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Design Optimization Study of a Nonlinear Energy Absorber for Internal Combustion Engine Pistons

[+] Author and Article Information
N. Dolatabadi, S. Theodossiades, S. J. Rothberg

Wolfson School of Mechanical, Electrical and
Manufacturing Engineering,
Loughborough University,
Leicestershire LE11 3TU, UK

Contributed by the Design Engineering Division of ASME for publication in the JOURNAL OF COMPUTATIONAL AND NONLINEAR DYNAMICS. Manuscript received July 31, 2017; final manuscript received May 3, 2018; published online July 26, 2018. Assoc. Editor: Tamas Kalmar-Nagy.

J. Comput. Nonlinear Dynam 13(9), 090910 (Jul 26, 2018) (12 pages) Paper No: CND-17-1339; doi: 10.1115/1.4040239 History: Received July 31, 2017; Revised May 03, 2018

Piston impacts against the cylinder liner are the most significant sources of mechanical noise in internal combustion (IC) engines. Traditionally, the severity of impacts is reduced through the modification of physical and geometrical characteristics of components in the piston assembly. These methods effectively reduce power losses at certain engine operating conditions. Frictional losses and piston impact noise are inversely proportional. Hence, the reduction in power loss leads to louder piston impact noise. An alternative method that is robust to fluctuations in the engine operating conditions is anticipated to improve the engine's noise, vibration and harshness (NVH) performance, while exacerbation in power loss remains within the limits of conventional methods. The concept of targeted energy transfer (TET) through the use of nonlinear energy sink (NES) is relatively new and its application in automotive powertrains has not been demonstrated yet. In this paper, a TET device is conceptually designed and optimized through a series of parametric studies. The dynamic response and power loss of a piston model equipped with this nonlinear energy sink is investigated. Numerical studies have shown a potential in reducing the severity of impact dynamics by controlling the piston's secondary motion.

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Figures

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Fig. 1

Piston assembly parameters and free body diagram

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Fig. 2

Fast Fourier transform spectra of piston's secondary motions at 3000 rpm: translation (ep) and rotation about the piston pin (β)

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Fig. 3

Pendulum NES coupled with the piston assembly

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Fig. 4

Free body diagram of the pendulum NES (external excitations and inertial forces)

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Fig. 5

Impact severity objective function variation with damping coefficient ct and stiffness coefficient kt (ε=7.5%)

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Fig. 6

Impact severity objective function variation with damping coefficient ct and stiffness coefficient kt (ε=12.5%)

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Fig. 7

Impact severity objective function variation with damping coefficient ct and stiffness coefficient kt (ε=20%)

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Fig. 8

Number of impacts objective function variation with damping coefficient ct and stiffness coefficient kt (ε=7.5%)

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Fig. 9

Number of impacts objective function variation with damping coefficient ct and stiffness coefficient kt (ε=12.5%)

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Fig. 10

Transferred energy objective function variation with damping coefficient ct and stiffness coefficient kt (ε=12.5%)

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Fig. 11

Eccentricity acceleration variation with damping coefficient for (a) 7.5% and (b) 12.5% NES mass ratios (maximum (mx) and minimum(mn) values at the piston top (et) and bottom (eb) lands)

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Fig. 12

Number of impacts variation with damping coefficient for (a) 7.5% and (b) 12.5% NES mass ratios at the top et and bottom (eb) of the piston skirt

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Fig. 13

Transferred energy variation with damping coefficient at (a) 7.5% and (b) 12.5% NES mass ratio (at TS and ATS of the cylinder liner)

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Fig. 14

Comparison of performance improvement for different objective functions and NES design specifications

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Fig. 15

Eccentricity displacements for three engine cycles (2DOF model (solid line) versus 3DOF model (dashed line))

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Fig. 16

Eccentricity accelerations for three engine cycles (2DOF model (solid line) versus 3DOF model (dashed line))

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Fig. 17

Power loss variations for the primary system (2DOF model) and piston equipped with 12.5% mass ratio NES (3DOF model)

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Fig. 18

Power loss variations for the primary system (2DOF model) and piston equipped with 20% mass ratio NES (3DOF model)

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Fig. 19

Power loss increase with respect to the primary system (without NES)

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Fig. 20

Frequency-energy plot of grounded pendulum and energy-wavelet cloud of the piston equipped with NES (3500 rpm and ε=12.5%)

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