JPH0351553A - planetary gear system - Google Patents

Abstract

PURPOSE:To prevent the chattering generated between the both planetary gears and a gear meshed with the planetary gears by dividing the planetary gear into the planetary gears on the meshed side with a sun gear and on the meshed side with an internal gear and connecting the both planetary gears by a flexible shaft. CONSTITUTION:When an input shaft 1 is revolution-driven, a sun gear 2 formed integrally with the input shaft 1 is revolution-driven, and a rotary driving power is transmitted to a planetary gear 11 on the input side meshed with the sun gear 2. Then, the planetary gear 11 on the input side is revolved reversely to the sun gear 2, and transmits the rotary driving power to a planetary gear 12 on the output side through a flexible shaft 16. Since the flexible shaft 16 is formed slender and long at this time, the revolution spring constant is made small, and the flexible shaft 16 is distorted properly in the revolution direction, and the reaction force due to the torsion is allowed to act onto the meshing surface between the planetary gear 11 on the input side and the sun gear 2, and to act onto the meshing surface between the planetary gear 12 on the output side and the internal gear 3 on the input side of an internal gear 15. Therefore, the meshed gear is always engaged in the revolution direction of the tooth flank.

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a planetary gear device that transmits the rotational driving force of an input shaft to an output shaft coaxially disposed at a variable speed. The present invention relates to a planetary gear device configured to prevent this.

[Prior Art] A planetary gear device is known as a device that transmits rotational driving force from an input shaft to an output shaft.

As shown in FIG. 3, the planetary gear device includes a sun gear 2 integrally fixed to the output end of an input shaft 1, and an input of an internal gear 15 having internal teeth 3.4 formed at both ends of the inner peripheral surface. side internal teeth 3
The planetary gear 5 that meshes with the sun gear 2 meshes with the input gear 7 that is integrally provided at the input end of the output shaft 6, and the planetary gear 5 meshes with the sun gear 2. 5 carrier shafts 9 are provided.

Therefore, the rotation of the input shaft 1 is transmitted from the sun gear 2 to the planetary gear 5, and from the planetary gear 5 to the input gear 7 of the output shaft 6 via the internal gear 15.

[Problems to be Solved by the Invention] The above-mentioned planetary gear device has a high torsional rigidity between the gears, and since it is impossible to adjust the torsional rigidity, the input end of the input shaft l and Elastic joint 10 between drive shafts
is set to prevent chattering.

However, the elastic joint 10 is expensive and is subject to manufacturing restrictions for those that intend to transmit large torques, so it has been desired to propose a planetary gear device that can prevent chatter without using an elastic joint.

[Ten Steps to Solve the Problems 1] This invention aims to solve the above problems, and provides a planetary gear device in which a sun gear and an internal gear are connected by a planet gear. The planetary gear is divided into an input side planetary gear that meshes with the internal gear and an output side planetary gear that meshes with the internal gear, and these are connected by a flexible shaft to form a planetary gear device.

[For example, when the sun gear is used as the input side of power transmission, the internal gear is used as the output, and the rotational driving force is transmitted from the sun gear to the planetary gear on the input side, the rotational driving force is transmitted via the deflection shaft. The rotational driving force is transmitted to the planetary gear on the output side, and the planetary gear on the output side transmits the rotational driving force to the internal gear. At this time, the flexible shaft is moderately twisted 11 in its four directions during transmission of the rotational driving force, and a reaction force due to the twist is applied to the planetary gears on the output side and the input side to prevent chatter link, Realizes the transmission of rotational driving force.

[Example] A preferred embodiment of the present invention will be described below with reference to the accompanying drawings.

Not shown in FIG. 1, 1 is an input shaft connected directly or indirectly to a power transmission system, and 6 is an output shaft.

A sun gear 2 rotatably housed in a cylindrical gauging 8 is integrally fixed to the output end of the input shaft 1, and the sun gear 2 has an input side gear connected to the input shaft at a constant interval in the circumferential direction. The planetary gear I1 is meshed.

A deflection shaft 16 extending parallel to the axial direction of the sun gear 2 toward the m side from the input measurement is integrally attached to the * star gear 11 of the input measurement, and the other end of the deflection shaft 16 is , is integrally connected to a power measuring planetary gear 12 rotatably supported by a bearing 13 in the casing 8. That is, in this embodiment, the planetary gear is divided into an output side and an input side, and both are connected by one flexible shaft 16 to form a top. The output measuring planetary gear 12 is meshed with the internal gear 15 housed in the goosing 8, so that the rotational driving force of the input gear 2 is transmitted to the internal gear 15.

In addition, in the embodiment, the inner IT wheel 15 has an input-side inner tooth 3 and an output-measurement inner tooth 4 formed on its inner circumferential surface with an interval of 1r in the axial direction. The output measuring planetary gear 12 is meshed with the teeth 3, and the input gear 7, which is integrally attached to the input end of the output shaft 6, is meshed with the internal teeth 4 on the output side to transmit power. be done.

Further, a carrier shaft 9 is integrally attached to each of the planetary gears 11 and 12, and each carrier III9 is rotatably supported by the casing 8.

Next, the action will be explained.

When the input shaft 1 is rotationally driven, the sun gear 2 integrated with the input shaft 1 is rotationally driven, and rotational driving force is transmitted to the planetary gear 11 on the input side meshed with the sun gear 2. The input planetary gear 11 is rotated in the opposite direction to the sun gear 2 and transmits rotational driving force to the output planetary gear 12 via the deflection shaft 16. At this time, the deflection axis 1
By making the deflection shaft 16 thin and long, the rotational spring constant becomes small, and the deflection shaft 16 twists appropriately in the direction of rotation, and the reaction force due to the twist is transferred to the planetary gear 11 on the input side. It acts on the meshing tooth surfaces of the sun gear 2, and also on the meshing tooth surfaces of the internal teeth 3 of the output-side planetary gear 12 and the input fltl of the internal gear 15.

As a result, the meshing tooth surfaces of each gear always engage with each other in the direction of rotation of the gear.

In addition, the reaction force due to the torsion of the deflection shaft 16 also acts between the output internal teeth 4 of the internal gear 15 and the tooth surfaces of the input gear 7 that meshes with them, so these meshing teeth also rotate. It is always engaged in the direction. Therefore, in the transmission of the rotational driving force, occurrence of chattering is prevented, the rotational driving force is transmitted quietly, and the output shaft 6 is rotationally driven with reduced rotation.

In this way, the natural frequency of vibration is adjusted by the rotational spring constant of the flexible shaft 16 to prevent chattering, and by appropriately twisting the flexible shaft 16, each of the six planetary gears 11, 12, the sun gear 2, and the inner The meshing with the gear 15 is improved, and the fitting of the south side can be improved.

By the way, the degree of twist of the flexible shaft 16 can be optimally set by appropriately selecting the shaft length and diameter of the flexible shaft 16. That is, the deflection axis 1
In order to make the torsional rigidity of the deflection shaft 16 smaller than the rigidity of the gears with which the M star gears 11 and 12 mesh, the torsional spring constant of the deflection shaft 16 is increased by increasing the shaft length and decreasing the shaft diameter. Optimal adjustment prevents chattering that occurs between gears, and in this state dynamic force can be transmitted smoothly.

FIG. 2 shows an embodiment in which the above-described planetary gear configuration is used to provide two systems of output measurement, normal rotation and reverse rotation (for example, a counter-rotating propeller). Components that are the same as those described above are given the same reference numerals.

As shown in the figure, the output shaft 6 and the input shaft 1 are formed as hollow shafts, and power is transmitted through the hollow portions 17 of the input shaft 1 and the output shaft 6 from input to output. A shaft 18 is rotatably provided via a bearing (not shown).

An assembly joint 19 that is integrally connected to the input shaft 1 through flanges is firmly housed in the power transmission shaft 18 .

With this configuration, rotation in the opposite direction to the direction of rotation transmitted from the input shaft 1 to the output shaft 6 can be directly extracted from the power transmission shaft 18.

Of course, it is also possible to provide the flexible shaft 16 with a key or spline fitting to the input side and output four planetary gears 11, 12.

[Effects of the Invention] As is clear from the above explanation, the present invention exhibits the following excellent effects.

In a planetary gear device in which a planetary gear is interposed between a sun gear and an internal gear, the L planetary gear is divided into a 111J planetary gear that meshes with the sun gear and a 111J planetary gear that meshes with the internal gear. Since these are connected by a flexible shaft, it is possible to prevent chattering between the gears meshing with both planetary gears.

4

[Brief explanation of drawings]

FIG. 1 is a sectional view showing a preferred embodiment of the present invention, FIG. 2 is a sectional view showing another embodiment, and FIG. 3 is a sectional view showing a conventional example. In the figure, 2 is a sun gear, 11 is an input measuring planetary gear, 12 is an output side planetary gear, 15 is an internal gear, and 16 is a deflection shaft.

Claims (1)

[Claims] 1. The sun gear (2) and internal gear (15) are connected to a planetary gear (
11, 12), in which the planetary gear is connected to an input-side planetary gear (11) that meshes with the sun gear (2) and an output-side planetary gear that meshes with the internal gear (15). A planetary gear device characterized by being divided into two parts and connected by a flexible shaft (16).