1. Introduction
Due to the extraordinary properties that natural materials do not possess, mechanical metamaterials have received extensive attention in practical engineering (Zhou et al. Reference Zhou, Wu, Chen, Chen, Lim and Reddy2020; Xu & Kong Reference Xu and Kong2023; Zheng et al. Reference Zheng, Chen, Dai, Qu and Meng2023). By special configurations of unit cells, these artificial periodic structures can achieve innovative functions, such as wave guidance (Zhao et al. Reference Zhao, Chen, Chang and Huang2023; Kundu, Naskar & Mukhopadhyay Reference Kundu, Naskar and Mukhopadhyay2024), low-frequency noise reduction (Wang, Yi & Zhu Reference Wang, Yi and Zhu2023; Jia et al. Reference Jia, Jin, Ye and Chen2025) and high impact resistance (Gan et al. Reference Gan, Li, Li, Li and Li2023; Yu et al. Reference Yu, Zhang, Ji, Yang, Tan, Chen, Tan, Laude and Kadic2024). Generally speaking, the design of mechanical metamaterials is mainly based on Bragg scattering and locally resonant mechanisms (Li et al. Reference Li, Kong, Xu and Hao2024; Wang, Meng & Chen Reference Wang, Meng and Chen2024). Different from the Bragg scattering mechanism, a locally resonant mechanism allows a unit cell to reach deep subwavelength scale, which is more practical in low-frequency wave manipulation (Arretche & Matlack Reference Arretche and Matlack2022; Euvé et al. Reference Euvé, Pham, Petitjeans, Pagneux and Maurel2024). Locally resonant metamaterials are typically constructed by integrating periodic resonant elements into beams, plates and shells. On the other hand, four-link mechanisms and continuous structures such as piezoelectric patches have been designed as resonant elements (He, Wang & Wang Reference He, Wang and Wang2021; Pierre, Leroy & Dollet Reference Pierre, Leroy and Dollet2022; Dong et al. Reference Dong, Huang, Wang and Chen2024). With the element resonance, the negative region of dynamic effective parameters appears, which prevents the propagation of elastic or sound waves (Chen, Hu & Huang Reference Chen, Hu and Huang2017; Venegas et al. Reference Venegas, Núñez, Boutin, Umnova and Zhang2022).
In order to adapt to increasingly complex engineering environments, locally resonant metamaterials with tunable properties have become a hot topic. The topological configuration or mechanical parameters of their unit cells can be changed with the variations of external loads (Jiao et al. Reference Jiao, Shu, He and Raney2024; Zhang, Hu & Rudykh Reference Zhang, Hu and Rudykh2024). This process is achieved by installing sensors and actuators into unit cells and introducing external energy, which is similar to traditional active control technology (Baz Reference Baz2022; Craig et al. Reference Craig, Wang, Su, Banerjee, Welch, Yip, Hu and Shi2022). Combining with smart materials such as piezoelectric (Sepehri, Mashhadi & Fakhrabadi Reference Sepehri, Mashhadi and Fakhrabadi2022), electromagnetic (Kwon, Zheng & Faraon Reference Kwon, Zheng and Faraon2022) and magnetorheological (Ramachandran & Rajagopal Reference Ramachandran and Rajagopal2024), active control systems with excellent performance can be designed to regulate the dynamic effective parameters. Due to the advantages of easy installation and fast response, the actuators composed of coils and magnets have been applied (Guo & Wang Reference Guo and Wang2024). Moreover, the influence of active control on metamaterials with multiple fields coupling requires further investigation.
Submarines have held great strategic significance because of exceptional underwater shielding. However, the noise resulting from such a complex and massive structure is inevitable. We know that sound waves in water are due to the fluid compressibility (Andrade et al. Reference Andrade, Bustamante, Kadri and Stuhlmeier2025; Farag Reference Farag2025). They are easily detected by sonar due to low attenuation. Therefore, modern submarines are typically covered with a layer of anechoic tiles to avoid active and passive sonar detection. With the development of sonar detection technology into the low-frequency range, the invisible effect achieved through anechoic tiles and other acoustic covering layer is always not satisfactory (Liu et al. Reference Liu, Huang, Zheng, Chen, Zhao, Qi, Li and Liu2023). In such a case, locally resonant metamaterials with low-frequency, lightweight and high-pressure resistance provide a novel technical approach (Yu et al. Reference Yu, Wang, Wang, Luo, Lei and Guo2023; Du et al. Reference Du, Li, Zhou, Shi, Zhang, Wang, Wang and Fan2025). Recent studies have reported on metamaterial plates with active control systems (Althamer Reference Althamer2024; Ji & Huber Reference Ji and Huber2024), which are highly suitable for the double-hull structure of submarines (Cao Reference Cao2023). The scattering of sound waves in fluid is a classical research topic that has engineering significance (Ayton Reference Ayton2016; Huang Reference Huang2017; Lyu Reference Lyu2023). Nevertheless, few researchers have investigated the acoustic scattering phenomenon of metamaterial plates to avoid active sonar detection.
In this work, metamaterial plates with active feedback control are proposed, which involves the four-link mechanism with local resonators. The negative region of dynamic effective density can be regulated by actuators composed of coils and magnets. Furthermore, a rigid baffle is considered to show the submarine bulkhead. The Fourier transform and Poisson summation formula are used to derive the scattered sound pressure without rigid baffle. Based on the Wiener–Hopf method, the scattered sound pressure resulting from the rigid baffle is obtained. The influence of active feedback control on the scattered sound pressure is studied. Moreover, the theoretical derivation is verified by the finite element method (FEM) and an acoustic scattering experiment. The present model is expected to be applied to new kinds of underwater vehicles, such as double-hull submarines with metastructure and active control. It provides lightweight design with the superior ability to avoid low-frequency active sonar detection.
2. Basic equations and derivations
2.1. Dynamic effective density and scattered sound pressure
As shown in figure 1(a), metamaterial plates with active feedback control are applied to a submarine hull for avoiding external sonar detection. The theoretical model is illustrated in figure 1(b), which consists of two infinite plates connected by periodic four-link mechanisms. The plate spacing is H, and the length and width of a unit cell are
$L_{x}$
and
$L_{y}$
, respectively. A Cartesian coordinate system (x, y, z) is established, and there is a baffle between the upper and lower plates at the position x = 0. The baffle is rigid with respect to the medium between the plates, but it does not affect the transverse motion of two plates. As shown in figures 1(c) and 1(d), each four-link mechanism has a pair of lateral and two vertical local resonators. The horizontal and vertical distances between the nodes on the link rod are
$ h/2 $
and
$ l/2 $
.
Metamaterial plates with active feedback control: (a) application to submarines; (b) structure with rigid baffle subjected to incident sound wave; (c) four-link mechanism in a unit cell and (d) its mechanical model.

The lateral resonator m
l
is connected to the four-link by the spring k
l
. The vertical resonator
$m_{v1}$
is attached to the upper and lower plates by the spring
$k_{v1}$
together with the four-link. The vertical resonators
$m_{v1}$
and
$m_{v2}$
are connected by a pair of springs with stiffness
$k_{v2}$
. The actuator includes a thin coil attached to resonator
$m_{v1}$
and a cylindrical magnet in resonator
$m_{v2}$
. The voltage load applied to the coil is tuned based on the received acceleration signal of resonator
$m_{v1}$
. Then a pair of control magnetic force
$F_{\kern-1pt c}$
is generated between resonators
$m_{v1}$
and
$m_{v2}$
. Displacements of the lateral resonator and link rod node are u
l
and
$ v $
. The displacements of vertical resonators
$m_{v1}$
and
$m_{v2}$
are
$u_{v1}$
and
$u_{v2}$
, and displacements of the upper and lower plates are
$w_{1}$
and
$w_{2}$
.
Based on the Kirchhoff plate theory, the governing equation of metamaterial plates is
where ∇4 = (∂2/∂x
2 + ∂2/∂y
2)2, D
j
=
$ E_{\!j} $
h
3
j
/[12(1 – μ
2
j
)] is the bending stiffness,
$ \rho_{pj} $
,
$ E_{\!j} $
,
$ \mu_{\!j} $
and
$ h_{\!j} $
are the density, Young’s modulus, Poisson’s ratio and thickness,
$ q_{\!j} $
is the internal lumped force generated by the four-link mechanism, and j = 1,2 represent the upper and lower plates, respectively.
The governing equations of vertical and lateral local resonators can be expressed as
where
$F_{\kern-1pt c}$
= B
L
I
c
, and B
L
is the parameter related to the size of the coil and magnet, and the axial distance between them (Guo & Wang Reference Guo and Wang2024).
The governing equation for the current I c in the coil can be written as
where R
e
and L
e
are the resistance and inductance, U
loud
= [G
1(∂2/∂t
2) + G
2]
$u_{v1}$
is the external voltage load, and G
1 (V s2 m−1) and G
2 (V m−1) are the acceleration and displacement feedback coefficients.
Based on the Bloch–Floquet theory of periodic systems, and considering the harmonic motion with time, the displacements of the metamaterial plates are
where W
1 and W
2 are the displacement amplitudes, k
x
and k
y
are the wavenumbers along the x- and y-axes, ω is the wave frequency, and
${\rm i}=\sqrt{-1}$
.
When the lattice constant of the metamaterial plates is subwavelength, the internal lumped forces are considered uniformly applied across the area of a unit cell, and can be expressed as
where
\begin{align}B=\frac{1}{L_{x}L_{y}}\left(\frac{k_{v1}^{2}}{A_{2}}-k_{v1}+\frac{k_{l}m_{l}\omega ^{2}}{k_{l}-m_{l}\omega ^{2}}\frac{h^{2}}{2l^{2}}\right)\!,\quad C=\frac{1}{L_{x}L_{y}}\left(\frac{k_{v1}^{2}}{A_{2}}-\frac{k_{l}m_{l}\omega ^{2}}{k_{l}-m_{l}\omega ^{2}}\frac{h^{2}}{2l^{2}}\right)\!.\end{align}
The explicit derivation is presented in Appendix A.
Substituting (2.4) and (2.5) into (2.1), and omitting the time-harmonic factor, we can obtain
where
$K=\sqrt{k_{x}^{2}+k_{y}^{2}}$
.
In order to derive the dynamic effective density, an equivalent single plate is considered with identical parameters for the upper plate, and
$K^{2}=\omega \sqrt{\rho _{\textit{eff}}h_{1}/D_{1}}$
is obtained. Considering the non-trivial solution for (2.7), the dynamic effective density can be derived as
\begin{align}\rho _{\textit{eff}1,2}=\frac{-b_{0}\pm \sqrt{b_{0}^{2}-4a_{0}c_{0}}}{2a_{0}},\end{align}
where
Compared with the scale of sound field, the thickness of the upper and lower plates can be negligible, and their position coordinates are regarded as z = 0 and z = −H. The space is divided into three regions by the metamaterial plates, each of which is occupied by a stationary fluid medium. The density and sound speed of the medium are ρ
η
and c
η
, in which η = 1, 2, 3 represent the mediums in the
$z \gt 0$
, −H <
$z \lt 0$
and
$z \lt -H$
regions, respectively. Interaction between the fluid medium and mechanical metamaterial is considered, and the whole system is excited by a plane sound wave p
in
incident on the upper plate. The propagating direction of the incident wave is parallel to the
$x{-}z$
plane, and the angle from the positive x-axis is θ
in
. The incident sound pressure is independent of the y-coordinate.
The incident sound pressure and specular reflection pressure can be written as
where k
1 =
$ \omega/c_{1} $
is the wavenumber in medium 1, and the harmonic time term e–iωt
is omitted during the following derivations.
Based on the principle of superposition, the total sound pressure
$p^{T}_{\eta}$
(x, z) in medium η, and the total displacement
$ w^{T}_{\!j} (x) $
of the upper and lower plates, can be expressed by
where
$p^{e}_{\eta}$
(x, z) and
$ w^{e}_{\!j}(x) $
are the pressure and displacement components generated by the elastic motion without the rigid baffle,
$p^{r}_{\eta}$
(x, z) and
$w^{r}_{\!j}$
(x) are the corresponding components from the rigid baffle, and p
sr
(x, z),
$p^{e}_{1}$
(x, z) and
$ p^{r}_{1}(x, z) $
constitute the total scattered sound pressure.
2.2. Scattered sound pressure of metamaterial plates without rigid baffle
According to the ideal fluid assumption (Batcheler Reference Batcheler1967; Lighthill Reference Lighthill1978; Landau & Lifshitz Reference Landau and Lifshitz1987), the sound pressure without rigid baffle in each medium region satisfies the Helmholtz equation
where
$ k_{2} = \omega/c_{2}$
and
$ k_{3} = \omega/c_{3}$
are the wavenumbers in mediums 2 and 3.
The Fourier transform with respect to the x-coordinate is applied to partial differential equations, and the transform of the pressure
$p^{e}_{\eta}$
(x, z) is defined as
where α is a complex variable.
Then the Fourier transform of (2.12) becomes
The general solutions of (2.14) are
where
$ \gamma^{2}_{\eta} = k^{2}_{\eta} - \alpha^{2} $
,
$ A^{e}_{\eta}(\alpha) $
and
$ B^{e}_{\eta}(\alpha) $
are the functions ofα to be determined.
For real values of α, the function γ η (α) is defined as
\begin{align}\gamma _{\eta }(\alpha )=\begin{cases} \sqrt{k_{\eta }^{2}-\alpha ^{2}}, & k_{\eta }^{2}\geq \alpha ^{2}, \\ {\rm i}\sqrt{\alpha ^{2}-k_{\eta }^{2}},& k_{\eta }^{2}\lt \alpha ^{2}, \end{cases}\end{align}
and for complex values of α, the branch cut is chosen to ensure Im(γ
η
)
$\geq$
0.
The total pressure
$ p^{t}_{1} $
(x, z) in medium 1 is
Substituting (2.10)–(2.17) and applying the Fourier transform gives
The continuous velocity conditions about the pressure at fluid–structure interfaces are (Xin & Lu Reference Xin and Lu2010; He et al. Reference He, Wang and Wang2021)
Considering the radiation condition for outgoing waves in mediums 1 and 3,
$ B^{e}_{1} = 0 $
and
$ A^{e}_{3} = 0 $
can be obtained. Substituting (2.15) into (2.19),
$ A^{e}_{\eta} (\alpha) $
and
$ B^{e}_{\eta} (\alpha) $
can be derived as
The sound pressure at the coupling interface is expressed as
Governing equations of the metamaterial plates with fluid load are (Xin & Lu Reference Xin and Lu2010; He et al. Reference He, Wang and Wang2021)
\begin{align} D_{1}\frac{\partial ^{4}w_{1}^{e}(x)}{\partial x^{4}}-\omega ^{2}M_{1}\,w_{1}^{e}(x)&=-p_{1}^{t}\left(x,0\right)+p_{2}^{e}\left(x,0\right)+\!\sum _{n=-\infty }^{\infty }\!F_{1}^{e}(x)\,\delta \left[x-\left(\frac{1}{2}+n\!\right)\!L_{x}\!\right]\!, \\[-12pt] \nonumber \end{align}
\begin{align} D_{2}\frac{\partial ^{4}w_{2}^{e}(x)}{\partial x^{4}}-\omega ^{2}M_{2}\,w_{2}^{e}(x)&=-p_{2}^{e}\left(x,-H\right)+p_{3}^{e}\left(x,-H\right)\nonumber\\&\quad +\sum _{n=-\infty }^{\infty }F_{2}^{e}(x)\,\delta \left[x-\left(\frac{1}{2}+n\right)L_{x}\right]\!, \\[9pt] \nonumber\end{align}
where
$ M_{\!j} $
=
$ \rho_{pj} $
$ h_{\!j} $
is the mass per unit area,
$ F^{e}_{1} (x) $
and
$ F^{e}_{2} (x) $
are the internal lumped forces, and
$ \delta (\cdot) $
is the Dirac delta function.
The Fourier transform of (2.22) is
\begin{align} \big(D_{1}\alpha ^{4}-\omega ^{2}M_{1}\big)\overline{w}_{1}^{e}(\alpha )&=-\overline{p}_{1}^{t}(\alpha ,0)+\overline{p}_{2}^{e}(\alpha ,0)+\sum _{n=-\infty }^{\infty }F_{1}^{e}\left(x_{n}\right){\rm e}^{-{\rm i}\alpha {x_{n}}}, \end{align}
\begin{align} \big(D_{2}\alpha ^{4}-\omega ^{2}M_{2}\big)\overline{w}_{2}^{e}(\alpha )&=-\overline{p}_{2}^{e}(\alpha ,-H)+\overline{p}_{3}^{e}(\alpha ,-H)+\sum _{n=-\infty }^{\infty }F_{2}^{e}\left(x_{n}\right){\rm e}^{-{\rm i}\alpha {x_{n}}}, \end{align}
where x
n
= x
0 + nL
x
, with x
0 =
$L_{x}$
/2.
Based on (2.5) and (2.6), the internal lumped forces can be expressed as
where K 1 = BL x and K 2 = CL x .
According to the property of an incident sound wave and the periodicity of structure, the displacement of two plates can be written as
Substituting (2.25) into (2.24), we can derive
During the following derivation, we consider
$ F^{e}_{1} $
and
$ F^{e}_{2} $
instead of
$ F^{e}_{1}(x_{0})$
and
$ F^{e}_{2}(x_{0})$
, respectively. Based on (2.18), (2.21) and (2.26), (2.23) can be derived as
\begin{align} &\left(D_{1}\alpha ^{4}-\omega ^{2}M_{1}-\frac{{\rm i}\omega ^{2}\rho _{1}}{\gamma _{1}}+\frac{\omega ^{2}\rho _{2}\cos \gamma _{2}H}{\gamma _{2}\,{\sin }\, \gamma _{2}H}\right)\,\overline{w}_{1}^{e}(\alpha )-\frac{\omega ^{2}\rho _{2}}{\gamma _{2}\,{\sin }\, \gamma _{2}H}\overline{w}_{2}^{e}(\alpha )\nonumber\\&\quad =-4\pi \delta \left(\alpha +k_{1}\,{\cos }\, \theta _{\textit{in}}\right)+F_{1}^{e}{\rm e}^{-{\rm i}\alpha {x_{0}}}\sum _{n=-\infty }^{\infty }{\rm e}^{-{\rm i}n{L_{x}}\left(\alpha +k_{1}\,{\cos }\, \theta _{\textit{in}}\right)}, \end{align}
\begin{align} &\frac{-\omega ^{2}\rho _{2}}{\gamma _{2}\,{\sin }\, \gamma _{2}H}\,\overline{w}_{1}^{e}(\alpha )+\left(D_{2}\alpha ^{4}-\omega ^{2}M_{2}-\frac{{\rm i}\omega ^{2}\rho _{3}}{\gamma _{3}}+\frac{\omega ^{2}\rho _{2}\cos \gamma _{2}H}{\gamma _{2}\,{\sin }\, \gamma _{2}H}\right)\overline{w}_{2}^{e}(\alpha )\nonumber\\&\quad =F_{2}^{e}\,{\rm e}^{-{\rm i}\alpha {x_{0}}}\sum _{n=-\infty }^{\infty }{\rm e}^{-{\rm i}n{L_{x}}\left(\alpha +k_{1}\,{\cos }\, \theta _{\textit{in}}\right)}. \end{align}
The matrix form of (2.27) is
\begin{align} \boldsymbol{S}(\alpha )\left\{\!\!\begin{array}{c} \overline{w}_{1}^{e}(\alpha )\\[5pt] \overline{w}_{2}^{e}(\alpha )\end{array}\!\!\right\}=-4\pi\left\{\!\!\begin{array}{c} \delta(\alpha +k_1 \cos \theta_{\textit{in}} )\\ 0\end{array}\!\!\right\}+\left\{\!\!\begin{array}{c} F_1^e\\[5pt] F_2^e\end{array}\!\!\right\} {\rm e}^{-{\rm i}\alpha {x_{0}}}\sum _{n=-\infty }^{\infty }{\rm e}^{-{\rm i}n{L_{x}}\left(\alpha +k_{1}\,{\cos }\, \theta _{\textit{in}}\right)} \end{align}
where S(α) represents the dynamic stiffness matrix with fluid damping effect (Springer, Scheit & Becker Reference Springer, Scheit and Becker2017).
The elements of matrix S(α) are
According to the Poisson summation formula, we can obtain
\begin{align}\sum _{n=-\infty }^{\infty }{\rm e}^{-{\rm i}n{L_{x}}(\alpha +{k_{1}}\,{\cos }\, \theta _{\textit{in}})}=\frac{2\pi }{L_{x}}\sum _{n=-\infty }^{\infty }\delta \left(\alpha +k_{1}\,{\cos }\, \theta _{\textit{in}}-\frac{2n\pi }{L_{x}}\right)\!.\end{align}
Based on (2.28) and (2.30), the following expressions are obtained:
\begin{align} & \overline{w}_{1}^{e}(\alpha )=\frac{-4\pi S_{22}(\alpha )}{{\varDelta }(\alpha )}\delta \!\left(\alpha -\kappa \right)+\frac{2\pi }{L_{x}{\varDelta }(\alpha )}\left[F_{1}^{e}S_{22}(\alpha )-F_{2}^{e}S_{12}(\alpha )\!\right]{\rm e}^{-{\rm i}\alpha {x_{0}}}\!\sum _{n=-\infty }^{\infty }\!\delta \!\left(\alpha -\kappa _{n}\right)\!, \end{align}
\begin{align} & \overline{w}_{2}^{e}(\alpha )=\frac{4\pi S_{12}(\alpha )}{{\varDelta }(\alpha )}\delta \left(\alpha -\kappa \right)-\frac{2\pi }{L_{x}{\varDelta }(\alpha )}\left[F_{1}^{e}S_{12}(\alpha )-F_{2}^{e}S_{11}(\alpha )\right]{\rm e}^{-{\rm i}\alpha {x_{0}}}\sum _{n=-\infty }^{\infty }\delta \!\left(\alpha -\kappa _{n}\right)\!, \end{align}
where κ = –k
1cos θ
in
, κ
n
= 2nπ/
$L_{x}$
– k
1cos θ
in
and Δ(α) = S
11(α)S
22(α) – S
12(α)S
21(α).
By Fourier inverse transform in (2.31), the displacement
$ w^{e}_{\!j}(x) $
can be derived as
where
\begin{align}&Q_{1}(x)=\sum _{n=-\infty }^{\infty }\frac{S_{22}(\kappa _{n})}{{\varDelta }(\kappa _{n})}{\rm e}^{{\rm i}{\kappa _{n}}\left(x-x_{0}\right)}, \qquad Q_{2}(x)=\sum _{n=-\infty }^{\infty }\frac{S_{11}(\kappa _{n})}{{\varDelta }(\kappa _{n})}{\rm e}^{{\rm i}{\kappa _{n}}\left(x-x_{0}\right)},\nonumber\\& Q_{3}(x)=\sum _{n=-\infty }^{\infty }\frac{-S_{12}(\kappa _{n})}{{\varDelta }(\kappa _{n})}{\rm e}^{{\rm i}{\kappa _{n}}(x-{x_{0}})}.\end{align}
It is obvious that as
$|n|$
increases, the term in the summation symbol will quickly approach zero. As a result, the sum can be evaluated by truncation. And Q
1 = Q
1(x
0), Q
2 = Q
2(x
0) and Q
3 = Q
3(x
0) are used during the following derivation. Based on (2.24) and (2.32), the internal lumped forces generated by the four-link mechanism at x = x
0 can be derived as
where
According to (2.15), (2.20) and (2.31), the sound pressures in mediums 1 and 2 can be expressed as
\begin{align} &\overline{p}_{1}^{e}(\alpha ,z)=\frac{4\pi {\rm i}\omega ^{2}\rho _{1}S_{22}(\alpha ){\rm e}^{{\rm i}{\gamma _{1}}z}}{{\Delta }(\alpha )\gamma _{1}}\delta \left(\alpha -\kappa \right)\nonumber\\&\qquad\qquad\quad-\frac{2\pi {\rm i}\omega ^{2}\rho _{1}{\rm e}^{{\rm i}{\gamma _{1}}z}}{L_{x}{\Delta }(\alpha )\gamma _{1}}\left[F_{1}^{e}S_{22}(\alpha )-F_{2}^{e}S_{12}(\alpha )\right]{\rm e}^{-{\rm i}\alpha {x_{0}}}\sum _{n=-\infty }^{\infty }\delta\! \left(\alpha -\kappa _{n}\right)\!, \end{align}
\begin{align} &\overline{p}_{2}^{e}(\alpha ,z)=\frac{\omega ^{2}\rho _{2}\,{\cos }\, \gamma _{2}(z+H)}{{\Delta }(\alpha )\gamma _{2}\sin \gamma _{2}H}\nonumber\\&\quad\times\left\{4\pi \delta \left(\alpha -\kappa \right)S_{22}(\alpha )-\frac{2\pi }{L_{x}}\left[F_{1}^{e}S_{22}(\alpha )-F_{2}^{e}S_{12}(\alpha )\right]{\rm e}^{-{\rm i}\alpha {x_{0}}}\sum _{n=-\infty }^{\infty }\delta\! \left(\alpha -\kappa _{n}\right)\right\}\nonumber\\&\quad+\frac{\omega ^{2}\rho _{2}\,{\cos }\, \gamma _{2}z}{{\Delta }(\alpha )\gamma _{2}\sin \gamma _{2}H}\left\{4\pi \delta \left(\alpha -\kappa \right)S_{12}(\alpha )-\frac{2\pi }{L_{x}}\left[F_{1}^{e}S_{12}(\alpha )-F_{2}^{e}S_{11}(\alpha )\right]{\rm e}^{-{\rm i}\alpha {x_{0}}}\right.\nonumber\\&\quad\times\left. \sum _{n=-\infty }^{\infty }\delta\! \left(\alpha -\kappa _{n}\right)\right\}\!. \end{align}
The inverse Fourier transform of (2.36) can be derived as
\begin{align}& p_{1}^{e}(x,z)=\frac{2{\rm i}\omega ^{2}\rho _{1}S_{22}(\kappa)}{{\Delta }(\kappa)k_{1}\,{\sin }\, \theta _{\textit{in}}}{\rm e}^{-{\rm i}{k_{1}}\left(x\,{\cos }\, \theta _{\textit{in}}-z\,{\sin }\, \theta _{\textit{in}}\right)}\nonumber\\&\qquad\qquad-\frac{{\rm i}\omega ^{2}\rho _{1}}{L_{x}}\sum _{n=-\infty }^{\infty }\frac{F_{1}^{e}S_{22}(\kappa _{n})-F_{2}^{e}S_{12}(\kappa _{n})}{{\Delta }(\kappa _{n})\gamma _{1}(\kappa _{n})}{\rm e}^{{\rm i}\left[\kappa _{n}\left(x-x_{0}\right)+\gamma _{1}(\kappa _{n})z\right]}, \end{align}
\begin{align}& p_{2}^{e}(x,z)=\frac{2\omega ^{2}\rho _{2}\left[S_{22}(\kappa){\cos }\, \gamma _{2}(\kappa)(z+H)+S_{12}(\kappa){\cos }\, \gamma _{2}(\kappa)z\right]{\rm e}^{{\rm i}\kappa x}}{{\Delta }(\kappa)\gamma _{2}(\kappa)\sin \gamma _{2}(\kappa)H}-\frac{\omega ^{2}\rho _{2}}{L_{x}}\sum _{n=-\infty }^{\infty }\nonumber\\&\times\frac{\left[\!F_{1}^{e}S_{22}(\kappa _{n})-F_{2}^{e}S_{12}(\kappa _{n})\!\right]{\cos }\, \gamma _{2}(\kappa _{n})(z+H)+\left[\!F_{1}^{e}S_{12}(\kappa _{n})-F_{2}^{e}S_{11}(\kappa _{n})\!\right]{\cos }\, \gamma _{2}(\kappa _{n})z}{{\Delta }(\kappa _{n})\gamma _{2}(\kappa _{n})\sin \gamma _{2}(\kappa _{n})H}\nonumber\\&\times {\rm e}^{{\rm i}{\kappa _{n}}\left(x-x_{0}\right)}. \end{align}
2.3. Scattered sound pressure resulting from rigid baffle
When the rigid baffle exists,
$ p^{r}_{1}(x, z) $
and
$ p^{r}_{3} (x,z) $
still satisfy (2.14). However,
$ p^{r}_{2} (x,z) $
is no longer continuous for the x-coordinate, and its governing equation becomes
The normal velocity of fluid on the rigid baffle at x = 0 should be zero, and the corresponding equation can be expressed as (Ayton Reference Ayton2016; Huang Reference Huang2017)
\begin{align}\left.\frac{\partial p_{2}^{T}(x,z)}{\partial x}\right| _{x=0}=\left.\frac{\partial p_{2}^{e}(x,z)}{\partial x}\right| _{x=0}+\left.\frac{\partial p_{2}^{r}(x,z)}{\partial x}\right| _{x=0}=0.\end{align}
According to (2.37b ), we can further obtain
\begin{align}\left.\frac{\partial p_{2}^{r}(x,z)}{\partial x}\right| _{x=0}=X{\rm e}^{{{\rm i}\gamma _{2}}(\kappa )z}+Y{\rm e}^{-{\rm i}{\gamma _{2}}(\kappa )z}+\sum _{n=-\infty }^{\infty }\big[X_{n}{\rm e}^{{\rm i}{\gamma _{2}}({\kappa _{n}})z}+Y_{n}{\rm e}^{-{\rm i}{\gamma _{2}}({\kappa _{n}})z}\big],\end{align}
where
\begin{align} X_{n}&=\frac{{\rm i}\omega ^{2}\rho _{2}\kappa _{n}{\rm e}^{-{\rm i}{\kappa _{n}}{x_{0}}}}{2L_{x}\Delta (\kappa _{n})\gamma _{2}(\kappa _{n})\sin \gamma _{2}(\kappa _{n})H}\Big\{F_{1}^{e}\big[{\rm e}^{{\rm i}{\gamma _{2}}({\kappa _{n}})H}S_{22}(\kappa _{n})+S_{12}(\kappa _{n})\big]\Big.\nonumber\\[4pt]&\quad\Big. -F_{2}^{e}\big[{\rm e}^{{\rm i}{\gamma _{2}}({\kappa _{n}})H}S_{12}(\kappa _{n})+S_{11}(\kappa _{n})\big]\Big\}, \\[-9pt] \nonumber \end{align}
\begin{align} Y_{n}&=\frac{{\rm i}\omega ^{2}\rho _{2}\kappa _{n}{\rm e}^{-{\rm i}{\kappa _{n}}{x_{0}}}}{2L_{x}\Delta (\kappa _{n})\gamma _{2}(\kappa _{n})\sin \gamma _{2}(\kappa _{n})H}\Big\{F_{1}^{e}\big[{\rm e}^{-{\rm i}{\gamma _{2}}({\kappa _{n}})H}S_{22}(\kappa _{n})+S_{12}(\kappa _{n})\big]\Big.\nonumber\\[4pt]&\quad\Big. -F_{2}^{e}\big[{\rm e}^{-{\rm i}{\gamma _{2}}({\kappa _{n}})H}S_{12}(\kappa _{n})+S_{11}(\kappa _{n})\big]\Big\}. \\[9pt] \nonumber \end{align}
According to the geometric characteristic of metamaterial plates and the loading condition, the mechanical field generated by the rigid baffle is symmetric with respect to x = 0. It can be obtained from (2.40) that
$ \partial p^{r}_{2} (x, z) / \partial x $
and
$ p^{r}_{2} (x,z) $
are even and odd functions of x, respectively. Then we can see that
$ p^{r}_{1}(x, z) $
,
$ p^{r}_{3} (x,z) $
,
$ w^{r}_{1} (x) $
and
$ w^{r}_{2} (x) $
are odd functions.
The Wiener–Hopf method is applied to the sound pressure scattered by the rigid baffle, and the half-range Fourier transforms are defined as
where the former integral function is analytic for all complex α in the upper half-plane Im(α)
$\geq$
0, and the latter is analytic in the lower half-plane Im(α)
$\leq$
0. In addition, both functions are algebraically bounded as
$|\alpha|$
approaches infinity.
Based on (2.43a ) with integration by parts, the Fourier transform of (2.38) can be derived as
Adding the corresponding equation evaluated at –α to (2.44), and substituting (2.40), we can obtain
\begin{align}&\left(\frac{\partial ^{2}}{\partial z^{2}}+\gamma _{2}^{2}\right)\left[\overline{p}_{2+}^{r}(\alpha ,z)+\overline{p}_{2+}^{r}(-\alpha ,z)\right]=-2\big[X{\rm e}^{{\rm i}{\gamma _{2}}(\kappa)z}+Y{\rm e}^{-{\rm i}{\gamma _{2}}(\kappa)z}\big]\nonumber\\&\quad -2\sum _{n=-\infty }^{\infty }\big[X_{n}{\rm e}^{{\rm i}{\gamma _{2}}(\kappa _{n})z}+Y_{n}{\rm e}^{-{\rm i}{\gamma _{2}}(\kappa _{n})z}\big].\end{align}
The solution to this equation can be directly derived as the superposition of the general and particular solutions as
\begin{align}\overline{p}_{2+}^{r}(\alpha ,z)+\overline{p}_{2+}^{r}\left(-\alpha ,z\right)&=A_{2}^{r}(\alpha ){\rm e}^{{\rm i}{\gamma _{2}}z}+B_{2}^{r}(\alpha ){\rm e}^{-{\rm i}{\gamma _{2}}z}+2\frac{X{\rm e}^{{\rm i}{\gamma _{2}}(\kappa)z}+Y{\rm e}^{-{\rm i}{\gamma _{2}}(\kappa)z}}{\alpha ^{2}-\kappa ^{2}}\nonumber\\&\quad+2\sum _{n=-\infty }^{\infty }\frac{X_{n}{\rm e}^{{\rm i}{\gamma _{2}}(\kappa _{n})z}+Y_{n}{\rm e}^{-{\rm i}{\gamma _{2}}(\kappa _{n})z}}{\alpha ^{2}-\kappa _{n}^{2}}.\end{align}
Then, setting z = 0 and z = −H, we obtain
\begin{align}\overline{p}_{2+}^{r}(\alpha ,0)+\overline{p}_{2+}^{r}\left(-\alpha ,0\right)&=A_{2}^{r}(\alpha )+B_{2}^{r}(\alpha )+2\frac{X+Y}{\alpha ^{2}-\kappa ^{2}}+2\sum _{n=-\infty }^{\infty }\frac{X_{n}+Y_{n}}{\alpha ^{2}-\kappa _{n}^{2}}, \end{align}
\begin{align} \overline{p}_{2+}^{r}(\alpha ,-H)+\overline{p}_{2+}^{r}(-\alpha ,-H)&=A_{2}^{r}(\alpha ){\rm e}^{-{\rm i}{\gamma _{2}}H}\!+\!B_{2}^{r}(\alpha ){\rm e}^{{\rm i}{\gamma _{2}}H}\!+\!2\frac{X{\rm e}^{-{\rm i}{\gamma _{2}}(\kappa)H}+Y{\rm e}^{{\rm i}{\gamma _{2}}(\kappa)H}}{\alpha ^{2}-\kappa ^{2}}\nonumber\\&\quad+2\sum _{n=-\infty }^{\infty }\frac{X_{n}{\rm e}^{-{\rm i}{\gamma _{2}}(\kappa_{n})H}+Y_{n}{\rm e}^{{\rm i}{\gamma _{2}}(\kappa_{n})H}}{\alpha ^{2}-\kappa _{n}^{2}}. \end{align}
Similar to (2.19b ) and (2.19c ), the boundary conditions can be written as
Substituting (2.46) into (2.48), we can derive that
\begin{align} \omega ^{2}\rho _{2}\left[\overline{w}_{1+}^{r}(\alpha )+\overline{w}_{1+}^{r}(-\alpha )\right]&={\rm i}\gamma _{2}\left[A_{2}^{r}(\alpha )-B_{2}^{r}(\alpha )\right]+\frac{2{\rm i}\gamma _{2}(\kappa )}{\alpha ^{2}-\kappa ^{2}}\left(X-Y\right)\nonumber\\&\quad+\sum _{n=-\infty }^{\infty }\frac{2{\rm i}\gamma _{2}(\kappa _{n})}{\alpha ^{2}-\kappa _{n}^{2}}\left(X_{n}-Y_{n}\right)\!, \end{align}
\begin{align}\omega ^{2}\rho _{2}\left[\overline{w}_{2+}^{r}(\alpha )+\overline{w}_{2+}^{r}(-\alpha )\right]&={\rm i}\gamma _{2}\big[A_{2}^{r}(\alpha ){\rm e}^{-{\rm i}{\gamma _{2}}H}-B_{2}^{r}(\alpha ){\rm e}^{{\rm i}{\gamma _{2}}H}\big]\nonumber\\[4pt]&\quad+\frac{2{\rm i}\gamma _{2}(\kappa )}{\alpha ^{2}-\kappa ^{2}}\big[X{\rm e}^{-{\rm i}{\gamma _{2}}(\kappa )H}-Y{\rm e}^{{\rm i}{\gamma _{2}}(\kappa )H}\big]\nonumber\\[4pt]&\quad +\sum _{n=-\infty }^{\infty }\frac{2{\rm i}\gamma _{2}(\kappa _{n})}{\alpha ^{2}-\kappa _{n}^{2}}\big[X_{n}{\rm e}^{-{\rm i}{\gamma _{2}}(\kappa_{n} )H}-Y_{n}{\rm e}^{{\rm i}{\gamma _{2}}(\kappa _{n})H}\big]. \end{align}
The unknown functions
$ A^{r}_{2} (\alpha) $
and
$ B^{r}_{2} (\alpha) $
can be eliminated by (2.47) and (2.49), and we can obtain
\begin{align}\overline{p}_{2+}^{r}(\alpha ,0)+\overline{p}_{2+}^{r}\left(-\alpha ,0\right)&=\frac{-\omega ^{2}\rho _{2}}{\gamma _{2}\,{\sin }\, \gamma _{2}H}\left\{\left[\overline{w}_{1+}^{r}(\alpha )+\overline{w}_{1+}^{r}\left(-\alpha \right)\right]{\cos }\, \gamma _{2}H\right.\nonumber\\[4pt]&\quad\left.-\left[\overline{w}_{2+}^{r}(\alpha )+\overline{w}_{2+}^{r}\left(-\alpha \right)\right]\right\}-F(\alpha ), \\[-9pt] \nonumber \end{align}
\begin{align}\overline{p}_{2+}^{r}(\alpha ,-H)+\overline{p}_{2+}^{r}(-\alpha ,-H)&=\frac{-\omega ^{2}\rho _{2}}{\gamma _{2}\,{\sin }\, \gamma _{2}H}\left\{\left[\overline{w}_{1+}^{r}(\alpha )+\overline{w}_{1+}^{r}\left(-\alpha \right)\right]\right.\nonumber\\[4pt]&\quad\left.-\left[\overline{w}_{2+}^{r}(\alpha )+\overline{w}_{2+}^{r}\left(-\alpha \right)\right]{\cos }\, \gamma _{2}H\right\}-G(\alpha ), \\[12pt] \nonumber \end{align}
where expressions for
$ F(\alpha) $
and
$ G(\alpha) $
are
\begin{align}F(\alpha )&=\frac{-2}{\alpha ^{2}-\kappa ^{2}}\left[X+Y+\frac{{\rm i}\gamma _{2}(\kappa)}{\gamma _{2}\,{\sin }\, \gamma _{2}H}\big(\tilde{X}\,{\cos }\, \gamma _{2}H-\tilde{Y}\big)\right]\nonumber\\&\quad+\sum _{n=-\infty }^{\infty }\frac{-2}{\alpha ^{2}-\kappa _{n}^{2}}\left[X_{n}+Y_{n}+\frac{{\rm i}\gamma _{2}(\kappa _{n})}{\gamma _{2}\,{\sin }\, \gamma _{2}H}\big(\tilde{X}_{n}\,{\cos }\, \gamma _{2}H-\tilde{Y}_{n}\big)\right]\!, \\[-9pt] \nonumber \end{align}
\begin{align}G(\alpha )&=\frac{-2}{\alpha ^{2}-\kappa ^{2}}\left\{X{\rm e}^{-{\rm i}{\gamma _{2}}(\kappa)H}+Y{\rm e}^{{\rm i}{\gamma _{2}}(\kappa)H}+\frac{{\rm i}\gamma _{2}(\kappa)}{\gamma _{2}\,{\sin }\, \gamma _{2}H}\big(\tilde{X}-\tilde{Y}\,{\cos }\, \gamma _{2}H\big)\right\}\nonumber\\&\quad+\!\sum _{n=-\infty }^{\infty }\frac{-2}{\alpha ^{2}-\kappa _{n}^{2}}\left\{X_{n}{\rm e}^{-{\rm i}{\gamma _{2}}(\kappa _{n})H}+Y_{n}{\rm e}^{{\rm i}{\gamma _{2}}(\kappa _{n})H}+\frac{{\rm i}\gamma _{2}(\kappa _{n})}{\gamma _{2}\,{\sin }\, \gamma _{2}H}\big(\tilde{X}_{n}-\tilde{Y}_{n}\,{\cos }\, \gamma _{2}H\big)\right\}\!. \\[12pt] \nonumber \end{align}
and
Based on the odd functions and half-range Fourier transform in (2.43), the following equations can be obtained:
Then (2.50) becomes
\begin{align}\overline{p}_{2+}^{r}(\alpha ,0)-\overline{p}_{2-}^{r}(\alpha ,0)&=\frac{-\omega ^{2}\rho _{2}}{\gamma _{2}\,{\sin }\, \gamma _{2}H}\left\{\left[\overline{w}_{1+}^{r}(\alpha )-\overline{w}_{1-}^{r}(\alpha )\right]{\cos }\, \gamma _{2}H\right.\nonumber\\&\quad\left.-\left[\overline{w}_{2+}^{r}(\alpha )-\overline{w}_{2-}^{r}(\alpha )\right]\right\}-F(\alpha ), \\[-9pt] \nonumber \end{align}
\begin{align}\overline{p}_{2+}^{r}(\alpha ,-H)-\overline{p}_{2-}^{r}(\alpha ,-H)&=\frac{-\omega ^{2}\rho _{2}}{\gamma _{2}\,{\sin }\, \gamma _{2}H}\left\{\left[\overline{w}_{1+}^{r}(\alpha )-\overline{w}_{1-}^{r}(\alpha )\right]\right.\nonumber\\&\quad\left.-\left[\overline{w}_{2+}^{r}(\alpha )-\overline{w}_{2-}^{r}\left(-\alpha \right)\right]{\cos }\, \gamma _{2}H\right\}-G(\alpha ). \\[12pt] \nonumber\end{align}
Although both γ
2 and sinγ
2
H are multivalued functions, we know through analysis that the functions
$1/\gamma _{2}\sin \gamma _{2}H$
and
$\cos \gamma _{2}H/\gamma _{2}\sin \gamma _{2}H$
in (2.55) have no branch points and are algebraically bounded as
$|\alpha|$
approaches infinity. Their only singularities are an infinite number of poles located at
$\alpha =\pm \sqrt{k_{2}^{2}-(m\pi /H)^{2}}=\pm \alpha _{m}$
(m = 0, 1, 2, …). Therefore, the singularities in (2.55) are ±κ, ±κ
n
and ±α
m
.
The Wiener–Hopf additive decomposition can be applied to obtain
The integral contours C 1 and C 2 in (2.56) are shown in figure 2. Based on (2.55), the singularities in the integrand of (2.56) are α, ±κ, ±κ n and ±α m . The path on real axis is deformed to lie above the negative singularities and below the positive ones when approaching them. It can be seen from residue formulas that all singularities are simple poles. The integral contour C 1 encloses the poles at −κ, −κ n and −α m , while contour C 2 encloses the poles at κ, κ n and α m . According to the Cauchy residue theory, the integral in (2.56) is transformed into the residue calculation as the following forms:
\begin{align} \overline{p}_{2+}^{r}(\alpha ,0)&=\frac{-\omega ^{2}\rho _{2}}{\gamma _{2}\,{\sin }\, \gamma _{2}H}\left[\overline{w}_{1+}^{r}(\alpha )\,{\cos }\, \gamma _{2}H-\overline{w}_{2+}^{r}(\alpha )\right]\nonumber\\&\quad-\frac{\omega ^{2}\rho _{2}\alpha }{H}\sum _{m=0}^{\infty }\frac{\varepsilon _{m}\left[\overline{w}_{1+}^{r}(\alpha _{m})-(-1)^{m}\overline{w}_{2+}^{r}(\alpha _{m})\right]}{\alpha _{m}\!\left(\alpha ^{2}-\alpha _{m}^{2}\right)}-F_{+}(\alpha ), \end{align}
\begin{align} \overline{p}_{2-}^{r}(\alpha ,0)&=\frac{-\omega ^{2}\rho _{2}}{\gamma _{2}\,{\sin }\, \gamma _{2}H}\left[\overline{w}_{1-}^{r}(\alpha )\,{\cos }\, \gamma _{2}H-\overline{w}_{2-}^{r}(\alpha )\right]\nonumber\\&\quad-\frac{\omega ^{2}\rho _{2}\alpha }{H}\sum _{m=0}^{\infty }\frac{\varepsilon _{m}\left[\overline{w}_{1+}^{r}(\alpha _{m})-(-1)^{m}\overline{w}_{2+}^{r}(\alpha _{m})\right]}{\alpha _{m}\!\left(\alpha ^{2}-\alpha _{m}^{2}\right)}+F_{-}(\alpha ), \end{align}
\begin{align} \overline{p}_{2+}^{r}(\alpha ,-H)&=\frac{-\omega ^{2}\rho _{2}}{\gamma _{2}\,{\sin }\, \gamma _{2}H}\left[\overline{w}_{1+}^{r}(\alpha )-\overline{w}_{2+}^{r}(\alpha )\,{\cos }\, \gamma _{2}H\right]\nonumber\\&\quad-\frac{\omega ^{2}\rho _{2}\alpha }{H}\sum _{m=0}^{\infty }\frac{\varepsilon _{m}\left[(-1)^{m}\overline{w}_{1+}^{r}(\alpha _{m})-\overline{w}_{2+}^{r}(\alpha _{m})\right]}{\alpha _{m}\!\left(\alpha ^{2}-\alpha _{m}^{2}\right)}-G_{+}(\alpha ), \end{align}
\begin{align} \overline{p}_{2-}^{r}(\alpha ,-H)&=\frac{-\omega ^{2}\rho _{2}}{\gamma _{2}\,{\sin}\,\gamma _{2}H}\left[\overline{w}_{1-}^{r}(\alpha )-\overline{w}_{2-}^{r}(\alpha )\,{\cos }\, \gamma _{2}H\right]\nonumber\\&\quad-\frac{\omega ^{2}\rho _{2}\alpha }{H}\sum _{m=0}^{\infty }\frac{\varepsilon _{m}\left[(-1)^{m}\overline{w}_{1+}^{r}(\alpha _{m})-\overline{w}_{2+}^{r}(\alpha _{m})\right]}{\alpha _{m}\!\left(\alpha ^{2}-\alpha _{m}^{2}\right)}+G_{-}(\alpha ), \end{align}
Integration contour of Wiener–Hopf additive decomposition for (a) the lower half-plane and (b) the upper half-plane.

where
\begin{align}\varepsilon _{m}&=\begin{cases}1, & m=0,\\2, & m=1,2,3,\ldots, \end{cases} \end{align}
\begin{align}F_{+}(\alpha )&=\sum _{m=0}^{\infty }\frac{{\rm i}\gamma _{2}(\kappa )\varepsilon _{m}\big[\tilde{X}-(-1)^{m}\tilde{Y}\big]}{H\alpha _{m}\big(\kappa ^{2}-\alpha _{m}^{2}\big)(\alpha +\alpha _{m})}+\sum _{n=-\infty }^{\infty }\sum _{m=0}^{\infty }\frac{{\rm i}\gamma _{2}(\kappa _{n})\varepsilon _{m}\big[\tilde{X}_{n}-(-1)^{m}\tilde{Y}_{n}\big]}{H\alpha _{m}\big(\kappa _{n}^{2}-\alpha _{m}^{2}\big)(\alpha +\alpha _{m})}, \\[-9pt] \nonumber \end{align}
\begin{align}F_{-}(\alpha )&=-\sum _{m=0}^{\infty }\frac{{\rm i}\gamma _{2}(\kappa)\varepsilon _{m}\big[\tilde{X}-(-1)^{m}\tilde{Y}\big]}{H\alpha _{m}\big(\kappa ^{2}-\alpha _{m}^{2}\big)(\alpha -\alpha _{m})}-\sum _{n=-\infty }^{\infty }\sum _{m=0}^{\infty }\frac{{\rm i}\gamma _{2}(\kappa _{n})\varepsilon _{m}\big[\tilde{X}_{n}-(-1)^{m}\tilde{Y}_{n}\big]}{H\alpha _{m}\big(\kappa _{n}^{2}-\alpha _{m}^{2}\big)(\alpha -\alpha _{m})}, \end{align}
\begin{align}G_{+}(\alpha )&=\sum _{m=0}^{\infty }\frac{{\rm i}\gamma _{2}(\kappa )\varepsilon _{m}\big[(-1)^{m}\tilde{X}-\tilde{Y}\big]}{H\alpha _{m}\big(\kappa ^{2}-\alpha _{m}^{2}\big)(\alpha +\alpha _{m})}+\sum _{n=-\infty }^{\infty }\sum _{m=0}^{\infty }\frac{{\rm i}\gamma _{2}(\kappa _{n})\varepsilon _{m}\big[(-1)^{m}\tilde{X}_{n}-\tilde{Y}_{n}\big]}{H\alpha _{m}\big(\kappa _{n}^{2}-\alpha _{m}^{2}\big)(\alpha +\alpha _{m})}, \\[-9pt] \nonumber \end{align}
\begin{align}G_{-}(\alpha )&=-\sum _{m=0}^{\infty }\frac{{\rm i}\gamma _{2}(\kappa )\varepsilon _{m}\big[(-1)^{m}\tilde{X}-\tilde{Y}\big]}{H\alpha _{m}\big(\kappa ^{2}-\alpha _{m}^{2}\big)(\alpha -\alpha _{m})}-\sum _{n=-\infty }^{\infty }\sum _{m=0}^{\infty }\frac{{\rm i}\gamma _{2}(\kappa _{n})\varepsilon _{m}\big[(-1)^{m}\tilde{X}_{n}-\tilde{Y}_{n}\big]}{H\alpha _{m}\big(\kappa _{n}^{2}-\alpha _{m}^{2}\big)(\alpha -\alpha _{m})}. \end{align}
According to (2.57) and (2.58), we can obtain
\begin{align}&\overline{p}_{2+}^{r}(\alpha ,0)+\overline{p}_{2-}^{r}(\alpha ,0)=\frac{-\omega ^{2}\rho _{2}}{\gamma _{2}\,{\sin }\, \gamma _{2}H}\left\{\left[\overline{w}_{1+}^{r}(\alpha )\!+\overline{w}_{1-}^{r}(\alpha )\!\right]{\cos }\, \gamma _{2}H\!-\!\left[\overline{w}_{2+}^{r}(\alpha )+\overline{w}_{2-}^{r}(\alpha )\!\right]\right\}\nonumber\\&\quad-\frac{2\omega ^{2}\rho _{2}\alpha }{H}\sum _{m=0}^{\infty }\frac{\varepsilon _{m}\left[\overline{w}_{1+}^{r}(\alpha _{m})-(-1)^{m}\overline{w}_{2+}^{r}(\alpha _{m})\right]}{\alpha _{m}\!\left(\alpha ^{2}-\alpha _{m}^{2}\right)}-F_{+}(\alpha )+F_{-}(\alpha ), \end{align}
\begin{align}&\overline{p}_{2+}^{r}(\alpha ,-H)+\overline{p}_{2-}^{r}(\alpha ,-H)=\frac{-\omega ^{2}\rho _{2}}{\gamma _{2}\,{\sin }\, \gamma _{2}H}\left\{\left[\overline{w}_{1+}^{r}(\alpha )-\overline{w}_{1-}^{r}(\alpha )\right]\right.\nonumber\\&\quad\left.-\left[\overline{w}_{2+}^{r}(\alpha )+\overline{w}_{2-}^{r}(\alpha )\right]{\cos }\, \gamma _{2}H\right\}-\frac{2\omega ^{2}\rho _{2}\alpha }{H}\sum _{m=0}^{\infty }\frac{\varepsilon _{m}\left[(-1)^{m}\overline{w}_{1+}^{r}(\alpha _{m})-\overline{w}_{2+}^{r}(\alpha _{m})\right]}{\alpha _{m}\!\left(\alpha ^{2}-\alpha _{m}^{2}\right)}\nonumber\\&\quad-G_{+}(\alpha )+G_{-}(\alpha ). \end{align}
The governing equations of the corresponding displacement components can be written as
where
Based on (2.21) and (2.43), the Fourier transform of (2.63) can be expressed as
\begin{align}&\left(D_{1}\alpha ^{4}-\omega ^{2}M_{1}-\frac{{\rm i}\omega ^{2}\rho _{1}}{\gamma _{1}}-B\right)\left[\overline{w}_{1+}^{r}(\alpha )+\overline{w}_{1-}^{r}(\alpha )\right]-C\left[\overline{w}_{2+}^{r}(\alpha )+\overline{w}_{2-}^{r}(\alpha )\right]\nonumber\\&\quad=\overline{p}_{2+}^{r}(\alpha ,0)+\overline{p}_{2-}^{r}(\alpha ,0), \\[-9pt] \nonumber \end{align}
\begin{align}&\left(D_{2}\alpha ^{4}-\omega ^{2}M_{2}-\frac{{\rm i}\omega ^{2}\rho _{3}}{\gamma _{3}}-B\right)\left[\overline{w}_{2+}^{r}(\alpha )+\overline{w}_{2-}^{r}(\alpha )\right]-C\left[\overline{w}_{1+}^{r}(\alpha )+\overline{w}_{1-}^{r}(\alpha )\right]\nonumber\\&\quad=-\left[\overline{p}_{2+}^{r}(\alpha ,-H)+\overline{p}_{2-}^{r}(\alpha ,-H)\right]\!. \end{align}
Substituting (2.62) into (2.65), the governing equations of displacement can be derived in the form
\begin{align}&\hat{\boldsymbol{S}}(\alpha )\left\{\!\begin{array}{c} \overline{w}_{1+}^{r}(\alpha )+\overline{w}_{1-}^{r}(\alpha )\\ \overline{w}_{2+}^{r}(\alpha )+\overline{w}_{2-}^{r}(\alpha ) \end{array}\!\right\}=\sum _{m=0}^{\infty }\frac{2\mathrm{i}\gamma _{2}(\kappa)\alpha \varepsilon _{m}}{H\alpha _{m}\!\left(\kappa ^{2}-\alpha _{m}^{2}\right)\left(\alpha ^{2}-\alpha _{m}^{2}\right)}\left\{\!\!\begin{array}{ll} -\tilde{X}+(-1)^{m}\tilde{Y}\\ (-1)^{m}\tilde{X}-\tilde{Y} \end{array}\!\!\right\}\nonumber\\&\quad+\sum _{n=-\infty }^{\infty }\sum _{m=0}^{\infty }\frac{2{\rm i}\gamma _{2}(\kappa _{n})\alpha \varepsilon _{m}}{H\alpha _{m}\!\left(\kappa _{n}^{2}-\alpha _{m}^{2}\right)\left(\alpha ^{2}-\alpha _{m}^{2}\right)}\left\{\!\!\begin{array}{ll} -\tilde{X}_{n}+(-1)^{m}\tilde{Y}_{n}\\ (-1)^{m}\tilde{X}_{n}-\tilde{Y}_{n} \end{array}\!\!\right\}\nonumber\\&\quad+\frac{2\omega ^{2}\rho _{2}\alpha }{H}\sum _{m=0}^{\infty }\frac{\varepsilon _{m}\!\left[\overline{w}_{1+}^{r}(\alpha _{m})-(-1)^{m}\overline{w}_{2+}^{r}(\alpha _{m})\right]}{\alpha _{m}\!\left(\alpha ^{2}-\alpha _{m}^{2}\right)}\left\{\!\!\begin{array}{ll} -1\\ (-1)^{m} \end{array}\!\!\right\}\!,\end{align}
where the elements of matrix
$\hat{\boldsymbol{S}}(\alpha )$
are
It is convenient to write
where
\begin{align}\boldsymbol{K}_{+}(\alpha )&=\frac{1}{2\pi {\rm i}}\int _{\underset{C_{3}}{-\infty }}^{\infty }\frac{\boldsymbol{K}(\xi){\rm d} \xi }{\xi -\alpha }, \end{align}
\begin{align}\boldsymbol{K}_{-}(\alpha )&=-\frac{1}{2\pi {\rm i}}\int _{\underset{C_{4}}{-\infty }}^{\infty }\frac{\boldsymbol{K}(\xi){\rm d} \xi }{\xi -\alpha }. \end{align}
The C 3 and C 4 represent the integral contours with negative and positive infinity as the upper and lower limits. And the contours C 3 and C 4 can be deformed away from the real axis to lie below and above the pole at ξ = α, respectively.
Since the elements of
$\hat{\boldsymbol{S}}(\alpha )$
given by (2.67) are even functions of α, (2.69) can be derived as
and the derivatives are
During the numerical calculation, the integration contour is deformed to lie slightly below the real axis, and the range that meets the error requirements is truncated.
The following Wiener–Hopf additive decomposition is performed:
\begin{align}\frac{2\alpha \boldsymbol{K}(\alpha )}{\alpha ^{2}-\alpha _{m}^{2}}&=\left[\frac{\boldsymbol{K}_{+}(\alpha )+\boldsymbol{K}_{+}(\alpha _{m})}{\alpha +\alpha _{m}}+\frac{\boldsymbol{K}_{+}(\alpha )-\boldsymbol{K}_{+}(\alpha _{m})}{\alpha -\alpha _{m}}\right]\nonumber\\&\quad+\left[\frac{\boldsymbol{K}_{-}(\alpha )-\boldsymbol{K}_{+}(\alpha _{m})}{\alpha +\alpha _{m}}+\frac{\boldsymbol{K}_{-}(\alpha )+\boldsymbol{K}_{+}(\alpha _{m})}{\alpha -\alpha _{m}}\right]\!,\end{align}
where the first term on the right-hand side is analytic in the upper complex half-plane, and the second term is analytic in the lower one.
Multiplying both sides of (2.66) by K(α) and considering (2.72), the Wiener–Hopf additive decomposition can be applied to obtain
\begin{align}&\left\{\!\!\begin{array}{ll} \overline{w}_{1+}^{r}(\alpha )\\ \overline{w}_{2+}^{r}(\alpha ) \end{array}\!\!\right\}=\sum _{m=0}^{\infty }\frac{{\rm i}\gamma _{2}(\kappa )\varepsilon _{m}}{H\alpha _{m}(\kappa ^{2}-\alpha _{m}^{2})}\left[\frac{\boldsymbol{K}_{+}(\alpha )+\boldsymbol{K}_{+}(\alpha _{m})}{\alpha +\alpha _{m}}+\frac{\boldsymbol{K}_{+}(\alpha )-\boldsymbol{K}_{+}(\alpha _{m})}{\alpha -\alpha _{m}}\right]\nonumber\\&\quad\times\left\{\!\begin{array}{ll} -\tilde{X}+(-1)^{m}\tilde{Y}\\ (-1)^{m}\tilde{X}-\tilde{Y} \end{array}\!\right\}+\sum _{n=-\infty }^{\infty }\sum _{m=0}^{\infty }\frac{{\rm i}\gamma _{2}(\kappa _{n})\varepsilon _{m}}{H\alpha _{m}(\kappa _{n}^{2}-\alpha _{m}^{2})}\left[\frac{\boldsymbol{K}_{+}(\alpha )+\boldsymbol{K}_{+}(\alpha _{m})}{\alpha +\alpha _{m}}\right.\nonumber\\&\quad\left.+\frac{\boldsymbol{K}_{+}(\alpha )-\boldsymbol{K}_{+}(\alpha _{m})}{\alpha -\alpha _{m}}\right]\left\{\!\begin{array}{ll} -\tilde{X}_{n}+(-1)^{m}\tilde{Y}_{n}\\ (-1)^{m}\tilde{X}_{n}-\tilde{Y}_{n} \end{array}\!\right\}\nonumber\\&\quad+\frac{\omega ^{2}\rho _{2}}{H}\sum _{m=0}^{\infty }\frac{\varepsilon _{m}\left[\overline{w}_{1+}^{r}(\alpha _{m})-(-1)^{m}\overline{w}_{2+}^{r}(\alpha _{m})\right]}{\alpha _{m}}\left[\frac{\boldsymbol{K}_{+}(\alpha )+\boldsymbol{K}_{+}(\alpha _{m})}{\alpha +\alpha _{m}}\right.\nonumber\\&\quad\left.+\frac{\boldsymbol{K}_{+}(\alpha )-\boldsymbol{K}_{+}(\alpha _{m})}{\alpha -\alpha _{m}}\right]\left\{\!\!\begin{array}{ll} -1\\ (-1)^{m} \end{array}\!\!\right\}\!, \\[-9pt] \nonumber \end{align}
\begin{align}&\left\{\!\!\begin{array}{ll} \overline{w}_{1-}^{r}(\alpha )\\ \overline{w}_{2-}^{r}(\alpha ) \end{array}\!\!\right\}=\sum _{m=0}^{\infty }\frac{{\rm i}\gamma _{2}(\kappa )\varepsilon _{m}}{H\alpha _{m}(\kappa ^{2}-\alpha _{m}^{2})}\left[\frac{\boldsymbol{K}_{-}(\alpha )-\boldsymbol{K}_{+}(\alpha _{m})}{\alpha +\alpha _{m}}+\frac{\boldsymbol{K}_{-}(\alpha )+\boldsymbol{K}_{+}(\alpha _{m})}{\alpha -\alpha _{m}}\right]\nonumber\\&\quad\times\left\{\!\begin{array}{ll} -\tilde{X}+(-1)^{m}\tilde{Y}\\ (-1)^{m}\tilde{X}-\tilde{Y} \end{array}\!\right\}+\sum _{n=-\infty }^{\infty }\sum _{m=0}^{\infty }\frac{{\rm i}\gamma _{2}(\kappa _{n})\varepsilon _{m}}{H\alpha _{m}(\kappa _{n}^{2}-\alpha _{m}^{2})}\left[\frac{\boldsymbol{K}_{-}(\alpha )-\boldsymbol{K}_{+}(\alpha _{m})}{\alpha +\alpha _{m}}\right.\nonumber\\&\quad\left.+\frac{\boldsymbol{K}_{-}(\alpha )+\boldsymbol{K}_{+}(\alpha _{m})}{\alpha -\alpha _{m}}\right]\left\{\!\begin{array}{ll} -\tilde{X}_{n}+(-1)^{m}\tilde{Y}_{n}\\ (-1)^{m}\tilde{X}_{n}-\tilde{Y}_{n} \end{array}\!\right\}\nonumber\\&\quad+\frac{\omega ^{2}\rho _{2}}{H}\sum _{m=0}^{\infty }\frac{\varepsilon _{m}\left[\overline{w}_{1+}^{r}(\alpha _{m})-(-1)^{m}\overline{w}_{2+}^{r}(\alpha _{m})\right]}{\alpha _{m}}\left[\frac{\boldsymbol{K}_{-}(\alpha )-\boldsymbol{K}_{+}(\alpha _{m})}{\alpha +\alpha _{m}}\right.\nonumber\\&\quad\left.+\frac{\boldsymbol{K}_{-}(\alpha )+\boldsymbol{K}_{+}(\alpha _{m})}{\alpha -\alpha _{m}}\right]\left\{\!\!\begin{array}{ll} -1\\ (-1)^{m} \end{array}\!\!\right\}\!. \end{align}
Setting α to α
0, α
1, …, α
M – 1 in (2.73a
), and considering the truncation at
$|n|$
= N, the following matrix equation can be derived:
where the elements of vector
$\tilde{\boldsymbol{w}}$
are
the elements of matrix J include
\begin{align}J_{\zeta \zeta }&=1+\frac{\omega ^{2}\rho _{2}\varepsilon _{\zeta -1}}{H\alpha _{\zeta -1}^{2}}\left[K_{11+}(\alpha _{\zeta -1})+K_{22+}(\alpha _{\zeta -1})+2(-1)^{\zeta }K_{12+}(\alpha _{\zeta -1})\right]\nonumber\\&\quad+\frac{\omega ^{2}\rho _{2}\varepsilon _{\zeta -1}}{H\alpha _{\zeta -1}}\left[K_{11+}^{\prime}(\alpha _{\zeta -1})+K_{22+}^{\prime}(\alpha _{\zeta -1})+2(-1)^{\zeta }K_{12+}^{\prime}(\alpha _{\zeta -1})\right]\!, \\[-9pt] \nonumber \end{align}
\begin{align}J_{\zeta \eta }&=\frac{\omega ^{2}\rho _{2}\varepsilon _{\eta -1}}{H\alpha _{\eta -1}(\alpha _{\zeta -1}+\alpha _{\eta -1})}\left\{K_{11+}(\alpha _{\zeta -1})+K_{11+}(\alpha _{\eta -1})+(-1)^{\zeta }\left[K_{12+}(\alpha _{\zeta -1})\right.\right.\nonumber\\&\quad\left.+K_{12+}(\alpha _{\eta -1})\right]\left.+(-1 )^{\eta }\left[K_{12+}(\alpha _{\zeta -1})+K_{12+}(\alpha _{\eta -1})\right]+(-1)^{\zeta +\eta }\left[K_{22+}(\alpha _{\zeta -1})\right.\right.\nonumber\\&\quad\left.\left.+K_{22+}(\alpha _{\eta -1})\right]\right\}+\frac{\omega ^{2}\rho _{2}\varepsilon _{\eta -1}}{H\alpha _{\eta -1}(\alpha _{\zeta -1}-\alpha _{\eta -1})}\left\{K_{11+}(\alpha _{\zeta -1})-K_{11+}(\alpha _{\eta -1})+(-1)^{\zeta }\right.\nonumber\\&\quad\times\left[K_{12+}(\alpha _{\zeta -1})-K_{12+}(\alpha _{\eta -1})\right]+(-1)^{\eta }\left[K_{12+}(\alpha _{\zeta -1})-K_{12+}(\alpha _{\eta -1})\right]+(-1)^{\zeta +\eta }\nonumber\\&\quad\times\left.\left[K_{22+}(\alpha _{\zeta -1})-K_{22+}(\alpha _{\eta -1})\right]\right\},\quad\eta \neq \zeta ). \end{align}
and the elements of vector
$\tilde{\boldsymbol{F}}$
can be expressed as
\begin{align*}&\tilde{F}_{\zeta }=\sum _{\begin{array}{cc} & \eta =1\\& \eta \neq \zeta \end{array}}^{M}\frac{-{\rm i}\gamma _{2}(\kappa )\varepsilon _{\eta -1}}{H\alpha _{\eta -1}(\kappa ^{2}-\alpha _{\eta -1}^{2})}\left\{2\alpha _{\zeta -1}\left[K_{11+}(\alpha _{\zeta -1})+(-1)^{\zeta }K_{12+}(\alpha _{\zeta -1})\right.\right.\nonumber\\&\quad\left.\left.+(-1 )^{\eta }K_{12+}(\alpha _{\zeta -1})+(-1)^{\zeta +\eta }K_{22+}(\alpha _{\zeta -1})\right]-2\alpha _{\eta -1}\left[K_{11+}(\alpha _{\eta -1})\right.\right.\nonumber\\&\quad\left.\left.+(-1)^{\zeta }K_{12+}(\alpha _{\eta -1})+(-1 )^{\eta }K_{12+}(\alpha _{\eta -1})+(-1)^{\zeta +\eta }K_{22+}(\alpha _{\eta -1})\right]\right\}\frac{\tilde{X}-(-1)^{\eta -1}\tilde{Y}}{\big(\alpha _{\zeta -1}^{2}-\alpha _{\eta -1}^{2}\big)}\nonumber\\&\quad-\frac{{\rm i}\gamma _{2}(\kappa )\varepsilon _{\zeta -1}}{H\alpha _{\zeta -1}\big(\kappa ^{2}-\alpha _{\zeta -1}^{2}\big)}\left[\frac{K_{11+}(\alpha _{\zeta -1})+2(-1)^{\zeta }K_{12+}(\alpha _{\zeta -1})+K_{22+}(\alpha _{\zeta -1})}{\alpha _{\zeta -1}}\right.\nonumber\\&\quad\left.+K_{11+}^{\prime}(\alpha _{\zeta -1})+2(-1)^{\zeta }K_{12+}^{\prime}(\alpha _{\zeta -1})+K_{22+}^{\prime}(\alpha _{\zeta -1})\right]\big[\tilde{X}-(-1)^{\zeta -1}\tilde{Y}\big]\end{align*}
\begin{align*}&\quad-\sum _{n=-N}^{N}\sum _{\begin{array}{cc} \eta =1\\ \eta \neq \zeta \end{array}}^{M}\frac{{\rm i}\gamma _{2}(\kappa _{n})\varepsilon _{\eta -1}}{H\alpha _{\eta -1}\big(\kappa _{n}^{2}-\alpha _{\eta -1}^{2}\big)}\left\{2\alpha _{\zeta -1}\left[K_{11+}(\alpha _{\zeta -1})+(-1)^{\zeta }K_{12+}(\alpha _{\zeta -1})\right.\right.\nonumber\\&\quad\left.\left.+(-1 )^{\eta }K_{12+}(\alpha _{\zeta -1})+(-1)^{\zeta +\eta }K_{22+}(\alpha _{\zeta -1})\right]\right.\left.-2\alpha _{\eta -1}\left[K_{11+}(\alpha _{\eta -1})\right.\right.\nonumber\\&\quad\left.\left.+(-1)^{\zeta }K_{12+}(\alpha _{\eta -1})+(-1 )^{\eta }K_{12+}(\alpha _{\eta -1})+(-1)^{\zeta +\eta }K_{22+}(\alpha _{\eta -1})\right]\right\}\frac{\tilde{X}_{n}-(-1)^{\eta -1}\tilde{Y}_{n}}{\big(\alpha _{\zeta -1}^{2}-\alpha _{\eta -1}^{2}\big)}\nonumber\\\end{align*}
\begin{align}&\quad-\sum _{n=-N}^{N}\frac{{\rm i}\gamma _{2}(\kappa _{n})\varepsilon _{\zeta -1}}{H\alpha _{\zeta -1}\big(\kappa _{n}^{2}-\alpha _{\zeta -1}^{2}\big)}\left[\frac{K_{11+}(\alpha _{\zeta -1})+2(-1)^{\zeta }K_{12+}(\alpha _{\zeta -1})+K_{22+}(\alpha _{\zeta -1})}{\alpha _{\zeta -1}}\right.\nonumber\\&\quad\left.+K_{11+}^{\prime}(\alpha _{\zeta -1})+2(-1)^{\zeta }K_{12+}^{\prime}(\alpha _{\zeta -1})+K_{22+}^{\prime}(\alpha _{\zeta -1})\right]\big[\tilde{X}_{n}-(-1)^{\zeta -1}\tilde{Y}_{n}\big].\end{align}
Considering the above matrix equation, the approximate values of
$\tilde{w}_{\zeta }$
are calculated and substituted into (2.66) to obtain the displacement
$\overline{w}_{1}^{r}(\alpha )$
of the upper plate. With reference to (2.14) and (2.20), the pressure in medium 1 can be expressed as
Then the inverse Fourier transform is performed to obtain
where
According to the stationary phase method, the far-field scattered sound pressure resulting from the rigid baffle can be expressed as
3. Results and discussions
Based on the theoretical derivation, the dynamic effective density and scattered sound pressure of metamaterial plates are calculated. The structural and material parameters are listed in table 1. Figure 3 shows the influence of feedback coefficients on dynamic effective density. According to (2.8), there are two modes of the dynamic effective density for metamaterial plates. As shown in figures 3(a) and 3(b), the in-phase mode indicates that movement directions of the upper and lower plates are the same. And only two vertical resonators are working, which results in two frequency ranges with negative effective density. The anti-phase mode is shown in figures 3(c) and 3(d), which shows that two plates move along opposite directions and only the lateral resonator is active. In this case, the frequency range of negative effective density is determined by the resonant frequency of the lateral resonator.
Dynamic effective density with acceleration feedback control G 1 (V s2 m−1) and displacement feedback control G 2 (V m−1): (a,b) in–phase mode, and (c,d) anti–phase mode.

Structural and material parameters.

Since the active feedback control is applied to vertical resonators, it has no effect on the dynamic effective density for the anti-phase mode. For the in-phase mode, acceleration feedback control can mainly adjust the latter negative region of dynamic effective density. It can be seen from figure 3(a) that positive acceleration feedback control extends the negative region. The displacement feedback control has opposite effects on two regions with negative effective density. As shown in figure 3(b), the previous negative region becomes larger, and the latter becomes smaller with positive displacement feedback control.
In order to be consistent with the submarine environment, the sound velocity and density of water are applied to mediums 1 and 2, and these of air are applied to medium 3. The scattered sound pressure of active metamaterial plates without a rigid baffle is presented in figures 4 and 5. The specular reflection pressure p
sr
and pressure
$p^{e}_{1}$
constitute the scattered sound pressure. And in (2.37a
), the first term of
$p^{e}_{1}$
corresponds to a plane wave consistent with the direction of p
sr
. It can be defined as a correction to p
sr
because of the elastic deformation of the upper plate. For the remaining terms resulting from the periodic four-link mechanisms, only ones with real γ
1(k
n
) can contribute to the far field. When the unit cell size is subwavelength, these terms also act as a correction to p
sr
. During the numerical calculation of (2.37), N = 6 is used to scatter sound pressure.
Influence of acceleration feedback control on scattered sound pressure without rigid baffle with incident frequency 350 Hz: (a–c) θ in = 20°, (d–f) θ in = 40°, (g–i) θ in = 60° and (j–l) θ in = 80°.

Influence of displacement feedback control on scattered sound pressure without rigid baffle with incident angle 70°: (a–c) f = 150 Hz, (d–f) f = 345 Hz, (g–i) f = 350 Hz and (j–l) f = 355 Hz.

Therefore, the scattered sound pressure without rigid baffle is still a plane wave propagating along the direction of specular reflection. Based on the dynamic effective density shown in figure 3, it is known as the frequency range in which active feedback control mainly acts. And the corresponding incident sound wave is applied to obtain the scattered sound pressure with different feedback coefficients. Control parameters G 1 = 0 and G 2 = 0 represent that active feedback control does not work. For acceleration feedback control, it can be seen from figure 4 that the scattered sound pressure is significantly attenuated with G 1 = 0.05 V s2 m−1. Moreover, the control performance is improved with the increase of incident angle.
The scattered sound pressure without rigid baffle can also be effectively reduced by displacement feedback control. As shown in figure 5, the excellent control performance is achieved for the incident frequency 150 Hz with G 2 = 2.5 × 105 V m−1. The scattered sound pressure is significantly reduced at 345 Hz, 350 Hz and 355 Hz, with G 2 = –2.5 × 105 V m−1. For such incident frequencies, the scattered sound pressure increases to a certain extent instead of the opposite feedback coefficient. It corresponds to the influence of active feedback control on negative effective density.
The displacement of active metamaterial plates without rigid baffle is presented in figures 6 and 7 to illustrate the vibroacoustic coupling behaviour. It can be seen that the overall vibration shape of the metamaterial plates corresponds to the distribution of scattered sound pressure. Due to the periodic four-link mechanisms, vibration shapes of the upper and lower plates are no longer harmonic waveforms. Furthermore, the displacement amplitudes of the metamaterial plates are effectively regulated by active feedback control. It is worth noting that when the displacement of the metamaterial plates increases, the scattered sound pressure is reduced at the same time. We know that an amplitude increase of the metamaterial plates will produce a larger pressure
$p^{e}_{1}$
. This means that there is a cancelled interference between
$p^{e}_{1}$
and p
sr
.
Displacement of metamaterial plates without rigid baffle with different acceleration feedback coefficients: (a–c) θ in = 20°, (d–f) θ in = 40°, (g–i) θ in = 60° and (j–l) θ in = 80°.

Displacement of metamaterial plates without rigid baffle with different displacement feedback coefficients: (a–c) f = 150 Hz, (d–f) f = 345 Hz, (g–i) f = 350 Hz and (j–l) f = 355 Hz.

The sound pressure in medium 2 due to the rigid baffle can excite the vibration of the metamaterial plates, which results in the scattered sound pressure in medium 1. Figures 8 and 9 show the sound pressure field scattered by the rigid baffle. The scattered sound pressure includes two cylindrical waves of opposite phase, which propagate from the rigid baffle along 45° and 135° directions. The pressure amplitude deceases with the propagation radius increasing. Moreover, the active feedback control can tune the scattered sound pressure resulting from the rigid baffle. It can be observed from figure 8 that the sound pressure field is effectively attenuated with G 1 = 0.05 V s2 m−1. As shown in figure 9, positive and negative displacement feedback controls achieve excellent control performance within the corresponding frequency range, respectively.
Influence of acceleration feedback control on sound pressure field scattered by rigid baffle: (a–c) f = 330 Hz, (d–f) f = 335 Hz, (g–i) f = 355 Hz and (j–l) f = 360 Hz.

Influence of displacement feedback control on sound pressure field scattered by rigid baffle: (a–c) f = 152 Hz, (d–f) f = 332 Hz, (g–i) f = 340 Hz and (j–l) f = 358 Hz.

Figures 10 and 11 show the sound directivity scattered by rigid baffle with different feedback control coefficients. The sound pressure level (SPL) is calculated in which reference pressure is
$ p_{w} $
= 1 × 10–6 Pa. The sound directivity features two symmetrical lobes, with maximum values occurring at 45° and 135°, and minimum value at 90°. As the plate spacing increases, the scattered SPL in almost all directions becomes much larger for each feedback coefficient. Compared to the structure without active control, the SPL is significantly lower for the appropriate acceleration and displacement feedback coefficients. This indicates that the scattered sound pressure without the rigid baffle has different characteristics from that generated by the rigid baffle. However, the controllable system has a similar regulatory effect on both cases.
Sound directivity scattered by rigid baffle with acceleration feedback control for different plate spacings: (a–c) f = 330 Hz, (d–f) f = 335 Hz, (g–i) f = 355 Hz and (j–l) f = 360 Hz.

Sound directivity scattered by rigid baffle with displacement feedback control for different plate spacings: (a–c) f = 152 Hz, (d–f) f = 332 Hz, (g–i) f = 340 Hz and (j–l) f = 358 Hz.

Influence of feedback coefficients on total scattered sound pressure for different incident angles: (a) θ in = 15°, (b) θ in = 45°, (c) θ in = 75°.

The total scattered sound pressure of metamaterial plates with rigid baffle comprises the superposition of the previous two pressure components. The modulus of total scattered sound pressure is presented in figures 12 and 13 to illustrate the influence of the feedback coefficient. The scattered sound pressure remains at approximately 1 Pa for most frequencies, which indicates that specular reflection dominates. Within the shared effective range, acceleration and displacement feedback controls reduce the scattered sound pressure below 1 Pa when
$ G_{2} \gt 0 $
V s2 m−1 and
$ G_{2} \lt 0 $
V m−1, respectively. Within another effective range for the displacement feedback control, the scattered sound pressure is reduced when
$ G_{2} \gt 0 $
V m−1. Pressure
$p^{e}_{1}$
in (2.11a
) generated by the elastic motion without the rigid baffle can result in the sharp peak of total scattered sound pressure. This phenomenon results from the obvious amplification of structure amplitude with opposite control coefficients. Furthermore, the performance of active feedback control improves as the unit cell length decreases. And the effective ranges of acceleration and displacement feedback controls shift to lower-frequency regions.
Influence of feedback coefficients on total scattered sound pressure for different unit cell lengths: (a)
$L_{x}$
= 0.1 m, (b)
$L_{x}$
= 0.2 m, (c)
$L_{x}$
= 0.3 m.

Figure 14 illustrates the influence of plate spacing on the total scattered sound pressure. It can be observed that as the frequency increases, the modulus of total scattered sound pressure shows obvious fluctuations. This indicates that the scattered sound pressure due to the rigid baffle becomes almost the same as the magnitude of the specular reflection pressure. A larger plate spacing results in greater fluctuation of total scattered sound pressure, which indicates that the scattered sound pressure due to the rigid baffle is large enough to be considered. Moreover, the fluctuation of total scattered sound pressure initially increases before decreasing with the incident angle becoming larger.
Influence of plate spacing on total scattered sound pressure: (a) θ in = 15°, (b) θ in = 45°, (c) θ in = 75°.

In order to support the theoretical derivation, the finite element simulation is performed, and the mesh model is shown in figure 15(a). The actual measurement is the total sound pressure, which includes the superposition of the incident and scattered sound pressures. Therefore, the controlled total SPL with incident angle 45° is presented in figures 15(b) and 15(c). It can be observed that the total SPL with active feedback control shows excellent agreement between the theoretical and FEM cases. Furthermore, the total SPL results with different incident angles are provided in figure 16 to verify the accuracy of numerical calculation. The vibration shapes of the metamaterial plates are obtained by FEM, which indicates significantly larger displacements within low frequencies. We can see that the displacement of the metamaterial plates becomes larger with the incident angle increasing.
Comparison between theory and FEM results: (a) finite element model, (b) total SPL with acceleration control, and (c) total SPL with displacement control.

Theory and FEM results of total SPL for different incident angles: (a) θ in = 25°, (b) θ in = 45°, (c) θ in = 65°, (d) θ in = 85°.

Then the acoustic scattering experiment is performed to support the theoretical derivation. Due to experimental constraints, the metamaterial plates are located in an anechoic room for acoustic testing in an air environment. Furthermore, waterproof packaging for the control system should be considered during the engineering application. Then the control circuits can be integrated and located inside the pressure hull. The experimental devices and overall layout are illustrated in figure 17(a)–(e). A loudspeaker array is used to generate incident plane waves. The total sound pressure is received by the microphones and acoustic data acquisition card. The theoretical and experimental results of total SPL without control are shown in figure 17(f), calculated based on the reference pressure p a = 2 × 10–5 Pa. It can be seen that the overall trend of the experimental results is basically consistent with the theoretical ones. And the experimental and theoretical values are in close agreement for most frequencies.
Acoustic scattering experiment: (a) experimental devices, (b) active metamaterial plates with rigid baffle, (c) feedback regulator, (d) four-link mechanism, (e) local resonator with accelerometer, and (f) theoretical and experimental results of total SPL without active control.

Furthermore, active feedback control is considered, and the experimental signal transmission process is shown in figure 18. The acceleration of vertical resonator
$m_{v1}$
is converted into a voltage signal by the accelerometer. With integration operations, the signal processor can obtain the displacement information. The adjustable gain for the acceleration and displacement signals is achieved by the feedback regulator in which an amplification circuit is included. Then the output voltage is applied to the coil to generate the magnetic interaction between vertical resonators. Figure 19 shows the SPL with active feedback control for both experiment and theory. For different feedback coefficients, the experimental and theoretical results are in good agreement within most frequency regions. The deviation between the experiment and theory for the first two frequencies is mainly due to the sound absorption conditions of the anechoic chamber. And due to the limit periodicity of metamaterial plates, boundary conditions during the experiment have some differences from those in the theoretical derivation.
Electrical circuit and signal transmission process of active feedback control.

Theoretical and experimental results of total SPL with active feedback control: (a) G 1 = 0.1 V s2 m−1, (b) G 1 = −0.1 V s2 m−1, (c) G 2 = 2 × 105 V m−1, (d) G 2 = −2 × 105 V m−1.

4. Conclusions
In this work, metamaterial plates with active feedback control are investigated to show the dynamic effective density and scattered sound pressure. The negative region of dynamic effective density is determined by resonant frequencies of local resonators, which can be tuned by acceleration and displacement feedback control. Within the low-frequency region, the total scattered sound pressure is mainly the specular reflection pressure after amplitude correction, and the pressure resulting from the rigid baffle is relatively small. Through proper feedback coefficients, the total scattered sound pressure in the negative region of dynamic effective density can be effectively reduced. Moreover, the results of the FEM and experiment are consistent with numerical results, which support the theoretical derivation. This research wishes to provide assistance in suppressing low-frequency acoustic scattering for underwater vehicles.
Supplementary movies
Supplementary movies are available at https://doi.org/10.1017/jfm.2026.11177.
Acknowledgements
The authors wish to express gratitude for the support provided by the National Natural Science Foundation of China (grant nos 12425203 and 12021002).
Declaration of interests
The authors report no conflict of interest.
Appendix A
Considering the system response with harmonic excitation, we can obtain
where
$ U_v $
1,
$ U_v $
2 and U
l
are the displacement amplitudes, and I is the current amplitude.
Substituting (A1)–(A4) into (2.2) and (2.3), the corresponding algebraic equations can be obtained. And the displacements of the vertical and lateral resonators can be derived as
where
\begin{align}A_{2}&=2k_{v1}-m_{v1}\omega ^{2}+2k_{v2}+\frac{B_{L}\left(-\omega ^{2}G_{1}+G_{2}+{\rm i}\omega B_{L}\right)}{R_{e}-{\rm i}\omega L_{e}}-A_{1}\left(2k_{v2}+\frac{{\rm i}\omega B_{L}^{2}}{R_{e}-{\rm i}\omega L_{e}}\right)\!. \end{align}
Furthermore, the internal force can be expressed as
Based on the small displacement assumption and the geometric relation in the four-link mechanism, the displacement of the link node can be given as
and (2.5) is obtained by substituting (A5)–(A7) and (A12) into (A10) and (A11).























