JP2657432B2 - Variable speed rotation device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention
The present invention relates to a speed change rotating device capable of increasing or decreasing the speed by combining the rotational forces of two motors into one output shaft using a one-way clutch mechanism, a gear transmission mechanism, and distortion energy of a torsion coil spring. .

[0002]

2. Description of the Related Art Hitherto, as a device capable of changing a rotation speed, a device using a pulse motor, a servo motor, or the like is known. In these devices, an operation signal is sent from a control circuit to a motor so that a desired rotation speed is obtained.

[0003] In mechanical elements, a cam mechanism or the like is often used in order to change the movement speed.

Further, in order to change the feed speed in a feed mechanism such as a belt conveyor, the amount of movement is detected by various sensors, and a drive device is controlled based on the signal.

As a mechanical transmission mechanism, a continuously variable transmission (trade name “RX Traction Drive”, a product of Shinpo Kogyo Co., Ltd.) having a structure in which a cone is arranged in a free state between an input disk, a ring, and a cam disk. Continuously variable transmission (trade name "mechanical continuously variable transmission", Miki pulley), which is made up of a combination of a V-type pulley and a V-belt, and which changes the substantial radius of rotation of the pulley. Is also known.

[0006]

As described above, various mechanisms can be employed as a device for shifting the mechanical movement, but all of them have a problem that the structure becomes complicated and the manufacturing cost becomes high. was there.

That is, in a variable speed rotating mechanism using a pulse motor, a servo motor, or the like, these motors themselves are expensive, and a control circuit for sending an operation signal to these motors is required, so that the manufacturing cost is extremely high. It will be.

Further, a speed change mechanism using a cam mechanism or the like requires high precision in the design and manufacture of the cam, and further requires an interlocking mechanism around the cam in order to realize the desired motion, and the device is large-scale. And the manufacturing cost is high.

Furthermore, a mechanism for detecting and controlling the feed of a belt conveyor or the like by a sensor can easily realize, for example, intermittent feed, but it is difficult to realize a feed that gradually increases or decreases in speed. .

[0010] The above-mentioned mechanical continuously variable transmission, which is already commercially available, has a narrow shift range, requires manual or electronic control of the shift, and has a complicated structure and a low manufacturing cost. There was a problem that it was expensive.

SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide a speed change rotating device in which stepless speed change such as gradually increasing or decreasing speed is automatically performed without requiring electrical control or the like. Is to do.

[0012]

In order to achieve the above object, a speed change rotating device of the present invention comprises a drive shaft A2 of a first motor A1 and a second motor A8 rotating in the same direction as the drive shaft A2 . The drive shaft A9 is coaxially butted and arranged,
Similarly, the split shaft B1 and the output shaft B15 are coaxially butted with each other and arranged in parallel with the drive shafts A2 and A9, and the drive shaft A2 of the first motor A1 is rotated by the drive shaft A2.
Via the one-way clutch A3 meshing inside fast relative rotational direction, a gear A4 is attached, together with the further gear A4
A cylindrical housing periphery extending in the axial direction, the drive
Through Wan'we <br/> Ikuratchi A12 meshing with the outer high speed relative to the rotational axis A2, equipped with a cylindrical clutch housing A13, the drive shaft A9 of the second motor A8, drive
Through Wan'u <br/> Eikuratchi A10 meshing inside fast with respect to the rotational direction of the shaft A2, equipped with a gear A11, further into the cylindrical housing periphery extending in the axial direction integrally with the gear A11 is driven High speed inside in the rotation direction of axis A2
A cylindrical clutch housing A16 is mounted via a one-way clutch A15 meshing with
Is fixed to the gear B3, and is integrated with the gear B3 in the axial direction.
On the outer periphery of the cylindrical housing that extends , the opposite of the drive shaft A2
A cylindrical clutch housing B5 is mounted via a one-way clutch B4 that meshes at a high speed inward with respect to the rotation direction, and a gear B14 is fixed to the output shaft B15.
The outer circumference of the cylindrical housing extending in the axial direction is fastened to the outside at a high speed with respect to the rotation direction opposite to the drive shaft A2.
A cylindrical clutch housing B12 is mounted via a mating one-way clutch B11, the gear A4 and the gear B3 are meshed, the gear A11 and the gear B14 are meshed, and the gear A4 is meshed with the gear A4. The gear ratio of the gear B3 is different from the gear ratio of the gear A11 and the gear B14, and the clutch housing A16 is provided between the clutch housings A13 and A16.
Rotation direction of the drive shaft A2 relative clutches housing A13
The first torsion coil spring A17 wound tightly around when rotating at high speed countercurrent mounted, between the clutch housing B5, B12, clutch housing B5 clutch housing B
12 high speed in the direction of rotation opposite to drive shaft A2
Second torsion coil spring B13 that winds up when rotating at
Is attached.

[0013]

[Action] with the action of the apparatus of the present invention, for example gear A4
The case where the gear ratio of gear / gear B3 is set to be larger than the gear ratio of gear A11 / gear B14 will be described.
It is as follows.

The rotation of the drive shaft A2 of the first motor A1 is the same as that of the first motor A1.
The power is transmitted to the gear A4 via the one-way clutch A3 meshing at a high speed inward with respect to the rotation direction of the drive shaft A2 , and the gear B3 meshing with the gear A4 rotates. The rotation of the drive shaft A9 of the second motor A8 is inward of the rotation direction.
The power is transmitted to the gear A11 via the one-way clutch A10 that meshes at high speed, and the gear B14 meshing with the gear A11 rotates. Even if the first motor A1 and the second motor A8 rotate at the same speed, the gear ratio of the gear A4 to the gear B3 and the gear A
Since the gear ratio between the gear 11 and the gear B14 is different, the rotational speeds of the gear B3 and the gear B14 are different . In this example, the gear B3 rotates at a higher speed than the gear B14.

The rotation of the drive shaft A2 is caused by the rotation of the gear B3.
Clutch housing B5 via a one-way clutch B4 meshing at a high speed inward with respect to the rotation direction opposite to the rotation direction.
Rotates. On the other hand, the clutch housing B12, the same times
The one-way clutch B11 that meshes with the outer direction at a high speed in the rolling direction does not directly transmit the rotational force from the gear B14, but transmits the rotational force to the gear B14 when it rotates at a higher speed than the gear B14. Therefore, the clutch housing B5 rotates at a higher speed than the gear B14, and the clutch housing B12 rotates the gear B14 unless the gear B14 is turned.
Since the rotation cannot be performed faster, the second torsion coil spring B13 mounted between the clutch housing B5 and the clutch housing B5 has a torsion effect.

When the second torsion coil spring B13 is twisted to the maximum, the clutch housing B5 and the clutch housing B12 are integrated, and the second torsion coil spring B13
Is released at a time, and the clutch housing B12 rotates at high speed together with the gear B14 and the output shaft B15. The output shaft B15 is rotated via the one-way clutch A10, the gear A11, and the gear B14 by the rotation of the drive shaft A9. When the strain energy of the second torsion coil spring B13 is released, the rotation speed of the output shaft B9 is reduced. It rotates at a higher speed and receives a speed increasing effect.

On the other hand, when the distortion energy of the second torsion coil spring B13 is released and the gear B14 rotates at high speed,
The gear A11 meshing with the gear B14 idles with respect to the drive shaft A9 and rotates at high speed. By the rotation of the gear A11 ,
Clutch housing A1 via a one <br/> way clutch A 15 meshing with inner high speed with respect to the rotational direction of the drive shaft A2
6 rotates at high speed. On the other hand, the clutch housing A13
Can not rotate faster than the gear A4 unless the one-way clutch A12 intervenes with the rotation direction of the drive shaft A2 unless the gear A4 is turned. As a result, a torsional action is generated in the first torsion coil spring A17 mounted between the clutch housing A13 and the clutch housing A16.

When the first torsion coil spring A17 is maximally twisted, the clutch housing A13 and the clutch housing A16 are integrated, and the first torsion coil spring A1
7 is released at a time, and the clutch housing A13 rotates at high speed together with the gear A4. This gear A
4, the second torsion coil spring B described above.
The torsional action of the thirteenth cycle is realized again by accelerating the cycle, and the release of the strain energy of the second torsion coil spring B13 and the high speed rotation of the clutch housing B12, the gear B14 and the output shaft B15 are performed again. Such torsion action of the second torsion coil spring B13 and the first torsion coil spring A17 is repeated alternately and with a faster cycle. As a result, the rotation of the output shaft B15 is gradually increased. Become.

The above operation is an example in which the present invention is applied to a speed increasing rotation device. However, the gear ratio of the gear A4 / gear B3 and the gear ratio of the gear A11 / gear B14, the first torsion coil spring A17 and the second By selecting the spring constant or the like of the torsion coil spring B13, the output shaft B15 can be operated to gradually decelerate.

[0020]

1 and 2 show an embodiment of the rotary transmission according to the present invention.

An apparatus frame is formed by connecting four corners of the frame A5 and the frame A7 which are substantially parallel to each other with poles A6. In frame A5, the first
The motor A1 is mounted so as to penetrate the drive shaft A2 inside, and the second motor A8 is mounted on the frame A7 by the drive shaft A9.
Through the drive shaft A2 and the second motor A8
And are mounted so that they are coaxially butted. In this embodiment, the driving shaft A2 of the first motor A1
The drive shaft A9 of the second motor A8 rotates at the same speed in the direction of arrow a in FIG. 1, and the first motor A1 is driven by the second motor A8.
The output is higher, that is, the rotational torque is higher.

A gear A4 is mounted on the outer periphery of the drive shaft A2 via a one-way clutch A3. The one-way clutch A3 transmits the rotational force from the drive shaft A2 to the gear A4 when the drive shaft A2 rotates faster than the gear A4 in the direction of the arrow a, but when the gear A4 rotates faster than the drive shaft A2. , And has a function of causing the drive shaft A2 to idle. The outer circumference of tubular housing extending in the axial direction of its integrally with gear A4, the clutch housing A13 through a one-way clutch A12 is mounted. The one-way clutch A12 transmits its rotational force from the clutch housing A13 to the gear A4 when the clutch housing A13 rotates in the direction of arrow a faster than the gear A4, but when the gear A4 rotates faster than the clutch housing A13. This has the effect of causing the clutch housing A13 to idle.

A gear A11 is mounted on the outer periphery of the drive shaft A9 via a one-way clutch A10. When the drive shaft A9 rotates faster than the gear A11 in the direction of arrow a, the one-way clutch A10 transmits the rotational force to the drive shaft A9.
9 to the gear A11, but the gear A11
When it rotates faster than 9, it acts to make the drive shaft A9 idle. Gears A11 and - on the outer circumference of the cylindrical housing extending in the axial direction of its body, a clutch housing A16 is attached via a one-way clutch A15. The one-way clutch A15 transmits its rotational force from the gear A11 to the clutch housing A16 when the gear A11 rotates faster than the clutch housing A16 in the direction of arrow a. However, when the clutch housing A16 rotates faster than the gear A11. , And has the effect of causing the gear A11 to idle.

A cylindrical sleeve A is provided between the end face of the clutch housing A13 and the end face of the clutch housing A16.
14 are arranged. Further, the clutch housing A1
3. A first torsion coil spring A17 is mounted on the outer periphery of the cylindrical sleeve A14 and the clutch housing A16. The first torsion coil spring A17 has a clutch housing A13 and a clutch housing A1 on the inner circumference at both ends.
6 is crimped to the outer periphery, and is substantially a clutch housing A13.
And is fixed to the clutch housing A16. The cylindrical sleeve A14 is a clutch housing A
13 and an outer diameter smaller than the outer diameter of the clutch housing A16. As a result, the inner circumference of the first torsion coil spring A17 and the cylindrical sleeve A
14 and a predetermined gap is formed between the outer circumference. The first torsion coil spring A17 is wound rightward. When the first torsion coil spring A17 is twisted rightward by a predetermined angle, the first torsion coil spring A17 is tightly wound and closely adheres to the outer periphery of the cylindrical sleeve A14.

On the other hand, a bearing B2 is mounted on the frame A5, and the divided shaft B1 is inserted and supported by the bearing B2. A bearing B16 is attached to the frame A7 facing the frame A5, and the bearing B16 is attached to the output shaft B
15 is inserted and supported. The split shaft B1 and the output shaft B15 are coaxially butted and supported in parallel with the drive shaft A2 and the drive shaft A9.

The split shaft B1 has a large diameter portion in the axial direction,
A gear B3 is fixed to the outer periphery of the large diameter portion, and the gear B3 meshes with the gear A4. Therefore, the gear B3 receives the rotation transmission from the gear A4,
It rotates in the direction of arrow b in FIG. 1 together with the split shaft B1. The housing outer periphery extending in an axial direction of its integrally with gear B3, clutch housing B5 through the one-way clutch B4 is mounted. One-way clutch B
4 transmits the rotational force from the gear B3 to the clutch housing B5 when the gear B3 rotates faster than the clutch housing B5 in the direction of arrow b. When the clutch housing B5 rotates faster than the gear B3, the gear B3 rotates. It has the effect of making the wheel idle. Also, the split shaft B
A clutch housing B7 is mounted on the outer periphery of the reduced diameter portion at the front end of the device 1 via a one-way clutch B6. When the clutch housing B7 rotates faster than the split shaft B1 in the direction of arrow b, the one-way clutch B6
The rotational force is transmitted from the clutch housing B7 to the split shaft B1, and when the split shaft B1 rotates faster than the clutch housing B7, the clutch housing B
7 has an effect of causing the idle rotation.

Similarly, the output shaft B15 has a large diameter portion and a reduced diameter portion in the axial direction, and a gear B14 is fixed to the outer periphery of the large diameter portion, and the gear B14 is in mesh with the gear A11. doing. Accordingly, the gear B14 receives rotation transmission from the gear A11 and rotates together with the output shaft B15 in the direction of the arrow b in FIG. The housing outer periphery extending in an axial direction of its integrally with gear B14, a clutch housing B12 via the one-way clutch B11 is mounted. The one-way clutch B11 transmits the rotational force from the clutch housing B12 to the gear B14 when the clutch housing B12 rotates in the direction of the arrow b faster than the gear B14, but transmits the clutch housing B12 when the gear B14 rotates faster. It has the effect of making the wheel idle. A clutch housing B9 is mounted on the outer periphery of the reduced diameter portion at the tip of the output shaft B15 via a one-way clutch B8. When the output shaft B15 rotates faster than the clutch housing B9 in the direction of the arrow b, the one-way clutch B8 transmits the rotational force from the output shaft B15 to the clutch housing B9, and the clutch housing B9 rotates faster than the output shaft B15. When it does, it acts to make the output shaft B15 idle.

A torsion coil spring B10 is mounted on the outer periphery of the clutch housing B7 and the one-way clutch B8. The torsion coil spring B10 has a clutch housing B7 and a one-way clutch B
8 and is substantially fixed to the clutch housing B7 and the one-way clutch B8. The torsion coil spring B10 is wound leftward, and when the output shaft B15 rotates faster than the split shaft B1 in the direction of the arrow b, the output shaft B1 is tightened by the action of the one-way clutch B6 and the one-way clutch B8.
5 rotation is regulated. As a result, an effect of preventing overrun of the output shaft B15 is achieved, as described later.

A sleeve B17 is provided between the end face of the clutch housing B5 and the end face of the clutch housing B12.
Is arranged. Further, the clutch housing B5,
A second torsion coil spring B1 is provided on the outer circumference of the sleeve B17.
3 is attached. The second torsion coil spring B13 is
The inner circumference of both ends is crimped to the outer circumference of the clutch housing B5 and the clutch housing B12, and is substantially fixed to the clutch housing B5 and the clutch housing B12. The sleeve B17 has an outer diameter smaller than the outer diameters of the clutch housing B5 and the clutch housing B12. As a result, in a state where no torsional force is applied, between the inner circumference of the second torsion coil spring B13 and the outer circumference of the sleeve B17. Is formed with a predetermined gap.
The second torsion coil spring B13 is wound rightward. When the second torsion coil spring B13 is twisted rightward by a predetermined angle, the second torsion coil spring B13 is tightly wound and comes into close contact with the outer periphery of the sleeve B17.

In this embodiment, the gear A4 has 65 teeth,
The number of teeth of the gear B3 is 55, the number of teeth of the gear A11 is 60, and the number of teeth of the gear B14 is 60. When the drive shafts A2 and A9 rotate at the same speed, the gear A4 and the gear A11 are the same. Gear B3, gear B1 meshing with them
The rotation speed of the gear B4 differs, that is, the gear B3 rotates faster in the direction of the arrow b than the gear B14.

Next, the operation of the speed change rotating device will be described.

In this variable speed rotation device, the drive shaft A2 and the drive shaft A9 are rotated at the same speed in the direction of arrow a. Drive shaft A2
Of the gear A through the one-way clutch A3
4 rotates in the same direction, the gear B3 meshing with the gear A4 rotates in the direction of arrow b, and the split shaft B1 rotates with it. Further, by the rotation of the drive shaft A9, the gear A11 rotates in the same direction via the one-way clutch A10, and the gear B14 meshing with the gear A11 rotates in the direction of arrow b.
At the same time, the output shaft B15 rotates.

As described above, since the gear ratio of gear A4 / gear B3 is made larger than the gear ratio of gear A11 / gear B14, gear B3 rotates faster in the direction of arrow b than gear B14. . The rotation of the gear B3 causes the clutch housing B5 to rotate via the one-way clutch B4. On the other hand, the clutch housing B12 cannot rotate faster than the gear B14 due to the one-way clutch B11. As a result, a right-handed torsion force acts on the second torsion coil spring B13 mounted between the clutch housing B5 and the clutch housing B12, and the second torsion coil spring B13 is tightened. When the second torsion coil spring B13 comes into close contact with the outer periphery of the sleeve B17 and the gap becomes zero, the clutch housing B5 and the clutch housing B12 are integrated, and at the same time, the strain energy of the second torsion coil spring B13 is released at one time,
The clutch housing B12 rotates at high speed. as a result,
The output shaft B15 rotates at a high speed via the one-way clutch B11 and the gear B14.

When the strain energy of the second torsion coil spring B13 is released, the gear B14 rotates at a high speed via the one-way clutch B11, so that the gear A11 meshing with the gear B14 rotates at a high speed in the direction of arrow a. At this time, since the one-way clutch A10 does not transmit the rotational force of the gear A11 to the drive shaft A9, the gear A11 idles with respect to the drive shaft A9. As a result, a rotation difference occurs between the gear A11 and the gear A4. The rotation of the gear A11 causes the clutch housing A16 to rotate via the one-way clutch A15. On the other hand, the clutch housing A1
No. 3 cannot be rotated faster than the gear A4 by the one-way clutch A12. As a result, a right-handed torsional force acts on the first torsion coil spring A17, and the first torsion coil spring A17 is tightened. When the first torsion coil spring A17 comes into close contact with the outer periphery of the cylindrical sleeve A14 and the gap becomes zero, the clutch housing A16 and the clutch housing A13 are integrated, the strain energy of the first torsion coil spring A17 is released, and the clutch housing A13 is released. Rotate at high speed. As a result, the gear A4 also rotates at a high speed via the one-way clutch A12,
No. 4 idles with respect to the drive shaft A2 by the one-way clutch A3.

The gear B3 meshing with the gear A4 normally rotates faster than the gear B14 due to the difference in the gear ratio described above, but the gear A4 rotates at high speed due to the release of the distortion energy of the first torsion coil spring A17. Then, receiving the rotation of the gear A4, the gear A4 further rotates. As a result, the gear B
The rotation difference between the second torsion coil spring B13 and the rotation of the second torsion coil spring B13 is further shortened. Then, when the second torsion coil spring B13 is tightened, the output shaft B15 rotates again at a high speed due to the release of the distortion energy. Thus, the second torsion coil spring B
Thirteen winding and release of strain energy, and first winding of the torsion coil spring A17 and release of strain energy occur alternately, and the cycle is gradually shortened. Second
Each time the distortion energy of the torsion coil spring B13 is released, the output shaft B15 rotates at a high speed, and its cycle is gradually shortened. As a result, the speed of the output shaft B15 is gradually increased.

When the drive shaft A2 of the first motor A1 and the drive shaft A9 of the second motor A8 are stopped, or when the strain energy of the second torsion coil spring B13 is released, the output shaft B15 overruns. There is a fear.
However, when the output shaft B15 rotates at a high speed, the rotation of the output shaft B15 is changed to the split shaft B1 by following the route of the one-way clutch B8 → the clutch housing B9 → the left-handed torsion coil spring B10 → the clutch housing B7 → the one-way clutch B6 → the split shaft B1. Is transmitted to Further, the split shaft B1 takes the route of the gear B3 → the one-way clutch B4 → the clutch housing B5 → the second torsion coil spring B13, and the second torsion coil spring B13.
Is applied again to apply a braking force to the output shaft B15. Also, as described above, the output shaft B
When the 15 rotates at a high speed, the first torsion coil spring A17 is wound and tightened, so that a braking force is also applied. As a result, overrun of the output shaft B15 is prevented.

In the above embodiment, the present invention is applied to a speed increasing rotation device. However, the device of the present invention has a gear ratio of gear A4 / gear B3 and a gear ratio of gear A11 / gear B14,
By selecting the spring constant and the like of the first torsion coil spring A17 and the second torsion coil spring B13, the output shaft B1
5 can be operated so as to be gradually decelerated. Hereinafter, the reason will be described.

In general, the force F required to compress and contract the spring by the distance x can be obtained by the following equation 1 according to Hook's law.

[0039]

## EQU1 ## F = kx (where k is a spring constant and x is a deformation distance of the spring).

The amount of work W required to contract the spring to a distance of ₀ to x0 can be obtained by the following _equation (2).

[0041]

(Equation 2)

When an object having a mass m is ejected upward by the spring force, the strain energy accumulated in the spring is transferred to the object, and becomes the velocity energy of velocity v represented by the following equation (3).

[0043]

(Equation 3)

On the other hand, the force for vibrating the object is expressed as a restoring force. Since the restoring force F always works to return to the original state, the restoring force F can be expressed by the following equation (4). From the following equation 5, the following equations 6 and 7 are derived.

[0045]

## EQU4 ## F = -kx (where k is a spring constant and x is a deformation distance of the spring).

[0046]

F = ma (where m is mass and a is acceleration)

[0047]

[Mathematical formula-see original document] ma = -kx

[0048]

(Equation 7)

Here, since k / m is a constant that does not change with time or displacement, the acceleration is proportional to the displacement and points toward the center. Therefore, a simple vibration occurs. Therefore, the following Expressions 9 and 10 are derived by comparing Expression 7 with Expression 8 below.

[0050]

Equation 8] a = -ω ² x (where, omega represents the rotational speed.)

[0051]

(Equation 9)

[0052]

(Equation 10)

[0053] Therefore, to Ku less angular frequency using a spring (rotational motion) it is found to be by reducing the bus Ne constant k. In order to reduce the spring constant k, for example, the diameter of the element wire of the coil spring may be reduced, or the diameter of the coil spring may be increased.

In the above embodiment, the gear A4 has 65 teeth, the gear B3 has 55 teeth, and the gear A11 has 6 teeth.
0, the number of teeth of the gear B14 is 60, but for example, the number of teeth of the gear A4 is 55, the number of teeth of the gear B3 is 55, and the gear A1
If the number of teeth of the first torsion coil spring B13 is changed to 54 and the number of teeth of the gear B14 is changed to 56,
Becomes １ ／, and the stored strain energy decreases.

As described above, the number of teeth of each gear is set so as to reduce the angular frequency (rotational motion) by reducing the spring constant k of each coil spring and to reduce the distortion energy accumulated in the spring. For example, it is possible to induce a deceleration operation.

In the above embodiment, if the direction of winding of each spring and the direction of engagement of each clutch are reversed, the same speed increase or rotation can be achieved for the rotation in the opposite direction (left rotation). A deceleration operation is achieved. Further, the shape of each gear is not limited to a normal spur gear, and gears having various tooth shapes can be freely selected. Furthermore, since the setting of the gap amount is proportional to the module size, a combination of different types of module sizes is possible.

[0057]

As described above, according to the present invention, the rotational forces of two motors rotating at a constant speed are utilized by utilizing the one-way clutch mechanism, the gear transmission mechanism, and the distortion energy of the torsion coil spring. A speed change rotating device capable of increasing or decreasing the speed by merging with one output shaft can be provided. Further, the speed change rotating device of the present invention can set a large speed change range, and
The shift operation can be performed automatically without manual or electric control. Such a device capable of continuously variable transmission can be applied to, for example, a mechanism for winding a belt-like object at a constant speed, and many application fields are conceivable. Furthermore, even if the speed change range is large,
Molding can be achieved.

[Brief description of the drawings]

FIG. 1 is a sectional view showing an embodiment of a speed change rotating device of the present invention.

FIG. 2 is a sectional view taken along the line AA of FIG. 1;

[Explanation of symbols]

 A1 First motor A2 Drive shaft A3 One-way clutch A4 Gear A5 Frame A6 Pole A7 Frame A8 Second motor A9 Drive shaft A10 One-way clutch A11 Gear A12 One-way clutch A13 Clutch housing A14 Cylindrical sleeve A15 One-way clutch A16 Clutch housing A17 B1 split shaft B2 bearing B3 gear B4 one-way clutch B5 clutch housing B6 one-way clutch B7 clutch housing B8 one-way clutch B9 clutch housing B10 torsion coil spring B11 one-way clutch B12 clutch housing B13 second torsion coil spring B14 gear B15 output shaft B16

Claims (1)

(57) [Claims] A drive shaft A2 of claim 1 the first motor A1, the drive
The drive shaft A9 of the second motor A8 , which rotates in the same direction as the drive shaft A2, is coaxially butted and arranged. The divided shaft B1 and the output shaft B15 are similarly coaxially butted, and the drive shaft A2 , A9 are arranged in parallel with each other, and the drive shaft A2 of the first motor A1 has a rotation direction of the drive shaft A2.
One-way clutch A3 that meshes at high speed inward
Via a gear A4 is mounted, further their integral with gear A4
The cylindrical housing periphery extending in an axial direction of the drive shaft A
2 through a one-way clutch A12 that meshes at a high speed on the outside with respect to the rotation direction of the cylinder clutch housing A1.
3 is mounted, the drive shaft A9 of the second motor A8, rotational direction of the drive shaft A2
One-way clutch A1 meshes at high speed inside
0 , the gear A11 is attached, and the gear A11 is
The cylindrical housing periphery extending in the axial direction in the body, drive
A cylindrical clutch housing A16 is mounted via a one-way clutch A15 that meshes with the rotation direction of the driving shaft A2 at a high speed inward, and a gear B3 is fixed to the divided shaft B1, and
The cylindrical housing periphery extending in the axial direction in the body, drive
Through <br/> one-way clutch B4 meshing inside fast the rotational direction opposite to the shaft A2, equipped with a cylindrical clutch housing B5, fixed gear B14 to the output shaft B15, a gear B14 one
The cylindrical housing periphery extending in the axial direction in the body, drive
A cylindrical clutch housing B12 is mounted via a one-way clutch B11 that engages at a high speed on the outside with respect to the rotation direction opposite to the driving shaft A2 . The gear A4 and the gear B3 mesh with each other, and the gear A11 and the gear A11 mesh with each other. Gear B
14 so that the gear ratio between the gears A4 and B3 and the gear ratio between the gears A11 and B14 are different from each other.
The housing A16 drives the clutch housing A13.
A first torsion coil spring A17 that is fastened when rotating at a high speed in the rotation direction of the driving shaft A2 is mounted, and the clutch housing B5 is disposed between the clutch housings B5 and B12.
Of the drive shaft A2 with respect to the switch housing B12
A variable speed rotation device comprising a second torsion coil spring B13 which is fastened when rotating at a high speed in a direction .