Abstract
Compared with traditional gear transmission, the multi-branch split-torsion gear transmission system has the advantages of large transmission power, small size and high reliability, so it is more and more used in high-speed heavy load occasions such as ships and aircraft. Since the transmission system of multi-branch split torsional gears belongs to over-constrained configuration, it is necessary to meet strict tooth matching condition in the design process in order to realize the correct synchronous meshing of each branch, which is of great significance to ensure its uniform installation and motion synchronization.Aiming at the coaxial six-branch twisted herringbone gear transmission system, this paper establishes a calculation method for the proper meshing conditions of each branch on the basis of considering the movement synchronization of each branch and preventing geometric interference.In addition, the calculation of gear allocation was carried out for a ship's power transmission system, and a parameter scheme that satisfies the requirements of transmission ratio, concentricity and synchronous meshing was obtained.The correctness of the calculation method of tooth matching in this paper is verified by three-dimensional modeling. This method has universal application value to the tooth matching design of other coaxial multi-branch gear transmissions.
Highlights
Compared with traditional gear transmission, the multi⁃branch split⁃torsion gear transmission system has the advantages of large transmission power, small size and high reliability, so it is more and more used in high⁃ speed heavy load occasions such as ships and aircraft
西北工业大学学报,2021,39 (2) : 341⁃349 LI Zhibin, WANG Sanmin, LI Fei, et al Research on matching conditions of coaxial six⁃branch split⁃torsion herringbone gear transmission system[ J]
Summary
设分支齿轮 41、51、52 和齿轮 51、41、6 之间位置 角分别为 θi( i = 1,2) ,则当 θ1 取最大和最小值时齿 轮几何极限分布如图 3 所示。 Oi( i = 41,51,52,6) 表 示齿轮 41、51、52,6 几何中心。 图 3 中,dia 和 di( i = 41,51,6) 分别表示齿轮 41、51、6 的齿顶圆直径和分 度圆直径。 由图 3 得齿轮 51 与齿轮 52 邻接条件 5i( i = 1,2,3,4,5,6) 旋转轴线。 如图 4 设 θi( i = 1, 3) 分别表示齿轮 41、51、52 和齿轮 6、51、52 之间的位 置角。 di( i = 41,51,6) 表示齿轮 41、51、6 的分度圆 直径,Oi( i = 41,51,52,6) 表示齿轮 41、51、52、和齿轮 6 几何中心。 由图 4 可得该分支满足
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