JPH07310804A - Transmission - Google Patents

Abstract

PURPOSE:To perform continuously variable gear shifting of an output shaft through simple constitution and easy operation by a method wherein various spur gears engaged with an input shaft and an output shaft installed coaxially with each other are disposed and the rotation speed of a rotary body effecting relative rotation with the input shaft is changed by a gear shifting means. CONSTITUTION:When a rotary body 8 is rotated in the same direction and the same speed as those of an input shaft 1, a gear shift spur gear 9, an input inner 7, an input outer spur gear 6, an intermediate inner spur gear 19, an intermediate outer spur gear 18, a planetary second outer spur gear 11, a planetary first outer spur gear 10, and a solar outer spur gear 4 are brought into respective locked state, and the gears 6, 7, 10, and 11 are not rotated but integrally rotated around an input rotary axis A. Thus, the number of revolutions of an output shaft 2 is brought into the same number of revolutions as that of the input shaft 1. When rotation of the rotary body 8 is further delayed than rotation of the input shaft 1 by a gear shifting means 17, the gears 6 and 7 are rotated around an eccentric axis C owing to a rotation speed difference therebetween and the gears 10 and 11 are rotated. Rotation of the gear 4, i.e., the output shaft 2, is further delayed than that of the input shaft 1 and rotation of the output shaft 2 is brought into a stop.

Description

Detailed Description of the Invention

[0001]

FIELD OF THE INVENTION The present invention relates to a transmission.

[0002]

2. Description of the Related Art As a transmission used for a machine tool, an industrial machine, a construction machine, an agricultural machine, a vehicle machine or the like, a transmission which is electrically controlled by an inverter or a servomotor has been known.

[0003]

However, in the above-mentioned transmission, there is a problem that the efficiency is poor because of low torque and insufficient output in the low speed range.

Further, in a transmission used in an automobile or the like which does not use electric power, there is a problem that control is difficult and the structure becomes complicated.

SUMMARY OF THE INVENTION It is therefore an object of the present invention to provide a transmission which has a simple structure, is easy to handle and manufacture, has a high efficiency in a wide range of speed change range, and has a good dynamic balance.

[0006]

In order to achieve the above object, a rotatable input shaft, an output shaft rotatable coaxially with an input rotation shaft center of the input shaft, and an output shaft coaxial with the output shaft are integrally formed. A sun outer spur gear that rotates, an eccentric shaft portion formed on the input shaft, and an input outer spur gear that is rotatably pivoted about the eccentric shaft center and rotates eccentrically around the input rotation shaft center, An input internal spur gear that rotates integrally with the input external spur gear coaxially and rotates eccentrically around the input rotation shaft; a rotating body that is rotatable relative to the input shaft coaxially with the input rotation shaft; A variable-speed external spur gear that rotates integrally with the rotating body and meshes with the input inner spur gear, and is rotatably pivotally mounted on the rotating body about an orbital axis parallel to the input rotational axis. Of the sun outer spur gear and is free to revolve around the input rotation axis. A first outer spur gear, a planet second outer spur gear that is integrally rotatable coaxially with the planet first outer spur gear and is free to revolve around the input rotation axis, and meshes with the second planet outer spur gear. And an intermediate outer spur gear that is rotatable around the input rotation axis, an intermediate inner spur gear that rotates integrally with the intermediate outer spur gear and that meshes with the input outer spur gear, and the rotation of the rotating body. A speed change means for changing the speed,
The number of teeth and the reference pitch circle of the variable speed outer spur gear and the intermediate inner spur gear are set to be the same, and the ratio of the number of teeth of the intermediate inner spur gear and the intermediate outer spur gear is set to 2: 1. The distance from the meshing point of the planetary first external spur gear and the sun outer spur gear to the meshing point of the planetary second outer spur gear and the intermediate outer spur gear, and the meshing point of the planetary first outer spur gear and the sun outer spur gear. To the above-mentioned axis of revolution, and the ratio is set to 1: 2.

Further, a rotatable input shaft, an output shaft which is rotatable coaxially with the input rotation axis of the input shaft, a sun outer spur gear which rotates integrally with the output shaft coaxially with the input shaft, An input external spur gear that is rotatably pivoted about the eccentric shaft center on the formed eccentric shaft portion and rotates eccentrically around the input rotation shaft center, and integrally rotates coaxially with the input external spur gear. An input internal spur gear that eccentrically rotates around the input rotation shaft center, a rotating body that is rotatable relative to the input shaft coaxially with the input rotation shaft center, and the input that rotates integrally with the rotation body coaxially. A variable speed internal spur gear that meshes with an outer spur gear, and is rotatably pivoted about the revolution axis parallel to the input rotation axis in the rotating body so as to mesh with the sun outer spur gear and the input. A planetary first external spur gear that can freely revolve around the axis of rotation, and the planetary first external spur gear A planetary second outer spur gear that rotates integrally around the input rotation axis and can freely revolve around the input rotation axis, and an intermediate first that meshes with the planetary second outer spur gear and is rotatable about the input rotation axis. An external spur gear, an intermediate second external spur gear that rotates integrally with the intermediate first external spur gear coaxially and meshes with the input internal spur gear, and a speed change means that changes the rotational speed of the rotating body. The number of teeth and the reference pitch circle of the variable speed internal spur gear and the intermediate second outer spur gear are set to be the same, and the ratio of the number of teeth of the intermediate second outer spur gear to the intermediate first outer spur gear is 2: 1 and the distance from the meshing point between the planetary first outer spur gear and the sun outer spur gear to the meshing point between the planetary second outer spur gear and the intermediate first outer spur gear, and the planetary first outer spur gear. The ratio of the distance from the mesh point of the spur gear and the outer spur gear to the orbital axis is set to 1: 2. That.

Furthermore, the number of teeth of the planetary first external spur gear and the planetary second external spur gear are slightly different. Furthermore, a plurality of planetary first external spur gears and a plurality of planetary second external spur gears are arranged at equal pitches in the circumferential direction on a circumference having a radius from the input rotation axis to the revolution axis.

Further, a rotatable input shaft, an output shaft rotatable coaxially with the input rotation shaft center of the input shaft, and an eccentric shaft portion formed on the output shaft rotatable about the eccentric shaft center. An output outer spur gear that is pivotally attached to and eccentrically rotates around the input rotation shaft center, and an output inner spur gear that integrally rotates coaxially with the output outer spur gear and rotates eccentrically around the input rotation shaft center, An input external spur gear that is rotatably pivoted about an eccentric shaft center on an eccentric shaft portion formed on the input shaft and rotates eccentrically around the input rotation shaft center, and coaxial with the input external spur gear. An input internal spur gear that rotates integrally and rotates eccentrically around the input rotating shaft, a rotating body that is rotatable relative to the input shaft coaxially with the input rotating shaft, and integrally rotates coaxially with the rotating body. And a variable speed first internal spur gear that meshes with the input external spur gear, and A second intermediate spur gear that rotates integrally with the output outer spur gear, meshes with the output inner spur gear and the input inner spur gear, and is rotatable about the input rotation axis An external spur gear and a speed change means for changing the rotation speed of the rotating body are provided, and the number of teeth and the reference pitch circle of the speed change first internal spur gear, the speed change second inner spur gear, and the intermediate outer spur gear are the same. It has been set.

Further, a rotatable input shaft, an output shaft rotatable coaxially with the input rotation shaft center of the input shaft, and an eccentric shaft portion formed on the output shaft rotatable about the eccentric shaft center. An output outer spur gear that is pivotally attached to and eccentrically rotates around the input rotation shaft center, and an output inner spur gear that integrally rotates coaxially with the output outer spur gear and rotates eccentrically around the input rotation shaft center, An input external spur gear that is rotatably pivoted about an eccentric shaft center on an eccentric shaft portion formed on the input shaft and rotates eccentrically around the input rotation shaft center, and coaxial with the input external spur gear. An input internal spur gear that rotates integrally and rotates eccentrically around the input rotating shaft, a rotating body that is rotatable relative to the input shaft coaxially with the input rotating shaft, and integrally rotates coaxially with the rotating body. And a variable speed first external spur gear that meshes with the input internal spur gear, and A speed-changing second external spur gear that integrally rotates with and meshes with the output inner spur gear, and an intermediate first inner spur gear that meshes with the input outer spur gear and is rotatable about the input rotation axis. An intermediate second internal spur gear that rotates integrally with the intermediate first internal spur gear and meshes with the output outer spur gear; and a speed change means that changes the rotational speed of the rotating body. The number of teeth and the reference pitch circle of the one outer spur gear, the variable speed second outer spur gear, the intermediate first inner spur gear, and the intermediate second inner spur gear are set to be the same.

[0011]

[Operation] With the input shaft rotating by the prime mover,
If the rotating body and the input shaft are made to have the same rotation direction and the same rotation speed by the speed changing means, all the gears that transmit the rotation torque from the input shaft to the output shaft are locked, and the output shaft rotates at the same speed as the input shaft Becomes a number. Then, when the rotation speed of the rotating body is delayed from the input shaft, the rotation speed difference causes the rotatable gear to start rotating in the gears, whereby, depending on the magnitude of the rotation speed difference, The output shaft rotates slowly.

[0012]

The present invention will be described in detail below with reference to the drawings illustrating the embodiments.

FIG. 1 shows an embodiment of a transmission according to the present invention. This transmission has a rotatable input shaft 1 and an input shaft 1.
Output shaft 2 which is rotatable coaxially with the input rotation axis A, a sun outer spur gear 4 which rotates integrally with the output shaft 2 coaxially with A, and an eccentric shaft portion 5 formed on the input shaft 1. An input external spur gear 6 rotatably (rotatably) pivotally about the center E,
An input internal spur gear 7 that rotates integrally with the input external spur gear 6 coaxially with the input external spur gear 6, a rotor 8 that is rotatable relative to the input shaft 1 coaxially with the input rotation axis A, and a coaxial A with the rotor 8. A variable-speed external spur gear 9 that rotates integrally, a planetary first external spur gear 10 that is rotatably mounted on a rotating body 8 about an orbital axis B that is parallel to the input rotational axis A, and a planetary first spur gear 10. A planetary second external spur gear 11 that rotates integrally with the outer spur gear 10 at the same axis B, an intermediate outer spur gear 18 that is rotatable about the input rotation axis A, and an intermediate outer spur gear 18 at the same coaxial A It is provided with a rotating intermediate internal spur gear 19 and a speed change means 17 for changing the rotation speed of the rotating body 8.

Specifically, the input shaft 1 and the output shaft 2 are rotatably supported by a casing or the like via bearings 3 ... The base end side of the input shaft 1 is connected to a prime mover (not shown) to be rotationally driven, and the tip end side of the output shaft 2 is connected to a machine that is driven at variable speeds. In the figure, the left side is the tip side and the right side is the base side.

The external sun spur gear 4 is integrally formed on a part of the output shaft 2 (base end portion in the illustrated example), and the tip end portion of the input shaft 1 is rotatably pivoted on the base end portion of the output shaft 2. Supported. The eccentric shaft portion 5 is formed on a part of the input shaft 1, and the eccentric shaft center C is parallel to the input rotation shaft A and is set to a relatively small eccentric amount.

The external input spur gear 6 and the internal input spur gear 7 are integrally formed so as to be aligned in the axial direction, and are eccentrically rotatable about the input rotation axis A. The input outer spur gear 6 meshes with the intermediate inner spur gear 19. The rotating body 8 is hollow and is provided on the input shaft 1 and the output shaft 2 so as to be fitted around the entire gears.

The variable speed outer spur gear 9 is integrally formed with the rotating body 8 and meshes with the input inner spur gear 7. The planetary first external spur gear 10 and the planetary second external spur gear 11 are integrally formed so as to be aligned in the axial direction, and are pivotally attached to a pivot 12 in the axial direction formed on the rotating body 8 to form a revolution axis. It is rotatable about B and revolves around the input rotation axis A.

The planetary first external spur gear 10 and the planetary second external spur gear 11 are paired with each other in a circumferential direction or the like on a circumference having a radius from the input rotation axis A to the revolution axis B. Arrange at a pitch.

The planetary first external spur gear 10 meshes with the sun outer spur gear 4 and the planetary second outer spur gear 11 meshes with the intermediate outer spur gear 18. The intermediate outer spur gear 18 and the intermediate inner spur gear 19 are integrally formed so as to be aligned in the axial direction, and rotatably attached to the input shaft 1.

The number of teeth of the variable speed outer spur gear 9 and the intermediate inner spur gear 19 and the reference pitch circle are set to be the same, and the ratio of the number of teeth of the intermediate inner spur gear 19 to the intermediate outer spur gear 18 is 2: 1. Set to. Further, the distance L ₁ from the meshing point between the planetary first external spur gear 10 and the sun outer spur gear 4 to the meshing point between the planetary second outer spur gear 11 and the intermediate outer spur gear 18, and the planetary first outer spur gear 10 The ratio of the distance L ₂ from the meshing point of the sun outer spur gear 4 to the revolution axis B (L
_1: L ₂₎ 1: Set to 2.

Here, to give an example of concrete numerical values such as the number of teeth of each gear in the embodiment of FIG. 1, there are 36 sun outer spur gears 4, 18 planetary first spur gears, 18 planetary spur gears. Two 27 outer spur gears 11 and intermediate outer spur gears 18, intermediate inner spur gears 19 and variable speed outer spur gears 9
54, the input external spur gear 6 is 48, and the input internal spur gear 7 is 60, and the dislocation amount is zero. Of course, other set values may be used, but it is preferable that the ratio between these gears be the same as in the above numerical example.

A pulley 13 is externally attached to the base end of the rotary member 8 via a slide key 14. Pulley 13
Consists of a pair of pulley halves 15a and 15b, and one pulley half 15a is fixed to the rotating body 8. The other pulley half body 15b is integrally rotatable with respect to the rotating body 8 and is slidable in the direction of the axis A, and is elastically biased in a direction approaching the pulley half body 15a by a spring or the like (not shown). To be done.

A V-belt 16 is wound around the pulley 13 and a pulley attached to a rotary shaft of an electric motor or the like (not shown), and the pulley 13 and the rotor 8 are rotated by the rotation of the rotary shaft.
Rotate together. Further, the V belt 16 is slid in the radial direction of the pulley 13 by moving the pulley half body 15b toward and away from the pulley half body 15a.
13 and the rotation speed of the rotating body 8 (that is, the variable speed spur gear 9,
The revolution speeds of the planetary first outer spur gear 10 and the planetary second outer spur gear 11) can be changed.

A transmission means 17 is constituted by the pulley 13, the V belt 16 and the like. In addition to this, it is also possible to freely configure the speed changing means 17 by using a friction wheel, hydraulic pressure, etc., and further, the speed changing means 17 that can control the rotating body 8 to rotate normally and reversely.
You are free to use.

Therefore, in the transmission constructed as described above, the rotating body 8 can be rotated in the same direction and rotational speed as the input shaft 1 with the input shaft 1 being rotated at a predetermined speed. For example, the variable speed outer spur gear 9, the input inner spur gear 7, the input outer spur gear 6, the intermediate inner spur gear 19, the intermediate outer spur gear 18, the planetary second outer spur gear 11, the planetary first outer spur gear 10, the sun outer The spur gears 4 are all locked, and the input inner spur gear 7, the input outer spur gear 6,
The planetary second outer spur gear 11 and the planetary first outer spur gear 10 rotate integrally around the input rotation axis A (in the same rotation direction as the input shaft 1) without causing rotation. Therefore, the output shaft 2 has the same rotation speed as the input shaft 1.

From this state, the rotation of the rotating body 8 is changed by the speed changing means.
When it is delayed from the rotation of the input shaft 1 at 17, both 8,
Due to the rotational speed difference of 1, the input inner spur gear 7 and the input outer spur gear 6 start to rotate about the eccentric axis C, and the planetary second outer spur gear 18 is passed through the intermediate inner spur gear 19 and the intermediate outer spur gear 18. Gear 11,
The planetary first outer spur gear 10 rotates, the rotation of the sun outer spur gear 4 (that is, the rotation of the output shaft 2) becomes slower than that of the input shaft 1, and finally the rotation of the output shaft 2 stops (hereinafter referred to as zero rotation). That).

In this way, the rotating means 8 is moved by the transmission means 17.
Simply by changing the rotation speed of the
Can be continuously variable. Moreover, the zero rotation of the output shaft 2 is
It is obtained regardless of the number of revolutions of the prime mover that rotates the input shaft 1, is guaranteed by the rotational force of the prime mover, and is a closed loop.

Further, in the transmission of FIG. 1, the intermediate internal spur gear 19
Since the variable speed spur gear 9 has the same diameter and the same number of teeth, there is no so-called "slip". In this transmission, without the automatic shifting means 17, for example, even if the rotation speed and torque of the input shaft 1 are constant, the rotation speed of the output shaft 2 and the like automatically change according to the load. ───, the number of teeth of the variable speed outer spur gear 9 and the intermediate inner spur gear 19 and the reference pitch circle, the teeth of the intermediate inner spur gear 19 and the intermediate outer spur gear 18 should be adjusted so that “slip” may occur. Adjust the number ratio, L ₁ : L _2, etc. In this transmission, in order to reduce the speed over a wider range, the rotating body 8
The transmission means 17 that can rotate the input shaft 1 in the same direction and in the opposite direction is used.

Next, FIG. 2 shows another embodiment in which the teeth of the variable speed outer spur gear 9, the input inner spur gear 7, the input outer spur gear 6, and the intermediate inner spur gear 19 in the embodiment of FIG. It is configured in reverse.

That is, in the transmission of FIG. 2, the input shaft 1, the output shaft 2, the sun outer spur gear 4, the rotor 8, the planetary first outer spur gear 10, the planetary second outer spur gear, which have the same construction as in FIG. 11 and speed change means 17
In addition to the input external spur gear 20, which is rotatably (rotatably) pivotally mounted on the eccentric shaft portion 5 formed on the input shaft 1 about the eccentric shaft center C, the input outer spur gear 20 is coaxial with the external spur gear 20. The internal spur gear 21 that rotates integrally with the rotating body 8, the variable speed internal spur gear 22 that integrally rotates with the rotor 8 coaxially with the input outer spur gear 20, and the mesh with the planetary second outer spur gear 11 and the input The intermediate first outer spur gear 23, which is rotatable around the rotation axis A, rotates integrally with the intermediate first outer spur gear 23 coaxially with the intermediate first outer spur gear 23, and the input inner spur gear
And an intermediate second external spur gear 24 that meshes with 21.

Specifically, the input outer spur gear 20 and the input inner spur gear 21 are integrally formed so as to be aligned in the axial direction, and are eccentrically rotatable about the input rotation axis A. Further, the variable speed internal spur gear 22 is integrally formed with the rotating body 8, and the intermediate first external spur gear 23 and the intermediate second external spur gear 24 are integrally formed so as to be aligned in the axial direction, so that the input shaft 1 is rotatable. Pivoted.

Furthermore, the number of teeth and the reference pitch circle of the variable speed internal spur gear 22 and the intermediate second external spur gear 24 are set to be the same, and
The ratio of the number of teeth of the intermediate second external spur gear 24 and the intermediate first external spur gear 23 is set to 2: 1, and the planetary second gear is changed from the meshing point of the planetary first external spur gear 10 and the sun external spur gear 4. The distance L ₁ to the meshing point between the outer spur gear 11 and the intermediate first outer spur gear 23, and the planetary first outer spur gear 10
And the distance L from the mesh point of the sun spur gear 4 to the revolution axis B
The ratio of ₂ and (L ₁ : L ₂ ) is set to 1: 2.

Here, to show an example of specific numerical values such as the number of teeth of each gear in the embodiment of FIG. 2, 33 sun sun spur gears 4, 21 planetary first spur gears, 21 planetary spur gears are used. Two outer spur gears 11 and middle first outer spur gears 23, 54 intermediate second outer spur gears 24 and variable speed inner spur gears 22, input outer spur gears 48, input inner spur gears
The number of 21 is 60 and the dislocation amount is zero. Of course, other set values may be used, but it is preferable that the ratio between these gears be the same as in the above numerical example.

When the input shaft 1 is rotated at a predetermined speed and the rotor 8 is rotated in the same direction and at the same rotation speed as the input shaft 1, the variable speed internal spur gear 22 and the external input spur gear 22 are rotated.
20, input internal spur gear 21, intermediate second outer spur gear 24, intermediate first outer spur gear 23, planet second outer spur gear 11, planet first outer spur gear 10,
The sun outer spur gears 4 are all locked, and the input outer spur gear 20, the input inner spur gear 21, the planetary second outer spur gear 11, and the planetary first outer spur gear 10 do not rotate and the input rotation shaft It rotates integrally around the center A (in the same rotation direction as the input shaft 1). Therefore, the output shaft 2 has the same rotation speed as the input shaft 1.

From this state, the rotation of the rotating body 8 is changed by the speed changing means.
When it is delayed from the rotation of the input shaft 1 at 17, both 8,
Input external spur gear 20 and input internal spur gear
21 starts to rotate around the eccentric axis C, and the planetary second outer spur gear 11 and the planetary first outer spur gear 10 rotate by way of the intermediate second outer spur gear 24 and the intermediate first outer spur gear 23. Then, the rotation of the sun outer spur gear 4 (that is, the rotation of the output shaft 2) becomes slower than that of the input shaft 1, and finally the rotation of the output shaft 2 stops.

In this way, the rotating means 8 is moved by the transmission means 17.
Simply by changing the rotation speed of the
Can be continuously variable. Moreover, the zero rotation of the output shaft 2 is
It is obtained regardless of the number of revolutions of the prime mover that rotates the input shaft 1, is guaranteed by the rotational force of the prime mover, and is a closed loop.

In the transmission of FIG. 2, the force becomes stronger when the number of teeth of the planetary first outer spur gear 10 and the planetary second outer spur gear 11 is slightly different (the number of teeth is closer). The number of teeth of the planetary first external spur gear 10 is set to be smaller than that of the planetary second external spur gear 11.

In the case of the transmission of the embodiment shown in FIG. 2, "slip" is likely to occur, which is suitable for automatic transmission. For example, it can be used as a converter in which the rotation speed of the output shaft 2 automatically changes according to the load. Further, as shown by the phantom line, the output shaft 2 is formed in a hollow shape, and the tip end side of the input shaft 1 is extended and rotatably inserted into the output shaft 2 so that a strong force is not required so much. It can be applied to automatic gear shifting of simple machines.

Next, FIG. 3 shows another embodiment, which is the sun outer spur gear 4, the planetary first outer spur gear 10, the planetary second outer spur gear 11, the intermediate first outer spur gear 23 in the embodiment of FIG. , Intermediate second external spur gear
It is configured by replacing 24 with another gear.

That is, in the transmission shown in FIG. 3, the input shaft 1, the rotor 8, the input external spur gear 20, and the input internal spur gear having the same structure as in FIG.
21, an output outer spur gear 26 rotatably (rotatably) about an eccentric shaft center E on an eccentric shaft portion 25 formed on the output shaft 2, and an output outer spur gear. 26 and coaxial E
Output internal spur gear 27 that rotates integrally with
And a transmission first internal spur gear 28 that rotates integrally with the input outer spur gear 20 and a transmission second inner spur gear 29 that rotates integrally with the rotor 8 coaxially with the output outer spur gear 26 and meshes with the output outer spur gear 26.
And an intermediate outer spur gear 30 that meshes with the output inner spur gear 27 and the input inner spur gear 21, respectively.

Specifically, the output outer spur gear 26 and the output inner spur gear 27 are integrally formed so as to be aligned in the axial direction, and are eccentrically rotatable about the input rotation axis A. Further, the first variable speed internal spur gear 28 and the second variable speed internal spur gear 29 are formed integrally with the rotating body 8. The intermediate outer spur gear 30 has an input rotary shaft center A on the input shaft 1.
It is rotatably pivoted around. Further, the number of teeth and the reference pitch circle of the first variable speed internal spur gear 28, the second variable speed internal spur gear 29, and the intermediate external spur gear 30 are set to be the same.

When the input shaft 1 is rotated at a predetermined speed and the rotating body 8 is rotated in the same direction and at the same rotation speed as the input shaft 1, the transmission first internal spur gear 28 and the input external spur gear 28 are rotated. Gear 20, input inner spur gear 21, intermediate outer spur gear 30, output inner spur gear 27, output outer spur gear 26, transmission second inner spur gear 29 are all locked, and input outer spur gear 20, inner input spur gear The spur gear 21, the output inner spur gear 27, and the output outer spur gear 26 rotate integrally around the input rotation axis A (in the same rotation direction as the input shaft 1) without causing rotation. Therefore, the output shaft 2 has the same rotation speed as the input shaft 1.

From this state, the rotation of the rotating body 8 is changed by the speed changing means.
When it is delayed from the rotation of the input shaft 1 at 17, both 8,
Input external spur gear 20 and input internal spur gear
21 starts to rotate about the eccentric axis C, and the output inner spur gear 27 and the output outer spur gear 26 rotate about the intermediate outer spur gear 30 to rotate the output inner spur gear 27 and the output outer spur gear 26. The eccentric rotation (that is, the rotation of the output shaft 2) becomes slower than that of the input shaft 1, and finally the rotation of the output shaft 2 stops.

In this way, the rotating means 8 is moved by the transmission means 17.
Simply by changing the rotation speed of the
Can be continuously variable. In this case, two component forces indicated by arrows F ₁ and F ₂ are connected at the output shaft 2 to form a rational closed loop.

Further, in the transmission of FIG. 3, the variable speed first internal spur gear 28, the variable speed second internal spur gear 29 and the intermediate external spur gear 30 have the same diameter.
There is no "slip" because it has the same number of teeth.

Next, FIG. 4 shows still another embodiment in which the gear teeth in the embodiment of FIG.

That is, in the transmission shown in FIG. 4, in addition to the input shaft 1, the output shaft 2, the rotor 8 and the speed changing means 17 having the same construction as in FIG. 3, the eccentric shaft portion 25 formed on the output shaft 2 is provided. The eccentric axis E
An output outer spur gear 31 rotatably (rotatably) pivoted about the output outer spur gear 31, an output inner spur gear 32 that integrally rotates coaxially with the output outer spur gear 31, and an eccentric shaft portion formed on the input shaft 1. 5, an input external spur gear 33 rotatably (rotatably) pivotally about its eccentric axis C, an input internal spur gear 34 which rotates integrally with the input external spur gear 33 coaxially with C, and a rotor 8 And a transmission first external spur gear 35 that integrally rotates with the input inner spur gear 34 and that mesh with the input inner spur gear 34, and a second shift outer spur gear that rotates integrally with the rotating body 8 coaxially with the output inner spur gear 32 and meshes with the output inner spur gear 32. An intermediate first internal spur gear 37 that meshes with the spur gear 36 and the input outer spur gear 33 and is rotatable about the input rotation axis A, and rotates integrally with the intermediate first inner spur gear 37 on the same axis A. An intermediate second internal spur gear 38 meshing with the output outer spur gear 31.

Specifically, the input outer spur gear 33 and the input inner spur gear 34 are integrally formed so as to be aligned in the axial direction, and are eccentrically rotatable about the input rotation axis A. Further, the output outer spur gear 31 and the output inner spur gear 32 are integrally formed so as to be aligned in the axial direction, and are eccentrically rotatable about the input rotation axis A.

The intermediate first internal spur gear 37 and the intermediate second internal spur gear 38 are integrally formed and pivotally attached to the input shaft 1. The variable speed first external spur gear 35 and the variable speed second external spur gear 36 are formed integrally with the rotating body 8. Further, the variable speed first external spur gear 35, the variable speed second outer spur gear 36, the intermediate first internal spur gear 37, and the intermediate second internal spur gear 38.
Set the same number of teeth and the standard pitch circle.

When the input shaft 1 is rotated at a predetermined speed and the rotating body 8 is rotated in the same direction and at the same rotation speed as the input shaft 1, the variable speed first external spur gear 35 and the input internal spur gear 35 are rotated. The gear 34, the input external spur gear 33, the intermediate first internal spur gear 37, the intermediate second internal spur gear 38, the output external spur gear 31, the output internal spur gear 32, and the transmission second external spur gear 36 are all in the locked state. Input internal spur gear 34, input outer spur gear 33, output outer spur gear 31, output inner spur gear
32 does not rotate, but rotates integrally (in the same rotation direction as the input shaft 1) around the input rotation axis A. Therefore, the output shaft 2 has the same rotation speed as the input shaft 1.

From this state, the rotation of the rotating body 8 is changed by the speed changing means.
When it is delayed from the rotation of the input shaft 1 at 17, both 8,
1 internal spur gear 34 and input external spur gear
33 starts to rotate around the eccentric shaft center C, and through the intermediate first internal spur gear 37 and the intermediate second internal spur gear 38, the output external spur gear.
31, the output inner spur gear 32 rotates, the eccentric rotation of the output outer spur gear 31 and the output inner spur gear 32 (that is, the rotation of the output shaft 2) becomes slower than that of the input shaft 1, and finally the rotation of the output shaft 2 Stops.

In this way, the rotating means 8 is moved by the transmission means 17.
Simply by changing the rotation speed of the
Can be continuously variable. In this case, two component forces indicated by arrows F ₁ and F ₂ are connected at the output shaft 2 to form a rational closed loop.

In the transmission of FIG. 4, the variable speed first external spur gear 35, the variable speed second external spur gear 36, the intermediate first internal spur gear 37 and the intermediate second internal spur gear 38 have the same diameter and the same number of teeth. Therefore, "slip"
There is no.

The present invention is not limited to the above-mentioned embodiments, and design changes can be freely made without departing from the gist of the present invention.
For example, the numbers of the planetary first external spur gear 10 and the planetary first external spur gear 11 can be freely increased or decreased.

In FIG. 1, the rotor 8 and the variable speed external spur gear 9, the input outer spur gear 6 and the input inner spur gear 7, the intermediate outer spur gear.
18 and the intermediate inner spur gear 19, the planetary first outer spur gear 10, the planetary second outer spur gear 11, the output shaft 2 and the sun outer spur gear 4 are not integrally formed, but separate parts are fixed to each other. May be integrated. Further, in FIG. 2, the rotating body 8 and the internal variable speed spur gear 22,
Input external spur gear 20, input internal spur gear 21, intermediate first external spur gear 23
The intermediate second external spur gear 24 and the second intermediate spur gear 24 may not be integrally formed, but separate components may be fixed to each other and integrated.

In FIG. 3, the rotary body 8 and the variable speed first internal spur gear 28, the rotary body 8 and the variable speed second internal spur gear 29, the output outer spur gear 26 and the output internal spur gear 27 are respectively integrated. Instead of being formed, separate parts may be fixed to each other and integrated. Furthermore, FIG.
, The rotating body 8 and the variable speed first outer spur gear 35, the rotating body 8 and the variable speed second outer spur gear 36, the input outer spur gear 33 and the input inner spur gear 34,
Even if the intermediate first internal spur gear 37 and the intermediate second internal spur gear 38, the output outer spur gear 31, and the output inner spur gear 32 are not integrally formed, respectively, but separate components are fixed to each other and integrated. Good.

[0057]

Since the present invention is constructed as described above, it has the following great effects.

The transmission of the present invention has a simple shape such as a gear.
Since it is composed of structural parts, it is easy to handle and manufacture. Further, by simply changing the rotation speed of the rotating body 8 by the speed changing means 17, the output shaft 2 can be speed-changed to a desired rotation speed in a stepless and constant output range. Moreover, because of the closed loop, the reaction force does not act on the gear, and the meshed gear can be turned lightly. Further, since it is not necessary to transfer each gear, strength is not insufficient and durability is good.
Furthermore, since the eccentricity of the eccentric shaft portions 5, 25 is small, the dynamic balance is good, and vibration during rotation can be suppressed.

Further, in the transmission according to the first, fifth and sixth aspects, there is no slip of the gears and the efficiency is high. In the transmission according to the second aspect, slipping easily occurs, which is suitable for automatic transmission.

Further, in the transmission according to claim 3, the output shaft 2 can be rotated with a high torque, and in the transmission according to claim 4, the planetary first outer spur gear 10 and the planetary second outer spur gear are provided. It is not necessary to use a weight balance (weight) for 11 and the weight balance of the entire transmission is improved, and vibration during rotation can be further suppressed.

[Brief description of drawings]

FIG. 1 is a sectional side view showing an embodiment of the present invention.

FIG. 2 is a sectional side view showing another embodiment.

FIG. 3 is a sectional side view showing another embodiment.

FIG. 4 is a sectional side view showing still another embodiment.

[Explanation of symbols]

1 Input Shaft 2 Output Shaft 4 Sun External Spur Gear 5 Eccentric Shaft 6 Input External Spur Gear 7 Input Internal Spur Gear 8 Rotating Body 9 Variable Outer Spur Gear 10 Planetary 1st Outer Spur Gear 11 Planetary 2nd Outer Spur Gear 17 Speed Change Means 18 Middle outer spur gear 19 Middle inner spur gear 20 Input outer spur gear 21 Input inner spur gear 22 Variable speed inner spur gear 23 Middle first outer spur gear 24 Middle second outer spur gear 25 Eccentric shaft 26 Output outer spur gear 27 Output Internal spur gear 28 Speed 1st internal spur gear 29 Speed 2nd internal spur gear 30 Middle outer spur gear 31 Output outer spur gear 32 Output inner spur gear 34 Input outer spur gear 34 Input inner spur gear 35 Speed first outer spur gear 36 Speed 2nd external spur gear 37 Intermediate 1st internal spur gear 38 Intermediate 2nd internal spur gear A Input rotation shaft center B Revolution shaft center C Eccentric shaft center E Eccentric shaft center L ₁ distance L ₂ distance

Claims (6)

[Claims] 1. A rotatable input shaft 1, an output shaft 2 which is rotatable coaxially with an input rotation axis A of the input shaft 1, and a sun external spur gear which rotates integrally with the output shaft 2 coaxially A. 4, an input external spur gear 6 which is rotatably attached to an eccentric shaft portion 5 formed on the input shaft 1 about an eccentric shaft center E thereof and eccentrically rotates around the input rotary shaft center A; An input internal spur gear 7 that rotates integrally with the input external spur gear 6 on the same axis C and eccentrically rotates around the input rotation axis A, and is rotatable relative to the input shaft 1 coaxially with the input rotation axis A. Rotating body 8 and the rotating body 8 and the input internal spur gear 7
And a variable speed external spur gear 9 that meshes with the sun outer spur gear 4 that is rotatably pivoted in the rotating body 8 about a revolution axis B parallel to the input rotation axis A. A planetary first external spur gear 10 that can freely revolve around the input rotation axis A.
And a planetary second external spur gear 11 which is integrally rotatable with the planetary first external spur gear 10 on the same axis B and is revolvable around the input rotation axis A.
An intermediate external spur gear 18 that meshes with the planetary second external spur gear 11 and is rotatable about the input rotation axis A, and integrally rotates with the intermediate outer spur gear 18 coaxially with the intermediate outer spur gear 18. An intermediate inner spur gear 19 meshing with the outer spur gear 6 and a speed change means 17 for changing the rotation speed of the rotating body 8 are provided, and the number of teeth of the speed change outer spur gear 9 and the intermediate inner spur gear 19 and a reference pitch. The circles are set to be the same, the ratio of the number of teeth of the intermediate inner spur gear 19 and the intermediate outer spur gear 18 is set to 2: 1, and the planetary first outer spur gear 10 and the sun outer spur gear 4 are Distance L from the meshing point to the meshing point of the planetary second outer spur gear 11 and the intermediate outer spur gear 18
_1, the distance L ₂ from the engagement point of the planet first Hokahira gear 10 and the sun Hokahira gear 4 to the revolution axis B, and a ratio of 1: 2
A transmission characterized by being set to. 2. A rotatable input shaft 1, an output shaft 2 which is rotatable coaxially with an input rotation axis A of the input shaft 1, and a sun external spur gear which rotates integrally with the output shaft 2 coaxially. 4, an input external spur gear 20 rotatably attached to an eccentric shaft portion 5 formed on the input shaft 1 about an eccentric shaft center C thereof and eccentrically rotated around the input rotary shaft center A; An input internal spur gear 21 that rotates integrally with the input external spur gear 20 on the same axis C and rotates eccentrically around the input rotation axis A, and is rotatable relative to the input shaft 1 coaxially with the input rotation axis A. And the input external spur gear 20 while rotating integrally with the rotating body 8 coaxially with the rotating body 8
And a variable speed internal spur gear 22 that meshes with the sun outer spur gear 4 that is rotatably attached to the rotating body 8 about a revolution axis B parallel to the input rotation axis A. A planetary first external spur gear 10 that can freely revolve around the input rotation axis A.
And a planetary second external spur gear 11 which is integrally rotatable with the planetary first external spur gear 10 on the same axis B and is revolvable around the input rotation axis A.
And an intermediate first external spur gear 23 that meshes with the planetary second external spur gear 11 and is rotatable about the input rotation axis A.
And an intermediate second outer spur gear 24 that rotates integrally with the intermediate first outer spur gear 23 on the same axis A and meshes with the input inner spur gear 21.
And a speed change means 17 for changing the rotation speed of the rotating body 8.
And the above-mentioned variable internal spur gear 22 and intermediate second external spur gear 24.
The number of teeth and the reference pitch circle are set to be the same, the ratio of the number of teeth of the intermediate second external spur gear 24 and the intermediate first external spur gear 23 is set to 2: 1, and the planetary first outer The distance L ₁ from the meshing point of the spur gear 10 and the sun outer spur gear 4 to the meshing point of the planetary second outer spur gear 11 and the intermediate first outer spur gear 23, and the planetary first outer spur gear 10 and the sun outer A transmission characterized in that a ratio of a distance L ₂ from the meshing point of the spur gear 4 to the revolution axis B is set to 1: 2. 3. A planetary first external spur gear 10 and a planetary second external spur gear.
The transmission according to claim 2, wherein the number of teeth of 11 is slightly different. 4. A plurality of first planetary external spur gears 10 ... And second planetary external spur gears 11 ... are circled on a circle having a radius from the input rotation axis A to the revolution axis B as a radius. The transmission according to claim 1, wherein the transmission is arranged at equal pitches in the direction. 5. A rotatable input shaft 1, an output shaft 2 rotatable coaxially with an input rotation axis A of the input shaft 1, an eccentric shaft portion 25 formed on the output shaft 2, and an eccentric shaft thereof. An output external spur gear 26, which is rotatably pivoted about a center E and eccentrically rotates around the input rotation axis A, and an output outer spur gear 26 coaxial with the output external spur gear 26.
The output internal spur gear 27, which rotates integrally with the eccentric shaft center A and the output internal spur gear 27 that eccentrically rotates around the input rotation shaft A, and the eccentric shaft portion 5 formed on the input shaft 1 so as to be rotatable about the eccentric shaft center C. Input spur gear that is eccentrically rotated about the input rotation axis A
20 and an input internal spur gear 21 that rotates integrally with the input external spur gear 20 on the same axis C and eccentrically rotates around the input rotation axis A,
A rotating body 8 which is rotatable relative to the input shaft 1 coaxially with the input rotating shaft A, and a first speed change gear which rotates integrally with the rotating body 8 coaxially with the rotating body 8 and meshes with the input external spur gear 20. The spur gear 28, the variable speed second inner spur gear 29 which rotates integrally with the rotating body 8 coaxially with the rotating body 8 and meshes with the output outer spur gear 26, the output inner spur gear 27 and the input inner spur gear 21 respectively. An intermediate outer spur gear 30 that meshes with the input rotation axis A and is rotatable about the input rotation axis A, and a speed change means 17 that changes the rotational speed of the rotor 8 are provided. A transmission in which the number of teeth and the reference pitch circle of the second internal spur gear 29 and the intermediate external spur gear 30 are set to be the same. 6. A rotatable input shaft 1, an output shaft 2 rotatable coaxially with an input rotation axis A of the input shaft 1, an eccentric shaft portion 25 formed on the output shaft 2, and an eccentric shaft thereof. An output external spur gear 31 that is rotatably pivoted about a center E and rotates eccentrically around the input rotating shaft center A, and an output outer spur gear 31 coaxial with the output external spur gear 31.
The output internal spur gear 32, which rotates integrally with the eccentric shaft center A, and the output internal spur gear 32 that eccentrically rotates around the input rotation shaft A and the eccentric shaft portion 5 formed on the input shaft 1 so as to be rotatable about the eccentric shaft center C. Input spur gear that is eccentrically rotated about the input rotation axis A
33, and an input internal spur gear 34 that rotates integrally with the input external spur gear 33 on the same axis C and eccentrically rotates around the input rotation axis A.
A rotating body 8 that is rotatable relative to the input shaft 1 coaxially with the input rotating shaft A, and a first outer gear that rotates integrally with the rotating body 8 coaxially with the rotating body 8 and meshes with the input internal spur gear 34. A spur gear 35, a speed-changing second external spur gear 36 that integrally rotates with the rotating body 8 coaxially with the output inner spur gear 32, and meshes with the input outer spur gear 33, and the input rotating shaft. Heart A
An intermediate first internal spur gear 37, which is rotatable around the center, and an intermediate second internal spur gear 38 which rotates integrally with the intermediate first internal spur gear 37 on the same axis A and meshes with the output outer spur gear 31; A speed change means 17 for changing the rotation speed of the rotating body 8;
The number of teeth and the reference pitch circle of the transmission first outer spur gear 35, the transmission second outer spur gear 36, the intermediate first inner spur gear 37, and the intermediate second inner spur gear 38 are set to be the same. Machine.