cannot rotate the worm with the worm wheel.

The present inventor has sought to eliminate this drawback.
A winch using a planetary gear set as a reduction gear has been developed. The planetary gear device connects the motor 3 to the center gear 17 and connects the winding drum 1 to the output rotation shaft 19 of the planetary gear 18 as shown in the schematic diagram of FIG. The sun gear 20 is fixed so as not to rotate. When the motor 3 rotates the center gear 17 of the winch, the planetary gear 18 rotates around the center gear 17, and the planetary gear 18 rotates the winding drum 1. The planetary gear device has excellent power transmission efficiency as compared with the worm gear. For this reason,
The output of the motor can be effectively transmitted to the winding drum.

However, in the planetary gear device, since the planetary gear is disposed around the center gear and the sun gear is disposed outside the planetary gear, it is difficult to reduce the outer diameter. Further, it is difficult for the planetary gear device to have a large reduction ratio like a worm gear. For this reason, it is necessary to reduce the rotation of the motor by another gear and rotate the center gear of the planetary gear. Since the winch of this structure uses a further reduction gear in addition to the planetary gear device as the reduction gear, the number of gears to be used is increased, so that the whole cannot be made compact, and the cost increases. There is also. Also,
Since the rotation of the motor is reduced to two stages, and the rotation shaft of the planetary gear is connected to the winding drum, the overall length in the axial direction is increased.

Further, the planetary gear device used for the winch requires extremely high machining accuracy for the output rotary shaft connecting the planetary gear to the take-up drum, thereby increasing the manufacturing cost. High precision is required for the output rotary shaft because it is necessary to connect a plurality of planetary gears with extremely high precision in a well-balanced manner. If the plurality of planetary gears are not accurately balanced and connected to the output rotation shaft, all the planetary gears cannot drive the output rotation shafts uniformly, and a strong rotational torque acts on the plurality of planetary gears in an unbalanced manner. Since the output rotary shaft is connected to the winding drum and the strongest force acts, the force acting on the imbalance has a bad influence on the output rotary shaft. Further, the output rotary shaft has one end connected to the winding drum and the other end connected to the planetary gear. Therefore, the output rotary shaft is liable to be twisted by an extremely strong rotating torque and requires a considerably tough structure. This also has the disadvantage that the cost of the winch using the planetary gear set is increased, and mass production at low cost is not possible.

The present invention has been developed with the object of further solving the above drawbacks. An important object of the present invention is to make the whole compact and to increase the power of the motor with high efficiency. To provide a winch capable of rotating the winding drum with a strong rotation torque.

Another important object of the present invention is to provide a winch which has a very simple structure and allows the winding drum to run idle and the wire to be fed out conveniently.

It is a further important object of the present invention to provide a winch capable of connecting a connecting portion between a reduction gear and a take-up drum with a simple structure and firmly.

[0012]

A winch according to the present invention includes a winding drum 1 for winding a wire, and a motor 3 for rotating the winding drum 1 via a reduction gear 2.
Furthermore, the winch of the present invention is characterized in that the reduction gear 2 has the following unique configuration. (A) The reduction gear 2 is a clutch internal gear 4 that is coaxially arranged so that it can approach and rotate independently.
A sun gear 4 including an A and an output internal gear 4B, a planetary gear 5 rolling along the inside of the sun gear 4, and a stopper 7 for stopping rotation of the clutch internal gear 4A. (B) The radius of the pitch gear of the planetary gear 5 is larger than that of the sun gear 4
External gear, which is arranged inside the sun gear 4
You. (C) The planetary gear 5 is connected to the clutch internal gear 4A and the output.
It has a width that meshes with both of the tooth gears 4B. (D) The output internal gear 4B has a different number of teeth from the clutch internal gear 4A, and the output internal gear 4B and the clutch internal gear 4A having different numbers of teeth are a single part and are more
Meshes with Yu Review gear 5 is Chi circle radius smaller external gear. ( E ) The planetary gear 5 is rotatably connected to a crankpin 6 </ b > A of a crankshaft 6 rotated by the motor 3. When the crankshaft 6 is rotated, the planetary gear 5 rotates along the inner surface of the sun gear 4. Roll while rolling. (F) Central axis S1 of crankshaft 6 and crankpin 6A
Is the distance between the eccentric shaft S2 and the pitch circle radius of the planetary gear 5.
Is r, and the pitch circle radius of the sun gear 4 is R, d + r
= R. ( G ) The output internal gear 4B is connected to the winding drum 1, and when the motor 3 rotates the crankshaft 6 with the stopper 7 stopping the rotation of the clutch internal gear 4, the output internal gear 4B is output. The output internal gear 4 </ b> B rotates the winding drum 1 while the rotation of the output internal gear 4 </ b> B is reduced with respect to the crankshaft 6.

[0013]

Embodiments of the present invention will be described below with reference to the drawings. However, the embodiments described below illustrate winches for embodying the technical idea of the present invention, and the present invention does not specify the winches as follows.

Further, in this specification, in order to make it easy to understand the claims, the numbers corresponding to the members shown in the embodiments will be referred to as “claims” and “ In the column of “means”. However, the members described in the claims are not limited to the members of the embodiments.

The winch shown in FIGS. 2 and 3 includes a winding drum 1 for winding a wire, and a motor 3 for rotating the winding drum 1 via a reduction gear 2.

The winding drum 1 is formed in a cylindrical shape having flanges 1A on both sides so that the wire can be wound. As shown in FIGS. 2 to 4, the winding drum 1 is disposed in an opening 8 </ b> A provided at an upper portion of the frame 8 and is connected to the frame 8 so as to be rotatable.

As shown in FIG. 3, the cylindrical portion 1B of the winding drum 1 is connected to the frame 8 via a bearing cylinder 10 on the opposite side of the reduction gear 2. The bushing 10 is connected to the frame 8
And is inserted into the cylindrical portion 1B to support the winding drum 1 so as to be rotatable. Furthermore, the winding drum 1
Connects the output internal gear 4B to the flange 1A on the reduction gear 2 side. The winding drum 1 is connected to the inner surface of the frame 8 via the output internal gear 4B. In the winding drum 1, the outer circumference of the output internal gear 4B fixed to the flange 1A is
The frame 8 is supported so as to be rotatable. Thus, the structure which supports the winding drum 1 with the inner surface of the frame 8 as a bearing can receive the winding drum 1 which receives a large load in a large area. For this reason, there is a feature that the rigidity against bending and twisting is increased and the winding drum 1 can be strongly supported.

Further, the winding drum 1 is provided with a dry metal 16 at a connecting portion between the cylindrical portion 1B and the bearing tube 10 and at a connecting portion between the output internal gear 4B and the frame 8.
As shown in FIG. 5, for example, the dry metal 16 is a ring-shaped metal cylinder coated with fluorine, and can rotate smoothly with less resistance at the contact surface. A sintered metal or the like can be used as the dry metal. The winch that connects the winding drum 1 to the frame 8 through the dry metal 16 can rotate the winding drum 1 smoothly, and can also rotate the winding drum 1 and the frame 8.
The feature is that the outer diameter of the winch can be reduced to make the entire winch compact. However, these connecting portions may be connected so as to be rotatable via bearings.

The motor 3 is fixed outside the frame 8 in a horizontal posture. As the motor 3, for example, a hydraulic motor is used. However, an electric motor can be used for the motor. Rotary shaft 3A of motor 3
Is inserted into the frame 8 through the frame cover 8B, and is connected to a connecting portion 6B at the rear end of the crankshaft 6 disposed horizontally in the frame 8. The connecting portion 6B between the rotating shaft 3A of the motor 3 and the crankshaft 6 is shown in FIG.
For example, as shown in FIG.

As shown in FIG. 3, the crankshaft 6 extends so as to penetrate the center of the winding drum 1 and has a distal end rotatably inserted into the bearing tube 10. The tip of the crankshaft is connected to the inner surface of the bearing sleeve 10 via the above-described dry metal 16. The rear end of the crankshaft 6
The outer periphery of the connecting portion 6B is connected to the frame cover 8B via a bearing 11 so as to be rotatable. Further, the crankshaft 6 has an intermediate portion connected to the cylindrical portion 1B of the winding drum 1 via a bearing 9. The crankshaft 6 arranged in this way is driven by the motor 3,
It has the feature that it can rotate independently and can rotate stably.

The reduction gear 2 is, as shown in FIGS.
A sun gear 4 including a clutch internal gear 4A and an output internal gear 4B, a planetary gear 5 rolling along the inside of the sun gear 4, and a stopper 7 for stopping rotation of the clutch internal gear 4A. Prepare.

The clutch internal gear 4A and the output internal gear 4B, which are the sun gears 4, are internal gears having the same pitch circle radius.
They are arranged coaxially close to each other. Further, the clutch internal gear 4 </ b> A and the output internal gear 4 </ b> B are arranged so as to be independently rotatable along the inner surface of the frame 8.
The outer diameter of the clutch internal gear 4 </ b> A and the output internal gear 4 </ b> B are designed to be substantially equal to the inner diameter of the frame 8.

Further, the clutch internal gear 4A and the output internal gear 4B are designed with different numbers of internal teeth. This is because the output is reduced by utilizing the difference in the number of teeth between the clutch internal gear 4A and the output internal gear 4B. The clutch internal gear 4A and the output internal gear 4B having different numbers of teeth are designed to mesh with the planetary gear 5 in a single part.

Further, the output internal gear 4B is connected to the winding drum 1. The output internal gear 4B is fixed to the flange 1A of the winding drum 1 via a connector 12 such as a bolt. As described above, the structure in which the output internal gear 4B is directly connected to the flange 1A of the winding drum 1 has a feature that the winding drum 1 can be strongly connected to the reduction gear 2 with a simple structure. Further, the output internal gear 4B connected to the winding drum 1 transmits the output transmitted from the planetary gear 5 directly to the winding drum 1 and outputs the output. In particular, since the output internal gear 4B rotates while the outer peripheral surface is supported by the frame 8, the output internal gear 4B has a feature that the winding drum 1 can be stably rotated.

The planetary gear 5 is an external gear having a smaller pitch circle radius than the sun gear 4 and is disposed inside the sun gear 4. The planetary gear 5 is designed to have a wide width so as to mesh with both the clutch internal gear 4A and the output internal gear 4B. Further, the planetary gear 5 is rotatably connected via a bearing 13 to a crankpin 6A of a crankshaft 6 rotated by the motor 3.

The crank pin 6A is provided at the rear end of the crankshaft 6, and is formed to be thicker than the crankshaft 6. Further, the crank pin 6A is provided with an eccentric shaft S2, which is a central shaft, eccentric from a central shaft S1 of the crank shaft 6. Therefore, the crank pin 6A rotates eccentrically with respect to the rotating crank shaft 6.

When the motor 3 rotates the crankshaft 6, the planetary gear 5 having this structure rotates inside the sun gear 4 while being eccentric with respect to the crankshaft 6 by the crankpin 6A which rotates eccentrically. . At this time, the planetary gear 5 rotates while rotating with respect to the crankpin 6A,
The inner surface of the sun gear 4 rolls while meshing with the clutch internal gear 4A and the output internal gear 4B at a single portion. In order to realize this, the distance between the center axis S1 of the crankshaft 6 and the eccentric axis S2 of the crankpin 6A is d, the pitch circle radius of the planetary gear 5 is r, and the pitch circle radius of the sun gear 4 is R.
Then, the relationship is designed so that d + r = R.

The stopper 7 controls the rotation of the clutch internal gear 4A. The stopper 7 includes a key groove 15 provided on the outer peripheral surface of the clutch internal gear 4 </ b> A and a key 14 connected to the frame 8. The key 14 is connected to a lever 21 disposed outside the frame 8,
The lever 21 is operated to be put in and out of the key groove 15. When the key 14 is inserted into the key groove 15, the stopper 7 having this structure enters a locked state in which the clutch internal gear 4A is fixed to the frame 8, and prevents the rotation of the clutch internal gear 4A. When the key 14 is removed from the key groove 15, the clutch internal gear 4 </ b> A is unlocked and becomes free, and can rotate along the inner surface of the frame 8.

The clutch internal gear 4A shown in FIG. 7 has one key groove 15 on the outer peripheral surface. As shown in FIG. 5, a plurality of key grooves 15 may be provided on the outer peripheral surface of the clutch internal gear 4A. In the clutch internal gear 4A shown in this figure, key grooves 15 are provided at three positions on the outer peripheral surface at equal intervals. However, the key grooves may be provided at two or four or more places at equal intervals on the outer peripheral surface of the clutch internal gear. As described above, when the clutch internal gear 4A having the plurality of key grooves 15 locks the clutch internal gear 4A, the key 14 is inserted into the key groove 15 at the nearest position, and the clutch internal gear 4A is optimized. There is a feature that can be stopped at the position.

The reduction gear 2 having the above-described structure operates as follows to reduce the rotation of the crankshaft 6 to reduce the rotation of the winding drum 1.
To communicate. However, the number of teeth of the clutch internal gear 4A is Z
1. The number of teeth of the output internal gear 4B is Z2, and the number of teeth of the planetary gear 5 is Z3.

With the stopper 7 stopping the rotation of the clutch internal gear 4A, the motor 3 is driven to rotate the crankshaft 6. While the crankshaft 6 rotates and the crank pin 6A makes one rotation, that is, while the planetary gear 5 rolls inside the clutch internal gear 4A and makes one revolution, the planetary gear 5 It meshes with the internal teeth of 4A and rotates Z1 / Z3 times around the crankpin 6A. As described above, since the planetary gear 5 is not fixed to the crank pin 6 </ b> A, the planetary gear 5 rotates while rotating at an extremely low rotation speed with respect to the rotation speed of the crank shaft 6.

Further, the rolling planetary gear 5 meshes with the output internal gear 4B, and while the planetary gear 5 rotates one revolution, (Z1 / Z3) at the meshing portion with the output internal gear 4B.
× Z3, that is, meshing with Z1 teeth. Output internal gear 4
B is designed to have a different number of teeth from the clutch internal gear 4A, so that the clutch internal gear 4
A rotates with respect to A by the number of teeth Z2-Z1. Assuming that the rotation speed of the crankshaft 6 is 1, the rotation speed of the output internal gear 4B is (Z2-Z1) / Z2, that is, 1-Z1 / Z2.

At this time, if Z1 <Z2, the reduction gear 2
Is decelerated and output in the same direction as the rotation direction of the crankshaft 6. Assuming that Z1> Z2, the reduction gear 2 outputs the reduced speed in the direction opposite to the rotation direction of the crankshaft 6. Therefore, the number of teeth of Z1 and Z2 is designed to an optimum value according to the purpose.

The reduction gear 2 preferably has a difference between the number of teeth Z1 of the clutch internal gear 4A and the number of teeth Z2 of the output internal gear 4B, that is, ± 1, that is, Z1 = Z2 ± 1. It can be decelerated in the ideal condition by designing it. The reduction gear 2 is
For example, the number of teeth Z1 of the clutch internal gear 4A is 43, the number of teeth Z2 of the output internal gear 4B is 44, and the number of teeth Z3 of the planetary gear 5 is Z3.
Is set to 38. When the motor 3 is driven with the clutch internal gear 4 </ b> A fixed with the stopper 7, the reduction gear 2 of this structure reduces the rotation speed of the winding drum 1 to 1/44 with respect to the rotation speed of the motor 3. Can slow down.

Furthermore, when the stopper 7 is released, the reduction gear 2 can let the winding drum 1 idle and feed the wire. This is because the clutch internal gear 4A from which the stopper 7 is released and the key 14 is removed from the key groove 15 is free to rotate. When the wire is fed out in this state, the output internal gear 4B connected to the winding drum 1
And a planetary gear 5 meshing with the output internal gear 4B, and a clutch internal gear 4A meshing with the planetary gear 5,
Or without any load on the frame 8. For this reason, the winding drum 1 can idle and unwind the wire freely.

The winch having the above-described structure operates as follows to wind a wire around the winding drum and to feed the wire. [When the motor is decelerated and the wire is wound by the winding drum] The stopper 7 locks the clutch internal gear 4A. The stopper 7 inserts the key 14 into the key groove 15 of the clutch internal gear 4A via the lever. The motor 3 is driven to rotate the crankshaft 6 connected to the rotating shaft 3A of the motor 3. When the crankshaft 6 rotates, the crankpin 6A
Rotate in a state of being eccentric with respect to the central axis S1 of the crankshaft 6. The planetary gear 5 includes a rotating crank pin 6.
Rolling along the inner surface of the clutch internal gear 4A while rotating about A. At this time, the planetary gear 5 rolls along the inner surface of the output internal gear 4B while also meshing with the output internal gear 4B. When the planetary gear 5 rolls one revolution along the inner surface of the clutch internal gear 4A, the output internal gear 4B rotates by the difference in the number of teeth from the clutch internal gear 4A. That is, the output internal gear 4 </ b> B rotates at a reduced speed with respect to the rotation speed of the motor 3. The output of the output internal gear 4B, which has been decelerated with respect to the motor 3, is
And the winding drum 1 rotates. The rotating winding drum 1 winds the wire.

[When the winding drum is idle and the wire is fed out while the motor is stopped] The motor 3 is stopped and the stopper 7 is released. When the stopper 7 is released, the clutch internal gear 4A becomes free and can rotate. When the wire is fed in this state, the winding drum 1 rotates to rotate the output internal gear 4B. The rotating output internal gear 4B meshes with the planetary gear 5 to rotate the planetary gear 5. The planetary gear 5 idles without rotating the crank pin 6A. Further, the rotating planetary gear 5 meshes with the clutch internal gear 4A to rotate the clutch internal gear 4A. Since the clutch internal gear 4 </ b> A is unlocked and is in a rotatable state, it idles in the frame 8. After the take-up drum 1 is idled and the wire is fed, the stopper 7 locks the clutch internal gear 4A and stops the rotation.

As described above, the winch according to the present invention is constructed such that the rotation of the internal gear 4A of the clutch is stopped while the motor 3 is stopped.
Is driven, the winding drum 1 is decelerated and rotated,
When the wire can be wound up and the stopper 7 is released to allow the clutch internal gear 4A to rotate,
The wire can be fed by rotating the winding drum 1 without rotating the crankshaft 6.

[0039]

The winch of the present invention is characterized in that the whole can be made compact and the power of the motor can be transmitted to the winding drum with high efficiency so that the winding drum can be rotated with a strong rotation torque. That is, the reduction gears used in the winch of the present invention are arranged coaxially so that they can approach each other and rotate independently, and have a sun gear composed of a clutch internal gear and an output internal gear having different numbers of teeth. A gear, a planetary gear rotatably connected to a crankpin of a crankshaft rotated by a motor and rolling along the inside of the sun gear, and a stopper for stopping rotation of the clutch internal gear. Because. In particular, this reduction gear skillfully utilizes the difference in the number of teeth between the output internal gear and the clutch internal gear that mesh with the rolling planetary gear in a single part, and moves the output internal gear to the crankshaft. It is rotating at a reduced speed. For this reason, the reduction gear of this structure is excellent in power transmission efficiency as compared with a structure in which the tooth surface slides like a conventional worm gear, and it is necessary to have a large outer diameter in order to increase the reduction ratio. Nor. Furthermore, unlike the conventional planetary gear device, there is no need to increase the number of gears and no need for extremely high machining accuracy. Therefore, the winch of the present invention can reduce the outer diameter of the gear to make the whole extremely compact, and can transmit the power of the motor to the winding drum with high efficiency and rotate the winding drum with a strong rotation torque. There are features.

Further, the reduction gear used for the winch of the present invention is not a mechanism in which a planetary gear is fixed to a crankshaft driven by a motor and the planetary gear is rotated directly with respect to the crankpin, instead of directly driving the planetary gear with the motor. Planetary gears roll along the inside of the sun gear. Unlike a conventional planetary gear device, the gear is not directly rotated by a motor. For this reason, in this reduction gear, the number of revolutions of the planetary gear can be extremely reduced as compared with the number of revolutions of the crankshaft. Therefore, the winch of the present invention minimizes the wear of the gears, thereby reducing the loss of the transmission efficiency, and can also extend the life of the gears and reduce the load on the motor. Has the advantage that a strong output can be obtained.

Further, the winch of the present invention has a very simple structure and has a feature that the wire can be conveniently fed out by spinning the winding drum. This is because the winch of the present invention has a stopper for stopping the rotation of the clutch internal gear. In this winch, when the motor is driven with the stopper stopping the rotation of the clutch internal gear, the output internal gear rotates at a reduced speed with respect to the crankshaft, and the output internal gear rotates the winding drum. You can wind up the wire. Conversely, release the stopper,
When the internal gear of the clutch is in a free state, the internal gear of the clutch idles, so that the winding drum idles and the wire can be fed out conveniently.

[Brief description of the drawings]

FIG. 1 is a partial cross-sectional side view of a reduction gear used for a winch previously developed by the present inventors.

FIG. 2 is a perspective view of a winch according to the embodiment of the present invention.

FIG. 3 is a sectional view of the winch shown in FIG. 2;

FIG. 4 is an exploded perspective view showing a frame portion of the winch shown in FIG. 2;

FIG. 5 is an exploded perspective view showing a take-up drum and a sun gear of the winch shown in FIG. 2;

FIG. 6 is an exploded perspective view showing a crankshaft and a planetary gear of the winch shown in FIG. 2;

FIG. 7 is a partially sectional perspective view showing a winch reduction gear according to the embodiment of the present invention.

[Explanation of symbols]

1: Winding drum 1A: Tsuba 1B
... Cylinder part 2 ... Reduction gear 3 ... Motor 3A ... Rotating shaft 4 ... Sun gear 4A ... Clutch internal gear 4B
... output internal gear 5 ... planetary gear 6 ... crankshaft 6A ... crankpin 6B
... Connecting part 7 ... Stopper 8 ... Frame 8A ... Opening 8B
... Frame cover 9 ... Bearing 10 ... Bearing cylinder 11 ... Bearing 12 ... Connector 13 ... Bearing 14 ... Key 15 ... Key groove 16 ... Dry metal 17 ... Center gear 18 ... Planetary gear 19 ... Output rotary shaft 20 ... Sun gear 21 ... lever

────────────────────────────────────────────────── ─── Continuation of the front page (56) References JP-A-5-132292 (JP, A) JP-A-5-54484 (JP, U) US Patent 3931958 (US, A) German Patent Application Publication 4436307 (DE) 1) UK Patent Application Publication 2069966 (GB, A) Swiss Patent Invention 682915 (CH, A5) (58) Fields investigated (Int. Cl. ⁷ , DB name) B66D 1/22 WPI / L (QUESTEL )

Claims (1)

(57) [Claims] 1. A winding drum (1) for winding a wire,
A winch comprising a motor (3) for rotating the winding drum (1) via a reduction gear (2), wherein the reduction gear (2) has all the following configurations. (A) The reduction gears (2) are coaxially arranged so that they can approach each other and rotate independently.
(4A) and a sun gear (4) composed of an output internal gear (4B), and a planetary gear (5) rolling along the inside of the sun gear (4),
Stopper (7) for stopping rotation of clutch internal gear (4A)
And (B) The planetary gear (5) is a half pitch circle longer than the sun gear (4).
An external gear with a small diameter, located inside the sun gear (4)
I have. (C) The planetary gear (5) is the output of the clutch internal gear (4A)
It has a width that engages with both the internal gear (4B). (D) The output internal gear (4B) has a different number of teeth from the clutch internal gear (4A), and the output internal gear (4B) and the clutch internal gear (4A) having different numbers of teeth are a single part . Than the sun gear (4)
Tsu is Chi circle radius smaller external gear meshes with Yu Review gear (5). ( E ) The planetary gear (5) is rotatably connected to the crankpin (6A) of the crankshaft (6) rotated by the motor (3), and when the crankshaft (6) is rotated, Sun gear
Roll while rotating along the inner surface of (4). (F) The center axis (S1) of the crankshaft (6) and the crankpin (6)
The distance between the eccentric shaft (S2) of (A) and (d) is the pitch circle of the planetary gear (5).
Let the radius be (r) and the pitch circle radius of sun gear (4) be (R)
And d + r = R. ( G ) The output internal gear (4B) is connected to the winding drum (1), the stopper (7) stops the rotation of the clutch internal gear (4A), and the motor (3) is turned on the crankshaft. When (6) is rotated, the output internal gear (4B) is rotated at a reduced speed with respect to the crankshaft (6), and the output internal gear (4B) is taken up by the winding drum.
It is configured to rotate (1).