JPH07133846A - Transmission - Google Patents

Abstract

PURPOSE:To carry out great speed decrease and increase with simple structure. CONSTITUTION:A revolving gear part 28 is constituted by coaxially and integrally forming a first pinion gear 30 and a second pinion gear 32. A driving means 34 revolves the revolving gear part 28 on a specified circular orbit free to autorotate. A fixed ring gear 38 is formed in a ring shape and fixed so as to surround the circular orbit, and a first internal tooth 40 with which the first pinion gear 30 is engaged and free to roll is on it is formed on the inner peripheral surface of it. An output ring gear 44 is formed in a ring shape, arranged so as to surround the circular orbit coaxially with the fixed ring gear 38, rotatable in the circumferential direction and has a second internal tooth 52 free to roll as the second pinion gear 32 is engaged with it on its inner peripheral surface.

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 Conventionally, as a transmission for performing deceleration and acceleration, there is known a transmission in which gears are combined and the speed of an output portion is decelerated and increased according to the gear ratio.

[0003]

However, the conventional transmission has the following problems. When performing large deceleration or acceleration, gears must be combined in multiple stages.
As a result, there are problems that the structure of the transmission becomes complicated and many failures occur, and that the transmission cannot be increased in size. Therefore, it is an object of the present invention to provide a transmission that can perform large deceleration and speed increase with a simple structure.

[0004]

In order to solve the above problems, the present invention has the following constitution. That is, a swivel gear portion in which a first pinion gear and a second pinion gear are coaxially and integrally formed, drive means for swiveling the swivel gear portion in a predetermined circular orbit, and a ring shape. A fixed ring gear that is fixed to surround the circular orbit and has first inner teeth that are rollable by meshing with the first pinion gear on the inner peripheral surface; Shaped like a circle, arranged coaxially with the fixed ring gear so as to surround the circular orbit, and rotatable in the circumferential direction, and the second pinion gear meshes with the inner peripheral surface to roll. Second
And an output ring gear having internal teeth formed therein. Further, in the above-mentioned transmission, a plurality of the turning gear parts may be provided so as to integrally turn the circular orbit. Further, the drive means includes the first
It is also possible to provide a drive gear for meshing with the pinion gear and rotating to rotate the swing gear portion while rotating.

[0005]

[Operation] The operation will be described. When the turning gear unit turns by the driving means, the first pinion gear meshing with the fixed ring gear turns and rotates about its own axis. The second pinion gear formed integrally with the first pinion gear also performs the same turning and rotation. The rotation speed of the first pinion gear and the second pinion gear, that is, the rotation gear portion is defined by the number of teeth between the first pinion gear and the first inner teeth of the fixed ring gear. The output ring gear meshed with the second pinion gear by the rotation and rotation of the second pinion gear is the second pinion gear and the second pinion gear.
It rotates in the circumferential direction at a speed specified by the number of teeth with the internal teeth of the. In particular, if a plurality of turning gear portions are provided and the circular orbit is integrally turned, the output ring gear can be rotated while being supported at a plurality of points. Further, when the drive means is provided with the drive gear, the gear is changed between the drive gear and the first pinion gear, so that a larger gear ratio can be obtained.

[0006]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT A preferred embodiment of the present invention will now be described in detail with reference to the accompanying drawings. (First Embodiment) A first embodiment will be described with reference to FIGS. First, the configuration will be described. Reference numeral 10 denotes a main body portion, which includes a lower base 12, an upper cover 14, and a connecting portion 16. The lower base 12 is supported by legs (not shown). The upper cover 14 has a through hole 18 at the center. Reference numeral 20 denotes an input shaft, which is rotatably and vertically inserted in the center of the lower base 12 via a bearing.

Reference numeral 22 is a lever, one end of which is horizontally fixed to the upper end of the input shaft 20 via a key 24. Therefore, the lever 22 rotates in the horizontal plane as the input shaft 20 rotates. A vertical shaft 26 is erected upward at the other end of the lever. Reference numeral 28 denotes a turning gear portion, and a first pinion gear 30 and a second pinion gear 32 are formed in the vertical direction. The first pinion gear 30 and the second pinion gear 32 having different numbers of teeth are coaxially and integrally formed. The swivel gear portion 28 is fitted onto the vertical shaft 26 so as to be rotatable (spin). When the lever 22 rotates, the turning gear unit 28 turns a circular orbit having the radius of the lever 22 (arrow A). Reference numeral 34 is a servo motor which is an example of a driving means, and is arranged below the lower base 12 via a fixing member 36. The motor 34 rotates the input shaft 20 and, in turn, turns the turning gear portion 28 (arrow A). The driving means is not limited to a servo motor,
For example, any means such as a mechanism in which an internal combustion engine and a crank are combined can be used as long as the turning gear portion 28 can rotate about a predetermined circular orbit so that the turning gear portion 28 can rotate.

Reference numeral 38 denotes a fixed ring gear formed in a ring shape, which is arranged coaxially with the through hole 18 and fixed to the lower surface of the upper cover 14. The fixed ring gear 38 is fixed so as to surround the circular orbit of the turning gear portion 28. On the inner peripheral surface of the fixed ring gear 38, first inner teeth 40 which are meshed with the first pinion gear 30 and capable of rolling (spinning) are formed. 42 is an outer ring portion, which is formed in a ring shape. The outer ring portion 42 is fixed to the edge of the through hole 18 of the upper cover 14.

Reference numeral 44 denotes an output ring gear formed in a ring shape and arranged inside the outer ring portion 42 coaxially with the through hole 18. A steel ball 46 is inserted between the output ring gear 44 and the outer ring portion 42 to form a ball bearing structure. Therefore, the output ring gear 44 is rotatable in the circumferential direction. The output ring gear 44 is also arranged so as to surround the circular orbit of the turning gear portion 28. Also, the output ring gear 4
On the inner peripheral surface of No. 4, second internal teeth 52 which are meshed with the second pinion gear 32 and capable of rolling (spinning) are formed. 48
Is an output part and is fixed to the upper surface of the output ring gear 44. An output shaft 50 is provided upright at the center of the upper surface of the output section 48. In this embodiment, the output shaft 50 is the output ring gear 4.
Since it rotates together with 4 (arrow B), it is possible to take out the shaft rotation output that has been decelerated or accelerated from the output shaft 50. The output may be taken out directly from the output ring gear 44 instead of the output shaft 50. In that case, the output is not the shaft rotation output but the turning output.

Next, the operation of the transmission having the above structure will be described. When the motor 34 is driven, the input shaft 20 is rotated. Since the input shaft 20 and the lever 22 are integrated, the lever 22 rotates in a horizontal plane, so that the swivel gear portion 28 swivels on a circular orbit having the radius of the length of the lever 22 (arrow A). At that time, since the first pinion gear 30 meshes with the first internal teeth 40 of the fixed ring gear 38, it rotates while rotating. The second pinion gear 32 integrally formed with the first pinion gear 30 also performs the same turning and rotation. First pinion gear 30 and second
The rotation speed of the pinion gear 32 of the first pinion gear 3 is
0 and the number of teeth between the first inner teeth 40 of the fixed ring gear 38 are defined.

The output ring gear 44 meshed with the second pinion gear 32 is rotated by the second pinion gear 32 to rotate and rotate, so that the output ring gear 44 becomes the second pinion gear 3.
2 and the second inner teeth 52 rotate at a speed defined by the relationship between the numbers of teeth. As a result, the changed shaft rotational force is output from the output shaft 50 (arrow B). That is, in the transmission of the present embodiment, the first pinion gear 30 and the fixed ring gear 38
Of the rotation of the orbiting gear portion 28 that has been changed according to the number of teeth of the first inner teeth 40, and the relation of the number of teeth of the second pinion gear 32 and the second inner teeth 52 of the output ring gear 44. Since gear shifting is performed with, it is possible to perform extremely large deceleration and acceleration.

(Second Embodiment) A second embodiment will be described with reference to FIGS. The same components as those in the first embodiment are designated by the same reference numerals as those in the first embodiment, and the description thereof will be omitted. In the second embodiment, the lever 22a is formed in a cross shape in a plane, and turning gear portions 28a, 28b, 28c, 28d are provided at the respective tip portions of the lever 22a. The turning gears 28a, 28b, 28c, 28d are all formed to have the same radius, the same number of teeth, etc., and the first pinion gears 30a, 30b, 30c, 30d are all the first internal teeth 40 of the fixed ring gear 38. The second pinion gears 32a, 32b, 32c, 32d are all in mesh with the second inner teeth 52 of the output ring gear 44. The configuration in which the changed rotational force is extracted from the output ring gear 44 and the output shaft 50 is the same as that in the first embodiment, but in the second embodiment, it is always output at a plurality of locations (four locations in the case shown). The ring gear 44 can be rotated while being supported.
Therefore, eccentricity of the output ring gear 44 can be prevented, so that noise and vibration can be prevented and stable rotation can be performed.

(Third Embodiment) A third embodiment will be described with reference to FIGS. 6 and 7. The same components as those of the preceding embodiment are designated by the same reference numerals and the description thereof will be omitted. In the first and second embodiments, the motor 34 directly rotates the swing gear portion 28 or 28a, 28b, 28c, 28.
It is turning d. However, in the configurations of the first and second embodiments, the motor 34 may be required to have a large output torque. The transmission of the third embodiment is a transmission that requires a small output torque. A driving gear 60 is fixed to the upper end of the input shaft 20 connected to the motor 34. The drive gear 60 is arranged coaxially with the fixed ring gear 38 and the output ring gear 44, and rotates integrally with the input shaft 20 which is rotationally driven by the motor 34. Furthermore, the drive gear 6
0 is all the first pinion gears 30a, 30b, 30
c, 30d, and the first pinion gear 30
It acts as a sun gear for a, 30b, 30c and 30d. The input shaft 20 is rotatably inserted into the lever 22a via a ball bearing 62.

In the transmission of the third embodiment having the above construction, the motor 34 is driven to drive the input shaft 20 and the drive gear 6.
When 0 is rotated, the drive gear 60 rotates the meshed first pinion gears 30a, 30b, 30c, 30d. As a result, all of the swivel gear parts 28 or 28a, 28b, 28c, 28d provided on the lever 22a.
Turns around a predetermined circular orbit while rotating. In the third embodiment, the gear shifting function of the turning gear parts 28a, 28b, 28c, 28d, the fixed ring gear 38 and the output ring gear 44 is the same as that of the second embodiment, and therefore the description thereof is omitted.

In the third embodiment, since only the drive gear 60 directly drives the motor 34 to rotate, the output torque of the motor 34 can be reduced. Further, since the drive gear 60 has a function as a sun gear with respect to the first pinion gears 30a, 30b, 30c, 30d, the drive gear 60 and the first
The pinion gears 30a, 30b, 30c, 30d also have a gear shifting effect, and a larger gear ratio can be obtained. Further, as compared with the second embodiment, when the same output torque is obtained, the turning gear portion 28a together with the lever 22a,
Since it is sufficient to rotate the whole 28b, 28c, 28d at a low speed, it is possible to suppress the generation of noise. It should be noted that in the third embodiment, the drive gear 60 is replaced by a plurality of swing gear portions 28 or 28.
Although it is provided in the transmission having a, 28b, 28c, 28d, it may be provided in the transmission having one swing gear portion 28 as in the first embodiment.

In the first to third embodiments described above, only one set of the fixed ring gear 38 and the output ring gear 44 is provided, but a second vertical shaft is erected on the upper surface of the output ring gear 44. When the second swing gear portion is rotatably fitted onto the second vertical shaft, and the second fixed ring gear and the second output ring gear are provided so as to surround the circular orbit of the second swing gear portion. Further, gear shifting is possible. In the multi-stage combination, not only these two stages but also any number of stages can be combined, so that it is possible to set a desired number of gear stages according to the driven body or the like. Although various preferred embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and it goes without saying that many modifications can be made without departing from the spirit of the invention. .

[0017]

When the transmission according to the present invention is used, the rotation of the orbiting gear portion, which is speed-changed in accordance with the number of teeth of the first pinion gear and the first internal teeth of the fixed ring gear, is further reduced to the second value. Since the gear shift is performed according to the number of teeth between the pinion gear and the second inner tooth of the output ring gear, extremely large deceleration and acceleration can be performed, so that the number of teeth can be reduced without combining a large number of gears. The gear ratio can be set only by adjustment. Therefore, the structure is simple, and it is possible to contribute to reduction in size and thickness. In particular, if the configuration of claim 2 is adopted, the output ring gear can be rotated while being supported at a plurality of locations. Therefore, eccentricity of the output ring gear can be prevented, so that noise and vibration can be prevented and stable rotation can be performed. Further, if the structure of claim 3 is adopted, only the drive gear is directly driven to rotate, so that the output of the drive means can be made small. Since the drive gear has a function as a sun gear with respect to the first pinion gear, a gear shift effect occurs between the two, and a larger gear ratio can be obtained, and the rotation speed of the swing gear portion can be gradually reduced. Therefore, it has a remarkable effect of suppressing the generation of noise.

[Brief description of drawings]

FIG. 1 is a plan view showing a first embodiment of a transmission according to the present invention.

FIG. 2 is a plan view showing a state in which an output portion is removed in the transmission of the first embodiment.

FIG. 3 is a front sectional view of the transmission of the first embodiment.

FIG. 4 is a plan view showing a state in which an output portion is removed in the transmission of the second embodiment.

FIG. 5 is a front sectional view of a transmission according to a second embodiment.

FIG. 6 is a plan view showing a state in which an output portion is removed in the transmission of the third embodiment.

FIG. 7 is a front sectional view of a transmission according to a third embodiment.

[Explanation of symbols]

22, 22a Lever 28, 28a, 28b, 28c, 28d Revolving gear unit 30, 30a, 30b, 30c, 30d First pinion gear 32, 32a, 32b, 32c, 32d Second pinion gear 34 Servo motor 38 Fixed ring Gear 40 1st internal tooth 44 Output ring gear 52 2nd internal tooth 60 Drive gear

Claims (3)

[Claims] 1. A swivel gear portion in which a first pinion gear and a second pinion gear are coaxially and integrally formed, and a drive means for swiveling the swivel gear portion in a predetermined circular orbit so as to rotate. A fixed ring gear that is formed in a ring shape and is fixed so as to surround the circular orbit, and has first inner teeth that are rollable by meshing with the first pinion gear on the inner peripheral surface. Is formed in a ring shape and is arranged coaxially with the fixed ring gear so as to surround the circular orbit, and is rotatable in the circumferential direction, and the second pinion gear meshes with the inner peripheral surface to rotate. An output ring gear having movable second inner teeth formed therein. 2. The plurality of turning gear portions are provided, and turn together on the circular orbit.
Gearbox described. 3. The drive means is provided with a drive gear that meshes with the first pinion gear and rotates to rotate the swing gear portion while rotating. The transmission according to Item 1 or 2.