The baffle influence on sound radiation characteristics of a plate

. The acoustic radiation characteristics of the baffle plates and unbaffle plates are calculated and compared by single-layer potential and double-layer potential. Based on the boundary integral equation, the sound pressure integral equation of the baffle and the baffle are deduced respectively. According to the boundary compatibility condition, the sound pressure and the vibration velocity of the plates are obtained. Further, the dynamic equation of the structure is substituted into the vibration equation in the form of the baffle plate and the baffle plate. The sound pressure difference and the displacement of a plate surface are in the form of the vibration mode superposition and the acoustic radiation impedance of the double integral form is obtained, which determines vibration mode coefficient and sound radiation parameters. The effect of the baffle on the acoustic radiation characteristics of the thin plate is analyzed by comparing the acoustic radiation parameters with the simple and simple rectangular plate in water.


Introduction
Many of the structures used in engineering can be treated as a finite plate approximately, and the acoustic radiation characteristics such as sound efficiency and sound power are widely concerned by engineers. When analyzing the acoustic radiation characteristics of a thin plate, a simple rectangular plate is usually used as the solution model. Not only because of the simple vibration pattern of simple-supported rectangular thin plate, it is convenient to use analytic solution to express its surface vibration velocity and sound radiation characteristic parameters, and its analytical solution can be compared with numerical calculation method such as finite element method to reveal the structural sound radiation general rule.
In the early study, the acoustic radiation characteristics of the simply supported rectangular thin plate are usually placed on an infinite baffle. Only the single-layer potential is needed to be calculated, and the integral term exhibits weak singularity, which can simplify the computational complexity. In the 1960s, Maidanik [1] first proposed the approximate equation of the acoustic radiation resistance of a simple rectangular plate, which provided a theoretical basis for later researchers. Wallace [2] then used the integral of the far field sound intensity to deduce a series of approximate integral equations of acoustic radiation resistance, and successfully solved the modal sound radiation power of the structure with an critical frequency. Heckl [3] uses Fourier transform to study the acoustic radiation problem of the plate in the wavenumber segment. Leppington [4] obtained several approximate equations to solve the vibration mode efficiency of the large wavenumber domain, but the above scholars neglected the influence of crossmodal on the sound power. To this end, using the modal radiation efficiency and taking into account the coupling between the modals, Snyder and Tanaka [5] calculated the low-frequency structural sound power. Li and Gibeling [6][7] used the integral transformation method to transform the acoustic radiation resistance from the quadratic integral form into the form of double integral and successfully transformed into a form of single integral, and obtained the self-radiation resistance, mutual-radiation resistance. For the acoustic radiation problem of underwater plate, because the need to consider the role of fluid on the structure, it can be attributed to the sound and vibration coupling problem. Crighton [8][9] analyzes the acoustic radiation of infinite plate in water under point excitation. Leibowitz [10] proposed a method for calculating the acoustic properties of finite plates in water. M.L.Rumerman [11] studied the effect of water load presence on the sound radiation efficiency. B.E. Sandman [12] further validated the correctness of the theory of plate vibration and acoustic radiation under fluid loading by experiments.
However, in the actual project, the infinite baffle is not present, so there is the need to study the sound properties of unbaffled plates. Williams [13] used the fast Fourier transform (FFT) to give the sound pressure of the simply supported thin plate in the air by the iterative operation. However, the convergence of the acoustic radiation impedance in high-order modes is poor. Atalla [14] calculated the sound characteristics of an unbaffled plate in air under any boundary conditions using Kirchhoff-Helmholtz integral equation, but ignores the impact of pressure fluctuations on both sides of the plate resulting in large error in high frequency.
Oppenheimer and Dubrowsky [15] used experiments to modify the acoustic radiation parameters of baffled plates to match unbaffled plates and gave empirical formulas for the acoustic radiation of an unbaffled plate.
In this paper, the acoustic radiation characteristics of the baffled and unbaffled plates are analyzed. The sound pressure integral equations of the baffled and unbaffled plates are deduced by the boundary integral equation, and sound pressure and velocity in double integral form are obtained according to boundary compatibility condition. Further, the structural dynamic equation is substituted into the sound pressure equation of the baffled and unbaffled plates. Through expanding sound pressure difference and the displacement of plates in the form of the vibration mode superposition, the acoustic radiation impedance in the double integral form is obtained to solve the vibration modal coefficient, and determine the sound radiation characteristics. The effect of the baffle on the acoustic radiation characteristics to a plate is analyzed by comparing the acoustic radiation parameters with the simply rectangular plate in water.

Plate dynamics equations and fundamentals of acoustics
The acoustic radiation characteristics of simply supported rectangular thin plates are studied in this paper. The density of the plate is s There is an excitation force ) , ( y x F of angular frequency  which is perpendicular to the plate shown in figure 1.
From the classical dynamics, the transverse vibration equation of the thin plate is shown as is the bending stiffness of the plate, E is Yong's modulus, h is the plate thickness and indicates the mass in an unit area.
The displacement of a simple rectangular plate can be expressed as a superposition of the following vibration modes: where mn A is the modal velocity amplitude and ) , ( y x mn  is the modal shape function which can be expressed as .External forces can also be expressed as follows similarly: where mn F is the modal force amplitude and is the difference between the sound pressure on the upper and lower surfaces of the plate shown as is the sound pressure acting on the lower surface of the plate, ) , ( y x p  is the sound pressure acting on the higher surface of the plate.  ( , ) p x y is the sound pressure at any point in the medium , k is the wave number, c is the velocity of sound. Based on Euler equation, the compatibility condition is: where f  is the density of the medium Using the Kirchhoff-Helmholtz integral formula to an infinite space of a bounding plate structure, the sound pressure at any point in the space can be expressed as The normal direction of the upper and lower surfaces of the thin plate is opposite, and for this purpose the uniform direction of Green function is defined as positive direction of z axial. The coordinates are shown in figure   2.
Take Fourier inverse transformation to the above equation x y x y dx dy dxdy is defined as the radiation impedance of ( , ) pq mn .
Through coordinate transformation, Suppose can be transformed into a double integral form The transformed acoustic radiation impedance is substituted into Eq.(15), a matrix form can be expressed as , F is external force array, In the formula,   The figure above shows that the presence of the baffle causes the acoustic radiation impedance to be different, which causes the change of resonance frequency of the structure. The existence of the baffle causes the resonance frequency of the structure to be further reduced, and the sound radiation power of the structure is increased. This is due to the existence of the baffle, that the flat surface compresses one side medium which can not flow to the other side medium, resulting in structural vibration energy being more effectively converted into sound energy, thereby increasing the energy of acoustic radiation.So at the same frequency, the radiation power and efficiency of a baffled plate are higher than the unbaffled plate. The radiation from the baffled plate is similar to that of the monopole, and the acoustic radiation of the unbaffle plate is similar to that produced by the dipole. The acoustic radiation resistance of the baffled plate is higher than that of the unbaffled plate, and the acoustic resistance is equivalent to the additional mass on the surface of the structure. Therefore, it can be seen from the figure that the mean square velocity of the baffle plate is lower than that of the unbaffled one.

Conclusion
By using the boundary integral equation, the formulas of the acoustic radiation of the baffled plate and the unbaffled one are established respectively. Their respective acoustic radiation impedances are analyzed, and the radiated sound power, mean square velocity and the radiation efficiency of them are compared. It can be concluded that: (1) The presence of the baffle causes the sound radiation power and efficiency of the structure to be improved, similar to the conversion of the structure of the dipole radiation to the monopole radiation; (2) The presence of the baffle also changes the resonance frequency of structures in heavy medium, resulting in a reduced resonant frequency of the structure; (3) In general, the mean square velocity of the baffled plate is lower than the unbaffled one.