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A planetary gear transmission and planetary gear technology, applied in the field of gear transmission, can solve the problems of process condition limitation, increase design cost, transmission ratio requirements, etc., and achieve the effect of reducing volume and weight, avoiding waste, and improving full utilization rate.
Active Publication Date: 2010-11-24
NINGGUO JULONG IND
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[0006] In the actual planetary gear transmission design, it is often encountered that the above assembly conditions cannot be met due to transmission ratio requirements, reducer volume, process conditions, or the use of existing workpieces, that is, (Za+Zb) / n≠C, If the above conventional assembly conditions must be met, the design cost will increase; it is imperative to design a new assembly method without increasing the design cost
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example 1
[0029] Example 1, the number of teeth Z of the sun gear 1 is known a =19, the number of teeth of the internal gear 2 Z b =67, 3 planetary gears n=4, then (Z a +Z b ) / n=(19+67) / 4=21.5 is a non-integer, it can be designed according to the steps of realizing the unequal division of the circumference assembly method, calculated as follows:
[0030] θ ab =360° / (Z a +Z b )=360° / (19+67)=4.186047°;
[0031] Take 21.5=E+e=21+0.5, then E is 21, e is 0.5, and the angle between two adjacent planetary gears 3 is θ 大 It is 4.186047°×(21+1)=92.093023°, and the included angle θ between two adjacent planetary wheels 小 It is 4.186047°×21=87.906977°;
[0032] Assign the number n of large and small included angles 1 , n 2 :n 1 = e × n = 0.5 × 4 = 2, n 2 =(1-e)×n=(1-0.5)×4=2;
[0034] The angles between the above three planetary wheels are distributed in order, that is, θ 小 , θ 小 , θ 大 , θ 大 (Such...
example 2
[0036] Example 2, known sun gear 1 tooth number Z a =23, the number of teeth Z of internal gear 2 b =61, 3 planetary gears n=5, then (Z a +Z b ) / n=(23+61) / 5=16.8 is a non-integer;
[0037] Calculated: θ ab =360° / (Z a +Z b )=360° / (23+61)=4.285714°;
[0038] Take 16.8=E+e=16+0.8, then E is 16, e is 0.8, wherein the angle between two adjacent planetary gears 3 is θ 大 =4.285714°×(16+1)=72.857138°, and the angle θ between two adjacent planetary wheels 小 =4.285714°×16=68.571424°;
[0039] Assign the number n of large and small included angles 1 , n 2 :n 1 =e×n=0.8×5=4,n 2 =(1-e)×n=(1-0.8)×5=1;
[0041] The angles between the above three planetary wheels are distributed in order, that is, θ 大 , θ 大 , θ 大 , θ 大 , θ 小 .
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Abstract
The invention discloses an assembling method for planetary gear transmission, and relates to the technical field of gear transmission, in particular to planetary gear transmission. In the assembling method for the planetary gear transmission, when the sum of the tooth number of a sun gear and an internal gear divides the number of planetary gears to obtain a quotient which is not an integer, in the planetary gear transmission, the planetary gears are distributed at the preset positions by adopting a circumference non-equant assembling method, so that correct meshed operation of the planetary gears is guaranteed. The circumference non-equant assembling method comprises four steps, wherein big and small included angles on the circumference can be in sequential distribution or staggered distribution. Compared with the prior art, the assembling method for the planetary gear transmission solves the technical problems which 'machine design handbook' and common reference books cannot solve, develops and improves a machine design theory, reduces the volume and weight during the gear transmission, greatly improves the full utilization rate of materials and avoids the waste of material resources; and in addition, the assembling method has a simple and clear computational formula without changing the parameters and structure of the gears per se.
Description
technical field [0001] The invention relates to the technical field of gear transmission, in particular to the transmission of planetary gears. Background technique [0002] Involute planetary gear transmission, represented by the single-row 2K-H (NGW) type, the number of teeth and the number of planetary gears, in addition to meeting the conditions of transmission ratio, concentricity and adjacency, must also meet the assembly conditions to ensure that each planet The wheels are installed evenly between the two central gears (that is, the sun gear and the inner gear), otherwise when the first planetary gear is installed in the meshing position, the other planetary gears cannot be installed. [0003] On pages 17-10 and 17-11 of Volume 3 of the 3rd edition of "Machine Design Manual" published by Machinery Industry Press in August 2004: [0004] The assembly condition of the single-row 2K-H planetary transmission is: the sum of the teeth of the two center gears should be an i...
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