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Research Papers: Design of Direct Contact Systems

Parametric Instability of Face-Gear Drives Meshing With Multiple Spur Pinions

[+] Author and Article Information
Meng Peng

Department of Mechanical,
Aerospace and Biomedical Engineering,
University of Tennessee,
Knoxville, TN 37996
e-mail: mpeng1@vols.utk.edu

Hans A. DeSmidt

Associate Professor
Department of Mechanical, Aerospace
and Biomedical Engineering,
University of Tennessee,
Knoxville, TN 37996
e-mail: hdesmidt@utk.edu

Jie Zhao

Department of Mechanical,
Aerospace and Biomedical Engineering,
University of Tennessee,
Knoxville, TN 37996
e-mail: jzhao11@vols.utk.edu

1Corresponding author.

Contributed by the Power Transmission and Gearing Committee of ASME for publication in the JOURNAL OF MECHANICAL DESIGN. Manuscript received January 29, 2015; final manuscript received August 17, 2015; published online October 15, 2015. Assoc. Editor: Hai Xu.

J. Mech. Des 137(12), 123301 (Oct 15, 2015) (9 pages) Paper No: MD-15-1051; doi: 10.1115/1.4031442 History: Received January 29, 2015; Revised August 17, 2015

This paper studies the dynamic behaviors for face-gear drives meshing with multiple spur pinions by using the model of a spinning disk with time-varying mesh loads that result from the unique face-gear meshing kinematics and nonunity contact-ratio. The system stability is assessed with respect to intersecting pinion shaft angles and pinion gear properties. The results provide information about parametric instability for dynamic-based design of multipinion/face-gear drives. This investigation also provides stabilization methods for pre-installed systems via gear radii and tooth numbers for a given intersecting pinion shaft angle.

Copyright © 2015 by ASME
Topics: Stability , Gears , Design
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References

Figures

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Fig. 6

Angular separation of two pinions on the same face-gear

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Fig. 5

Radial and circumferential positions of contact points and contact centroid

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Fig. 4

Contact centroid, for 1 < cr < 2

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Fig. 3

Illustration of effective radial and circumferential location of mesh contact points, and phase lags between different meshing tooth pairs

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Fig. 2

Face-gear tooth geometry with midpoint of contact lines (symbol “x”)

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Fig. 1

Sketch of dual pinion face-gear drive

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Fig. 7

Dimensionless phase difference versus total separation angle for N2 = 52

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Fig. 8

Multipinion/face-gear drive structural dynamics model: spinning elastic disk with lumped mass/spring/damper units acting at prescribed locations

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Fig. 10

Dual pinion/face-gear drive stability with respect to pinion discrete positioning angle and operating speed: N1 = 31, N2 = 155, h = 0.07 a, τ = 1, μ = 0.25, and ζ = 1 × 10−5 s, with θp = 0 deg

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Fig. 11

Dual pinion/face-gear drive stability with respect to nondimensional phasing angle and operating speed for three different values of θs with N1 = 31, N2 = 155, h = 0.07 a, τ = 1, μ = 0.25, and ζ = 1 × 10−5 s: (a) θs = 90.6 deg, ΔN2 = 39, (b) θs = 118.5 deg, ΔN2 = 51, and (c) θs = 181.2 deg, ΔN2 = 78

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Fig. 9

Dual pinion/face-gear drive stability with respect to pinion separation angle and operating speed: (a) N1 = 26, N2 = 130, h = 0.05 a, τ = 0.8, μ = 1.5, and ζ = 1 × 10 − 6 s and (b) N1 = 31, N2 = 155, h = 0.07 a, τ = 1, μ = 0.25, and ζ = 1 × 10−5 s

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Fig. 12

Dual pinion/face-gear drive stability with respect to nondimensional pinion mass with N1 = 31, N2 = 155, h = 0.07 a, μ = 0.25, ζ = 1 × 10−5 s, and θc = 120 deg

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Fig. 13

Dual pinion/face-gear drive stability with respect to bearing damping with N1 = 31, N2 = 155, h = 0.07 a, τ = 1, μ = 0.25, and θc = 120 deg

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Fig. 14

Dual pinion/face-gear drive stability with respect to nondimensional pinion bearing stiffness with N1 = 31, N2 = 155, h = 0.07 a, ζ = 1 × 10−5 s, and θc = 120 deg: (a) τ = 1 and (b) τ = 0.4

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Fig. 15

Dual pinion/face-gear drive stability as a function of the number of pinion gear teeth for gear ratio m12 = 5 for three different pinion separation angles cases with h = 0.07 a, τ = 1, μ = 0.25, ζ = 1 × 10−5 s: (a) θc = 90 deg, (b) θc = 120 deg, and (c) θc = 180 deg

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