Research Papers

Mechanical and Acoustic Performance of Sandwich Panels With Hybrid Cellular Cores

[+] Author and Article Information
Qing Li

State Key Laboratory of Ocean Engineering,
Collaborative Innovation Center for Advanced
Ship and Deep-Sea Exploration,
School of Naval Architecture,
Ocean and Civil Engineering,
Shanghai Jiao Tong University,
800 Dongchuan Road,
Shanghai 200240, China
e-mail: liqing5504@sjtu.edu.cn

Deqing Yang

State Key Laboratory of Ocean Engineering,
Collaborative Innovation Center for Advanced
Ship and Deep-Sea Exploration,
School of Naval Architecture,
Ocean and Civil Engineering,
Shanghai Jiao Tong University,
800 Dongchuan RoadZ,
Shanghai 200240, China
e-mail: yangdq@sjtu.edu.cn

1Corresponding author.

Contributed by the Technical Committee on Vibration and Sound of ASME for publication in the JOURNAL OF VIBRATION AND ACOUSTICS. Manuscript received February 2, 2018; final manuscript received June 1, 2018; published online July 5, 2018. Assoc. Editor: Stefano Gonella.

J. Vib. Acoust 140(6), 061016 (Jul 05, 2018) (15 pages) Paper No: VIB-18-1049; doi: 10.1115/1.4040514 History: Received February 02, 2018; Revised June 01, 2018

Sandwich structures that are embedded with cellular materials show excellent performance in terms of mechanics, electromagnetics, and acoustics. In this paper, sandwich panels with hybrid cellular cores of hexagonal, re-entrant hexagonal, and rectangular configurations along the panel surface are designed. The spectral element method (SEM) is applied to accurately predict the dynamic performance of the sandwich panels with a reduced number of elements and the system scale within a wide frequency range. The mechanical performance and the acoustic performance at normal incidence of the proposed structures are investigated and compared with conventional honeycomb panels with fixed cell geometries. It was found that the bending stiffness, fundamental frequencies, and sound transmission loss (STL) of the presented sandwich panels can be effectively changed by adjusting their hybrid cellular core configurations. Shape optimization designs of a hybrid cellular core for maximum STL are presented for specified tonal and frequency band cases at normal incidence. Hybrid sandwich panels increase the sound insulation property by 24.7%, 20.6%, and 109.6% for those cases, respectively, compared with conventional panels in this study. These results indicate the potential of sandwich structures with hybrid cellular cores in acoustic attenuation applications. Hybrid cellular cores can lead to inhomogeneous mechanical performance and constitute a broader platform for the optimum mechanical and acoustic design of sandwich structures.

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Fig. 1

The cell geometry and coordinate system for hexagonal honeycombs: (a) regular unit cell (θ > 0 deg) and (b) auxetic unit cell (θ < 0 deg)

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Fig. 2

The cellular core sandwich panels, each with a constant overall dimension (a total length of 1 m and height of 0.058m)

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Fig. 3

Sign convention for the frame element

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Fig. 4

Local and global coordinate systems

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Fig. 5

Node and element connection details of the frame members for cellular core sandwich panels

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Fig. 6

The iteration procedure used to compute the rth eigenfrequency below ω* based on the W–W algorithm

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Fig. 7

Static bending stiffness of the conventional and hybrid models with a relative density of ρ*/ρs from 0.05 to 0.3

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Fig. 8

Static responses of the conventional and hybrid models with a relative density of ρ*/ρs = 0.1

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Fig. 9

Trends of the first ten natural frequencies of the considered models (Hz)

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Fig. 10

Modes of the conventional and hybrid models: (a) the tenth flexural modes and (b) the foremost nonflexural modes

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Fig. 11

Locations of two specific points on the top face sheet of model 4 and the dynamic responses of these points

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Fig. 12

Dynamic responses of the conventional and hybrid models at 20,000 Hz

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Fig. 13

Applied loading and radiation conditions for the baffled, simply supported sandwich panel

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Fig. 14

Radiated sound pressure level for the hybrid models: (a) model 4 and (b) model 5

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Fig. 15

Sound transmission loss of the considered constant mass models from 1 to 1500 Hz: (a) conventional models and (b) hybrid models

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Fig. 16

Overall averaged STLs for the considered constant mass models from 1 to 1500 Hz

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Fig. 17

Workflow describing the optimization stages of the Multistart algorithm

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Fig. 18

Tonal optimization design at 950 Hz: (a) STLs and configurations of the baseline and optimized sandwich panels; (b) iterative curve of the optimized conventional panel; and (c) iterative curve of the optimized hybrid panel

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Fig. 19

Optimization design for the frequency band from 700 to 800 Hz: (a) STLs and configurations of the baseline and optimized sandwich panels; (b) iterative curve of the optimized conventional panel; and (c) iterative curve of the optimized hybrid panel

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Fig. 20

Optimization design for the frequency band from 200 to 1400 Hz: (a) STLs and configurations of the baseline and optimized sandwich panels; (b) iterative curve of the optimized conventional panel; and (c) iterative curve of the optimized hybrid panel



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