CN2183471Y - Less tooth-differance epicyclic gear driving mechanism - Google Patents
Less tooth-differance epicyclic gear driving mechanism Download PDFInfo
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- CN2183471Y CN2183471Y CN 93244799 CN93244799U CN2183471Y CN 2183471 Y CN2183471 Y CN 2183471Y CN 93244799 CN93244799 CN 93244799 CN 93244799 U CN93244799 U CN 93244799U CN 2183471 Y CN2183471 Y CN 2183471Y
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- gear
- driving mechanism
- internal gear
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- centering
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Abstract
The utility model provides a less tooth-difference epicyclic gear driving mechanism which is mainly composed of a centering annular gear, a planetary frame, a planetary wheel and a non-centering annular gear, wherein, the planetary wheel is a wide gear whose left and right are separately engaged with two annular gears. Compared with an existing NN model mechanism, the utility model has the advantages of simple structure, easy processing and installation, easy gain of higher precision, low fabrication cost, higher bearing capacity, good transmission quality, etc., being specially suitable for making a speed reducing mechanism with large speed ratio.
Description
The utility model belongs to a kind of improved gear drive, and particularly a kind of novel small teeth number difference planet gear driving mechanism is suitable for making the reducing gear of big retarding ratio.
The engineers and technicians that are engaged in mechanical major work know a kind of input mechanism is arranged for few tooth differential, output mechanism are the gearing mechanism of zero tooth differential in the small teeth number difference planet gear gearing, also claim NN type mechanism.This motion of mechanism reason as shown in Figure 1, mainly by centering internal gear 1, planet carrier 2, first planet wheel 3, second planet wheel 4, form to gear 5, bearing 6 and bearing 7 in aroused in interest, the number of teeth difference of centering internal gear 1 and first planet wheel 3 is that few tooth of 1 is poor, and the number of teeth difference of the aroused in interest internal gear 4 and second planetary pinion 4 is zero.This mechanism can be easy to obtain higher precision with standard cutter processing on general purpose machine tool, and with the gear transmission mode output power, thereby overcome unsteady disc type, pin axle type, slide block type and double crank type output mechanism exist processing with installation precision height, shortcoming such as fretting wear is big, transmission efficiency is low, cost is high and the life-span is short, thereby make the small teeth number difference planet gear driving mechanism be able to popularization and application as retarder.Yet, also there is the following deficiency in this driving mechanism: in order to realize the constant speed eccentric gearing, the throw of eccentric of zero tooth differential output mechanism must equate with the throw of eccentric of previous small teeth number difference planet gear driving mechanism, therefore, in the design alternative of modification coefficient, all much more difficult in the manufacturing of gear and the technical requirements than common modified gear.In addition, because internally external gear carries out radially and tangent modification, thereby make the topping of gear, in order to guarantee addendum thickness, usually before this modulus to gear being got-and the twice of N type organization gear modulus, and the number of teeth is taken as 0.5 times, like this must be with two cuttves when its internal gear of processing, increase machining error, reduced transmission quality.In the error of the caused teeth directional of planet wheel that the bigeminy tooth is installed, also can reduce transmission quality to axis.
The purpose of this utility model is to overcome the existing deficiency of small teeth number difference planet gear driving mechanism that above-mentioned zero tooth differential is made output mechanism, provide a kind of simple in structure, be convenient to process, transmission quality reaches the high a kind of novel small teeth number difference planet gear driving mechanism of bearing capacity well.
Above-mentioned task is achieved in that as shown in Figure 2, this mechanism includes centering internal gear 1, planet carrier 2, aroused in interest internal gear 5 and bearing 6 and bearing 7 but has done following improvement, establish a planet wheel 82 of planet carriers, mesh with centering internal gear 1 and aroused in interest internal gear 5 respectively about planet wheel 8, planet wheel 8 is few tooth differential driving mechanism with the transmission of centering internal gear 1 and centering gear 5.
Fig. 1 is the schematic representation of existing NN type mechanism.
Fig. 2 is the utility model structural representation.
Can try to achieve the velocity ratio of this mechanism according to fixed shaft gear train:
ixa＝ (Za)/(Za-Zb)
In the formula: ixa is a velocity ratio.
Za is the number of teeth of aroused in interest internal gear 5.
Zb is the number of teeth of centering gear 1.
Input is rotated in the same way with output when Za＞Zb, reverse rotation when Za＜Zb.
From the velocity ratio formula as can be known, this Speed Ratio is only relevant with two internal gear numbers of teeth, and these two internal gears are not meshing with each other, and this just makes things convenient for manyly than existing few tooth difference transmission mechanism in the selection of number of teeth difference.In addition, this mechanism also has following characteristics: first zero teeth difference type output mechanism only plays output action, and this mechanism had both participated in realizing the motion of a certain velocity ratio, has played the effect of output movement again; It two is that NN type mechanism is four gear transmissions of two moduluses, and this mechanism is three gear transmissions of a modulus, only with one cutter is got final product when adding work gear; It three is that planet wheel B is not the bigeminy tooth, does not have the difficulty of processing and installation aspect, thereby improves transmission quality easily; It four is that NN type number of teeth difference generally only is one, and this mechanism can reach three to five, so the working pressure angle of this organization gear transmission is littler than NN type mechanism, and bearing capacity is just than NN type mechanism height.In sum, the utlity model has simple in structure, part is few, processing and easy for installation, be easy to obtain higher precision, advantage such as cost is low, bearing capacity is high and transmission quality is good.
This mechanism is suitable for making the reducing gear of big retarding ratio.
Claims (1)
1, a kind of novel small teeth number difference planet gear driving mechanism, include centering internal gear 1, planet carrier 2, aroused in interest internal gear 5 and bearing 6 and bearing 7, it is characterized in that having only a planet wheel 8 to be arranged on the planet carrier 2, mesh with centering internal gear 1 and aroused in interest internal gear 5 respectively about planet wheel 8, planet wheel 8 is few tooth differential driving mechanism with the transmission of centering internal gear 1 and aroused in interest internal gear 5.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 93244799 CN2183471Y (en) | 1993-11-15 | 1993-11-15 | Less tooth-differance epicyclic gear driving mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 93244799 CN2183471Y (en) | 1993-11-15 | 1993-11-15 | Less tooth-differance epicyclic gear driving mechanism |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2183471Y true CN2183471Y (en) | 1994-11-23 |
Family
ID=33817923
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 93244799 Expired - Fee Related CN2183471Y (en) | 1993-11-15 | 1993-11-15 | Less tooth-differance epicyclic gear driving mechanism |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2183471Y (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107687500A (en) * | 2017-08-08 | 2018-02-13 | 胡黄龙 | Envelope gear drive |
-
1993
- 1993-11-15 CN CN 93244799 patent/CN2183471Y/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107687500A (en) * | 2017-08-08 | 2018-02-13 | 胡黄龙 | Envelope gear drive |
| CN107687500B (en) * | 2017-08-08 | 2020-12-08 | 胡黄龙 | Envelope gear transmission device |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C19 | Lapse of patent right due to non-payment of the annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |