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Design method and manufacturing method of multi-linkage planetary gear speed change mechanism and gear speed change mechanism

A transmission mechanism and planetary gear technology, which is applied in the design of multiple planetary gear transmission mechanisms and in the field of gear transmission mechanisms, can solve the problems of difficulty in designing gear ratios, increasing manufacturing costs, difficulty in maintenance, and inability to design speed ratios, etc., to achieve The effect of reducing manufacturing cost and difficulty of maintenance

Active Publication Date: 2022-03-25
王国富
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  • Summary
  • Abstract
  • Description
  • Claims
  • Application Information

AI Technical Summary

Problems solved by technology

Among them, for the NGW planetary gear transmission mechanism, adjust the number of planetary gear teeth Z g , sun gear teeth number Z a , Number of ring gear teeth Z b All conditions can be met, but due to physical size constraints and economic requirements, the speed ratio is below 10, while for other types of multi-planetary gear transmission design, due to assembly conditions Due to the limited design conditions and many design variable relationships, many required speed ratios cannot be designed, and the practicability is limited. Moreover, this assembly condition can only be used for double-linked planetary gear transmission mechanisms. It is more difficult to design such gears with many gears and the gear ratio needs to change linearly. At the same time, the transmission design becomes more complicated, which increases the manufacturing cost and the difficulty of maintenance.
[0003] For manufacturing do not have to meet Conditional multi-connected planetary gear transmission mechanism, the existing method is to assemble two sets of planetary gears, sun gears and ring gears designed according to the transmission principle of the NGW type planetary gear transmission mechanism, and then fix the two sets of planetary gears into a It is used to realize the dual planetary gear transmission mechanism as a whole, but it depends on assembling the teeth, because the sun gear, the planetary gear and the ring gear all have inevitable meshing gaps between the teeth, and there is no accurate calculation of the positioning of the assembly, and the meshing error is very large. Large, basically unusable, this method can not be used for multi-connected planetary gear transmission mechanism, and in order to achieve the speed ratio, the tooth shape displacement of planetary gear, sun gear, and ring gear is used to manufacture it, which does not meet the requirements. Conditional multi-planetary gear transmission mechanism is typically the same as the patent "201780034752.1" applied by the National University of Yokohama, Japan. However, such a design variable relationship is particularly large, the design calculation is complicated, and because the displacement coefficient cannot be too large, it is limited Given the designable range of gear ratios, it is very difficult to design double gears with limited gear ratios, and it is even more impossible to design multiple planetary gear transmission mechanisms with a wide range of gear ratios.

Method used

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  • Design method and manufacturing method of multi-linkage planetary gear speed change mechanism and gear speed change mechanism
  • Design method and manufacturing method of multi-linkage planetary gear speed change mechanism and gear speed change mechanism
  • Design method and manufacturing method of multi-linkage planetary gear speed change mechanism and gear speed change mechanism

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Embodiment 1

[0032] for figure 1 In the multi-connected planetary gear transmission mechanism shown in , we use multiple coaxial planetary gears g as a group, and the tooth-aligning mechanism on the same radial plane and multiple planetary gears g form a group, in which the tooth-aligning mechanism is a ring gear b or sun gear a, and each planetary gear set aligns teeth with the gear-aligning mechanism on the planet carrier H, assuming that the multi-connected planetary gear transmission mechanism has N links in total, and the planetary gears in each set of planetary gear sets are gn, n is the sequence of each planetary gear, n=1, 2, 3,... N, each ring gear is by, y is the sequence of each ring gear, y=1, 2, 3...N, each The joint sun gear is ax, and x is the joint sequence of each joint sun gear, and x=1, 2, 3...N.

[0033] When we follow the design principle of the NGW planetary gear mechanism to figure 1 When designing the multi-connected planetary gear transmission mechanism, the sun ...

Embodiment 2

[0058] In the first embodiment, we use the ring gear as the tooth alignment mechanism, and design and calculate according to the tooth alignment between the planetary gear set and the ring gear. The design calculation of the sun gear pair teeth is the same as in Embodiment 1.

[0059] Specifically, the formula for calculating the tooth difference angle position of each planetary gear in each planetary gear set relative to the reference line position is: In the formula, M is the number of planetary gear sets, m is the group sequence of each planetary gear set in the counterclockwise direction, m=1, 2, 3...M, Z gn is the number of teeth of each planetary gear in the multiple planetary gear transmission mechanism, Z ax is the number of teeth of the sun gear connected with the planetary gear, and the integer number of teeth is Integer bits in , is the tooth difference angle of each planetary gear in each planetary gear set relative to the reference line position.

[0060]...

Embodiment 3

[0074] According to the design method and principle in Embodiment 1 and Embodiment 2, this embodiment also provides a manufacturing method of a multiple planetary gear transmission mechanism, including the following steps:

[0075] 1. Process and assemble each planetary gear set according to the reference line position and tooth difference angle position.

[0076] 2. On the planet carrier, assemble each planetary gear set and the tooth alignment mechanism sequentially according to the group sequence.

[0077] When processing and assembling each planetary gear set, after determining the base line position of the planetary gear set, then determine the tooth difference angle position of each planetary gear with the base line position, that is, find the tooth valley center closest to the base line position, Finally, the center of the tooth valley that can be found is the starting position of the tooth processing of each planetary gear to process and assemble the planetary gear set...

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Abstract

The invention relates to a design method and a manufacturing method of a multi-connection planetary gear speed change mechanism and a gear speed change mechanism, teeth of a planetary gear set are designed in a specific calculation mode, the planetary gear set is positioned and assembled in combination with different machining modes, the limitation of assembly conditions of the multi-connection planetary gear speed change mechanism is broken through, and the assembly efficiency of the multi-connection planetary gear speed change mechanism is improved. The assembled and manufactured multi-connection planetary gear speed change mechanism can obtain different speed ratios according to different transmission requirements, and application of the multi-connection planetary gear speed change mechanism is expanded.

Description

technical field [0001] The invention relates to the technical field of mechanical engineering, in particular to a design method and a manufacturing method of a multi-connected planetary gear transmission mechanism and the gear transmission mechanism. Background technique [0002] Planetary gear transmission is an important part of the transmission method in the field of mechanical engineering technology, because planetary gear transmission has the advantages of small mass, small volume, large load capacity, and high transmission efficiency, and is widely used in various mechanical equipment. In order to meet the needs of use, on the basis of the original NGW, NN, NW, WW, NGWN and other planetary gear transmissions, Lavina, Simpson and other planetary gear mechanisms have been developed. When designing these mechanisms, the transmission must be satisfied. The four conditions are ratio, adjacency, concentricity and assembly. Among them, for the NGW planetary gear transmission...

Claims

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Application Information

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IPC IPC(8): F16H3/44F16H57/00G06F30/17G06F30/20G06F111/10G06F119/14
CPCF16H3/44F16H57/00G06F30/17G06F30/20F16H2057/0087G06F2111/10G06F2119/14
Inventor 王国富
Owner 王国富