New Parallel Compound Movable Tooth Transmission Principle and Its Meshing Characteristics

doi:10.3969/j.issn.1004-132X.2025.11.006

Abstract

Abstract:

The transmission ratio of single-stage movable tooth transmissions was relatively low，while the series-connected movable tooth transmission structure was lack of compactness and inability to achieve power splitting transmission.Therefore， a novel parallel compound movable tooth transmission device was proposed， which comprised of a primary planetary gear transmission and a planar steel ball movable tooth transmission. The operating principles and structures of this device were introduced， along with the tooth number calculation method. The profile equations of the double-circular-arc tooth profiles were derived， and the analysis of the meshing characteristics was conducted. The results show that this innovative transmission device features a compact structure， enabling a high transmission ratio. By adjusting the number of teeth， the device achieves both forward and reverse output rotation， power splitting transmission， and “concave-convex” tooth contact. It exhibits high load-bearing capacity and is suitable for applications requiring large transmission ratios and high power density.

Key words: parallel compound movable tooth transmission, power splitting, tooth profile equation, contact analysis

摘要：

单级活齿传动的传动比较小，而串联式活齿传动结构不紧凑且无法实现功率分流传动，为此，提出一种由一级行星齿轮传动和一级平面钢球活齿传动构成的新型并联复式活齿传动装置。介绍了该装置的传动原理及结构，给出了配齿计算方法，推导了双圆弧活齿啮合副齿廓方程，对其啮合特性进行了分析。研究结果表明，该新型传动装置结构紧凑，可获得大传动比，能通过齿数调整实现正反向输出，实现了功率分流传动和“凹-凸”齿接触，具有较高的承载能力，可应用于有大传动比和高功率密度要求的场合。

关键词: 并联复式活齿传动, 功率分流, 齿廓方程, 接触分析

CLC Number:

TH122

Hengyi LEI, Xuesong DU, Zilong JIANG, Caichao ZHU. New Parallel Compound Movable Tooth Transmission Principle and Its Meshing Characteristics[J]. China Mechanical Engineering, 2025, 36(11): 2517-2524.

雷恒毅, 杜雪松, 江子龙, 朱才朝. 新型并联复式活齿传动原理及其啮合特性[J]. 中国机械工程, 2025, 36(11): 2517-2524.

Figures/Tables 11

Fig.1 Transmission principle of parallel compound movable teeth

Fig.2 Planar steel ball movable tooth transmission

Fig.3 The principle of tool path generation of center wheel movable tooth fixed plate

Fig.4 Tooth profile calculation coordinate system

Fig.5 Contact analysis of meshing pair

Tab.1 Prototype design parameters

参数	数值
总传动比	89.82
第一级传动比 $i 13 H$	-8.882
第二级传动比 $i J G K$	-9
太阳轮齿数Z₁	17
行星轮齿数Z₂	67
内齿圈齿数Z₃	151
活齿数Z_G	18
中心轮活齿定盘齿数Z_K	20
动盘刀具轨迹长半轴a/mm	85
动盘刀具轨迹短半轴b/mm	82
活齿半径r/mm	5
轨道圆弧半径R/mm	5.4
活齿材料Gr15弹性模量/GPa	207
活齿材料Gr15泊松比	0.3
齿轮、动盘、定盘、保持架材料40Cr弹性模量/GPa	206
齿轮、动盘、定盘、保持架材料40Cr泊松比	0.29

Tab.1 Prototype design parameters

参数	数值
总传动比	89.82
第一级传动比 $i 13 H$	-8.882
第二级传动比 $i J G K$	-9
太阳轮齿数Z₁	17
行星轮齿数Z₂	67
内齿圈齿数Z₃	151
活齿数Z_G	18
中心轮活齿定盘齿数Z_K	20
动盘刀具轨迹长半轴a/mm	85
动盘刀具轨迹短半轴b/mm	82
活齿半径r/mm	5
轨道圆弧半径R/mm	5.4
活齿材料Gr15弹性模量/GPa	207
活齿材料Gr15泊松比	0.3
齿轮、动盘、定盘、保持架材料40Cr弹性模量/GPa	206
齿轮、动盘、定盘、保持架材料40Cr泊松比	0.29

Fig.6 Kinematics analysis results

Fig.7 Analysis results of force and energy parameters

Fig.8 Finite element model

Fig.9 Contact state of movable tooth meshing pair

Fig.10 Contact pressure of movable teeth meshing pair

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