Abstract
Although the frequency dependence of linear tuned-mass-damper (TMD) is overcome by the nonlinear energy sink (NES), it is sensitive to the input energy. When the structure with NES is subjected to harmonic excitation, a larger or smaller excitation amplitude may deteriorate the performance of the NES. In particular, the large excitation may make the coupled system of NES produce a high closed detached response (CDR). The appearance of CDR means that NES may be completely ineffective. To solve this problem, multiple acoustic black hole (ABH) beams with damping layers at their tip are attached to the mass block of NES to improve NES’s mitigation effect. This novel NES is called ABH-NES in this paper. Its theoretical model is first established using the Gaussian Expansion Element Method (GEEM) and modal approach. Then, the influence of ABH effects and the number of ABH beams on the ABH-NES’s vibration mode are analyzed based on this model. After that, the responses of ABH-NES, NES, and Uniform Beam-NES (UB-NES, using uniform beams to replace the ABH’s in ABH-NES) are compared using time-domain integration, energy method, and harmonic balance method (HBM). The results show that ABH-NES has a better and more robust damping effect, especially under large excitation. The introduction of the ABH beam has two main influences: First, it raises the CDR's excitation threshold by increasing the energy dissipation pathway. Second, it reduces the amplitude of the CDR utilizing the highly damped modes of ABH-NES. Parametric analysis is carried out to discuss the effects of the partial parameters, such as absorber mass, stiffness, damping, ABH-NES’s frequency, on the new absorber. Finally, an experiment is provided to verify the effectiveness of theoretical analysis.
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The data that support the findings of this study are available from the corresponding author [Y. Tang], upon reasonable request.
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This work is supported by the National Natural Science Foundation of China (Nos. 11902001, 12132010, 12072221), and China Postdoctoral Science Foundation (No. 2018M641643).
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Appendices
Appendix A: Harmonic balance method
Since the nonlinear stiffness of the coupled system is cubic-type, its periodic solution xd and the nonlinear force Fdn are mainly composed of odd harmonics and can be assumed as [9, 42,43,44]
where a2k−1 and b2k−1 are the harmonic coefficients of the periodic solution. And they also are n + 1 dimensional vectors. The Nk determines the order of the harmonics and is set as 3 in this paper. The c2k−1 and d2k−1 denote the harmonic coefficients of nonlinear force and are scalar.
Substituting Eqs. (A.1) and (A.2) into Eq. (26) and performing harmonic balance, a set of algebraic equations can be obtained
Equation (A.3) contains 2n × Nk algebraic equations obtained based on the Arc-length method. We first divided these variables in H into two parts. One is P = [ωd, a1, b1, …, a2k−1, b2k−1, …]T with 2n × Nk + 1 elements considered as unknown. The other is Pn = [c1, d1, …, c2k−1, d2k−1, …]T seen as the functions of P. Its detailed form can be obtained using MATLAB or Maple but is not given in this paper for simplicity.
The procedure using the Arc-length method [9] is as follows:
(1) Step 1: Suppose a start P is known, written as Pi, and the next imprecise solution Pi+10 can be calculated by
where ds is an arc length increment, set to 0.001 in this paper. The \({\varvec{\nu}} = {\varvec{\nu}}^{*} /\left| {{\varvec{\nu}}^{*} } \right|\) (ν* = [v1, v2, …, v2n×Nk+1]T) is the tangent vector of the change in P and can be obtained by
where pi−1 or pi+1 is the i−1th or i + 1th element in P, and dH/dpi−1 can be derived by the chain rule of derivation
(2) Step 2: Use the Newton–Raphson method to handle Pi+10 to get an exact Pi+1. Suppose Pi+1 k represents Pi+10 after k Newton’s iterations. The Pi+1k+1 can be calculated by
When \(\left| {{\varvec{p}}_{i + 1}^{k + 1} - {\varvec{p}}_{i + 1}^{k} } \right|/\left| {{\varvec{p}}_{i + 1}^{k} } \right| < {\text{tolerable error}}\), we consider Pi+1k+1 to be sufficiently accurate and treat it as Pi+1. Here, the tolerable error is set as 0.0001.
(3) Step 3: Repeat the above steps with Pi+1 as a new initial condition to get the next solution Pi+2 until ωd reaches the excitation frequency boundary.
Appendix B: Floquet theory
Suppose xd* = [xdm*, xd1*, …, xdn*]T is the solution of Eq. (26), and its period is Td. After it is subjected to a perturbation ∆xd, the new solution is xd = xd* + ∆xd. Substituting it into Eq. (26) and preserving the linear part of ∆xd, we get
where
where I denotes the unit matrix, the Ad(τ) is a time-varying matrix with period Td. Its monodromy matrix is \({\varvec{B}} = \exp \left( {\int_{0}^{{{\text{T}}_{{\text{d}}} }} {{\varvec{A}}_{{\text{d}}} \left( \tau \right){\text{d}}\tau } } \right)\). By calculating the eigenvalues of B, we can get the stability of xd* (The absolute values of all eigenvalues are smaller than 1, and the xd* is stable, otherwise unstable) [9].
It is worth noting that the exact monodromy matrix B is usually difficult to obtain. To address this problem, Hsu et al. [46] divided Td into Nt segments and considered Ad to be constant in each subinterval, so that an approximate formula for B can be derived
When Nt is large enough, Eq. (35) can accurately predict the stability of xd*. And it is set as 1000 in this paper.
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Wang, T., Tang, Y., Qian, X. et al. Enhanced nonlinear performance of nonlinear energy sink under large harmonic excitation using acoustic black hole effect. Nonlinear Dyn 111, 12871–12898 (2023). https://doi.org/10.1007/s11071-023-08511-w
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DOI: https://doi.org/10.1007/s11071-023-08511-w