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Research Papers: Design of Direct Contact Systems

A Study on the Design and Performance of Epicycloid Bevels of Pure-Rolling Contact

[+] Author and Article Information
Rulong Tan

The State Key Laboratory of
Mechanical Transmission,
Chongqing University,
Chongqing 400044, China;
College of Electrical Engineering,
Chongqing University,
Chongqing 400044, China

Bingkui Chen, Dong Liang

The State Key Laboratory of
Mechanical Transmission,
Chongqing University,
Chongqing 400044, China

Dongyun Xiang

Changan Automobile (Group) Co. Ltd,
Chongqing 401120, China

1Corresponding author.

Contributed by the Power Transmission and Gearing Committee of ASME for publication in the JOURNAL OF MECHANICAL DESIGN. Manuscript received October 7, 2017; final manuscript received December 8, 2017; published online February 27, 2018. Assoc. Editor: Hai Xu.

J. Mech. Des 140(4), 043301 (Feb 27, 2018) (11 pages) Paper No: MD-17-1674; doi: 10.1115/1.4039008 History: Received October 07, 2017; Revised December 08, 2017

To avoid the negative influence of sliding contact, this paper tries to investigate the spiral bevels of pure-rolling contact that can be manufactured by existing manufacture technology. In this process, spatial conjugate curve meshing theory and conjugate surface theory are both introduced to investigate the geometric principles and face hobbing process of the pure-rolling contact epicycloid bevel (PCEB for short in this paper). The tooth surface models of PCEBs by face hobbing process are obtained. Next, a sample is represented to show an application of this model. Then, finite element analysis (FEA) is applied to investigate the contact mechanics characteristics of these gears. Finally, the performance experiment of a prototype is completed to evaluate the deviations between theoretical expectations and practical results. From the FEA and experimental results, it is concluded that the PCEBs can mesh correctly and achieve a higher transmission efficiency.

Copyright © 2018 by ASME
Topics: Gears , Design
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References

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Figures

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Fig. 5

Location of the point, P

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Fig. 7

Schematic of the blade

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Fig. 6

Diagram of the spatial curves Γg, Γ1, and Γ2

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Fig. 4

Applied coordinate systems in face hobbing process

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Fig. 3

Schematic of coordinate systems and components in face hobbing

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Fig. 2

Coordinate systems in the meshing process of the pinion and gear

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Fig. 1

Schematic of continuous indexing motion

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Fig. 19

Prototype gearbox

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Fig. 20

Principle scheme of the test system

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Fig. 21

Testing rig: 1—driving motor, 2—torque and rotational speed transducer 1, 3—prototype gearbox, 4—torque and rotational speed transducer 2, 5—gear reducer, and 6—loading motor

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Fig. 15

Maximum contact stresses of the middle teeth of the pinion and gear

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Fig. 16

The deviation distance between theoretical and real locations with maximum contact pressure

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Fig. 17

Theoretical and real contact paths on the pinion tooth

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Fig. 18

Slip ratios at real locations with maximum contact pressure

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Fig. 8

Blades with single-arc profiles

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Fig. 9

Blades with double-arc profiles

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Fig. 10

Relationships of generating tooth surfaces and manufactured tooth surfaces

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Fig. 11

Assemble model of the manufactured pinion and gear

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Fig. 12

Assemble model of the generating crown gear and manufactured pinion

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Fig. 13

Schematic of finite element model

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Fig. 14

Stress distribution of the pinion in the mesh cycle

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Fig. 23

Transmission efficiency of the prototype gearbox

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Fig. 24

Transmission efficiency of the original gearbox

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Fig. 22

Contact areas under light loads

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Fig. 25

Oil temperature variations of the prototype gearbox

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Fig. 26

Oil temperature variations of the original gearbox

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