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Research Papers

Multiphysics Investigations on the Dynamics of Differential Hypoid Gears

[+] Author and Article Information
M. Mohammadpour, H. Rahnejat

Wolfson School of Mechanical &
Manufacturing Engineering,
Loughborough University,
Loughborough LE113TU, UK

S. Theodossiades

Wolfson School of Mechanical &
Manufacturing Engineering,
Loughborough University,
Loughborough LE113TU, UK
e-mail: s.theodossiades@lboro.ac.uk

1Corresponding author.

Contributed by the Design Engineering Division of ASME for publication in the JOURNAL OF VIBRATION AND ACOUSTICS. Manuscript received December 5, 2013; final manuscript received April 3, 2014; published online April 30, 2014. Assoc. Editor: Philippe Velex.

J. Vib. Acoust 136(4), 041007 (Apr 30, 2014) (3 pages) Paper No: VIB-13-1420; doi: 10.1115/1.4027403 History: Received May 12, 2013

Vehicular differential hypoid gears play an important role on the noise, vibration, and harshness (NVH) signature of the drivetrain system. Additionally, the generated friction between their mating teeth flanks under varying load-speed conditions is a source of power loss in a drivetrain while absorbing some of the vibration energy. This paper deals with the coupling between system dynamics and analytical tribology in multiphysics, multiscale analysis. Elastohydrodynamic lubrication (EHL) of elliptical point contact of partially conforming hypoid gear teeth pairs with non-Newtonian thermal shear of a thin lubricant film is considered, including boundary friction as the result of asperity interactions on the contiguous surfaces. Tooth contact analysis (TCA) has been used to obtain the input data required for such an analysis. The dynamic behavior and frictional losses of a differential hypoid gear pair under realistic operating conditions are therefore determined. The detailed analysis shows a strong link between NVH refinement and transmission efficiency, a finding not hitherto reported in literature.

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References

Figures

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Fig. 1

(a) The multibody dynamics model and (b) the corresponding free body diagrams

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Fig. 2

Frequency spectra of the maximum and minimum DTE amplitudes (nominal case)

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Fig. 3

One meshing cycle (time period = 0.005 s) of the DTE variation of section A-A (Fig. 2)

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Fig. 4

Magnified views of the first and the second resonance regions of Fig. 2

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Fig. 5

Frequency spectra of the maximum and minimum DTE amplitudes (low damping)

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Fig. 6

Frequency spectra of the maximum and minimum DTE amplitudes (high bearing stiffness)

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Fig. 7

Frequency spectra of the maximum and minimum DTE amplitudes (torsional model)

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Fig. 8

Frequency spectra of the lateral motion maximum and minimum amplitudes (nominal case)

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Fig. 9

Frequency spectra of the axial motion maximum and minimum amplitudes (nominal case)

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Fig. 10

Frequency spectra of the maximum and minimum radial transmitted force amplitudes

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Fig. 11

Frequency spectra of the maximum and minimum axial transmitted force amplitudes

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Fig. 12

Frequency spectra of the maximum and minimum pinion friction torque

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Fig. 13

One meshing cycle of the friction torque variation (position A in Fig. 12)

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Fig. 14

One meshing cycle of the friction torque variation (position B in Fig. 12)

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Fig. 15

Input pinion torque for the considered case study

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