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Research Papers: Applications

Effects of Contact Ratio on Transmission Errors of Trochoidal Gears

[+] Author and Article Information
Hiroyuki Ohta

Department of Mechanical Engineering,
Nagaoka University of Technology,
1603-1 Kamitomioka, Nagaoka,
Niigata 940-2188, Japan
e-mail: ohta@mech.nagaokaut.ac.jp

Masahumi Kurita

Department of Mechanical Engineering,
Graduate School,
Nagaoka University of Technology,
1603-1 Kamitomioka, Nagaoka,
Niigata 940-2188, Japan

Kengo Kishi

Engineering Department,
Kamo Seiko Corporation,
1166 Kamewari, Matsuki,
Toyota, Aichi 470-0424, Japan

For descriptive purposes, it was assumed that er = ec in this calculation.

In this calculation, it was assumed that er = ec = eru = ecu = erl = ecl.

For descriptive purposes, the measured TEP-P of the type C gear was plotted by setting er + ec equal to erl + ecl.

Contributed by the Tribology Division of ASME for publication in the JOURNAL OF TRIBOLOGY. Manuscript received July 14, 2013; final manuscript received February 20, 2014; published online April 1, 2014. Assoc. Editor: Mihai Arghir.

J. Tribol 136(3), 031101 (Apr 01, 2014) (10 pages) Paper No: TRIB-13-1137; doi: 10.1115/1.4027130 History: Received July 14, 2013; Revised February 20, 2014

This article deals with the effects of the contact ratio ε on transmission errors of trochoidal gears (which consist of a roller gear anda cam gear). First, the experiments and multibody analysis (MBA) for the transmission errors of two types of single-row trochoidal gears (types A and B gears) were carried out. The type A gear is a commercial trochoidal gear with ε = 1.1 and the type B gear is a trochoidal gear with ε = 2.1 (by increasing the number of teeth). The experimental and MBA results showed that the peak-to-peak value TEP-P of the transmission errors of the type B gear (with ε = 2.1) was lower than the type A gear (with ε = 1.1). The TEP-P of types A and B gears increased as the rotational speed of the roller gear increased. However, the increasing rate of the measured TEP-P of the type B gear due to an increase of the rotational speed was less than that of the type A gear. Increasing the contact ratio due to an increase in the number of teeth in a single-row trochoidal gear (such as a type B gear) decreases the strength of the teeth and rollers. To overcome this problem, as a new transmission error reduction method, a double-row trochoidal gear (type C gear), having two times the contact ratio of the type A single-row trochoidal gear was presented and its transmission error was examined. The experimental and MBA results showed that the TEP-P of the transmission errors of the type C double-row trochoidal gear were lower than that of the type A single-row trochoidal gear. Therefore, it is clear that using a double-row trochoidal gear is effective for reducing the transmission errors of trochoidal gears.

Copyright © 2014 by ASME
Topics: Gears , Errors
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References

Figures

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Fig. 4

Initial positions of the geometric and rotation centers of a single-row trochoidal gear (Type A)

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Fig. 2

Amplitude and phase of eccentricity in a single-row trochoidal gear (Type A)

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Fig. 1

Single-row trochoidal gear

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Fig. 5

Measured transmission error waveforms of single-row trochoidal gears (Nr = 60 rpm)

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Fig. 6

Effects of the rotational speed and contact ratio on TE

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Fig. 7

Measured transmission error spectra of single-row trochoidal gears (Nr = 60 rpm)

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Fig. 9

Friction characteristics in the revolute joint of the rollers

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Fig. 11

Calculated transmission error waveform of single-row trochoidal gears (Nr = 60 rpm, c = 1 Ns/mm)

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Fig. 12

Calculated transmission error spectra of single-row trochoidal gears (Nr = 60 rpm, c = 1 Ns/mm)

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Fig. 13

Effects of the rotational speed, contact ratio, and viscous damping coefficient on TEP-P of single-row trochoidal gears

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Fig. 14

Effects of eccentricity and contact ratio on TEP-P (Nr = 60 rpm)

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Fig. 8

MBA model of a single-row trochoidal gear (Type A)

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Fig. 15

A double-row trochoidal gear (Type C)

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Fig. 10

Friction characteristics between the rollers and cam gear

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Fig. 16

Initial positions of the geometric and rotation centers of a double-row trochoidal gear (Type C)

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Fig. 17

Measured transmission error waveform of a double-row trochoidal gear (Type C, Nr = 60 rpm)

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Fig. 18

Measured transmission error spectrum of the double-row trochoidal gear (Type C, Nr = 60 rpm)

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Fig. 19

MBA model of a double-row trochoidal gear (Type C)

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Fig. 20

Calculated transmission error waveform of a double-row trochoidal gear (Type C, Nr = 60 rpm, c = 1 Ns/mm)

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Fig. 21

Calculated transmission error spectrum of a double-row trochoidal gear (Type C, Nr = 60 rpm, c = 1 Ns/mm)

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