Design of HoneycombMicroperforated Structure with Adjustable Sound Absorption Performance

In this work, a double-layer honeycomb microperforated structure with adjustable back-cavity’s height is designed based on cylinder honeycomb structure andmicroperforated panel (MPP).,e sound absorption performance can be changed by adjusting the height of back-cavity. ,us, a better absorption performance is achieved by changing the position of the inner MPP. Acoustic impedance of the structure was calculated based on transfer matrix method. ,e sound absorption coefficient of the structure was obtained by finite element method (FEM). Meanwhile, the 3D printing technology was used to produce the experimental samples. ,e experimental results demonstrate that the sound absorption coefficient of the structure is greater than 0.8 in the range of 750–1250Hz, greater than 0.9 in the range of 2297–3592Hz, and above 0.5 in the range of 500–4000Hz. In addition, the feasibility of achieving adjustable sound absorption by means of changing the height of the back-cavity is verified by theoretical, simulation, and experimental results. ,e structure proposed in this work can realize the function of wide-band and better sound absorption performance by changing the position of the inner MPP, which can be applied to effectively reduce different frequencies noise.


Introduction
e ubiquitous noise problem has become a significant issue in today's society. From daily living environment to military equipment, structures and equipment used for noise reduction can be seen everywhere, such as noise reduction headphones [1,2], sound insulation layer of room walls [3,4], noise reduction in aircraft combustion chambers [5], and acoustic liner [6,7]. Honeycomb microperforated panel (HMPP) structure is one of the noise reduction structures [8]. It combines simple structures and significant noise reduction performance of MPP with high specific strength and good fatigue resistance. Meanwhile, it forms a lightweight but high-strength composite structure which can reduce noise in harsh environments [9,10]. However, the sound absorption performance of this noise reducer is limited by its own structure, materials, and other factors.
In recent years, in order to improve its noise reduction performance, scholars have made improvements in different aspects. Kim et al. used the analysis method, revealed the influence of each layer of perforated panels on the sound absorption performance, and came up with an improvement measure [11]. Gai et al. designed an L-shaped back-cavity to enhance the sound-absorbing performance of the structure [12]. Zhang et al. designed a corrugated honeycomb microperforated composite structure by changing the internal propagation path of sound waves, which could effectively improve the noise reduction performance [13]. Xie et al. designed a honeycomb microperforated structure with different apertures, which refined the sound absorption performance [14]. By means of parallel mechanical impedance, Zhao improved the sound absorption performance of MPP in low frequency [15]. Scholars have done a lot of research on acoustic superstructure, metamaterials and made great progress, such as phonon crystal, chiral material, and local resonance acoustic metamaterial [16][17][18][19]. Xiong used optimization algorithm to design a multiarea honeycomb microperforated structure, which greatly improves the sound absorption bandwidth of the structure. However, the optimized parameters cannot be accurately processed and manufactured [20]. Although the sound absorption performance of HMPP will be better after optimizing the parameters, the sound absorption performance of the structure is determined completely. Even more, due to the difficulties in manufacturing, it could not be easily applied on a large scale.
In the process of increasing the noise reduction performance of the structure, scholars found that if the sound absorption performance of the structure was designed to be adjustable, the noise reduction capability of the structure would be improved. Shao designed an adjustable muffler based on the membrane structure [21]. Zhang et al. designed a honeycomb microperforated structure which can adjust the structure's sound absorption performance with the appropriate shape of inner panel. By changing the perforation rate, the purpose of adjustable sound absorption performance was achieved [22]. Ning et al. designed an adjustable resonance unit to control the width of the resonant band gap [23].
To sum up, there are many ways to improve the acoustic absorption performance of the MPP structure, but most research results are difficult to popularize in practical applications, such as too complex structures, production and manufacturing difficulties, and expensive defects. erefore, in order to broaden the sound absorption frequency band of the sound absorber, under the premise that the size of the structure does not change, a double-layer HMPP with adjustable back-cavity height is designed and fabricated, which can efficiently improve the sound absorption performance and broaden the application range.
In the remainder of the paper, geometric model of the structure is designed and theoretical results are calculated by using two methods in Section 2. Next, Section 3 calculates the simulation results of the structure. Moreover, experimental results of samples are measured in Section 4 and compared with theoretical and simulation results. Finally, Section 5 concludes this work.

Structural Acoustic Impedance
Although the single-layer structure with microperforated sound absorber and honeycomb core has excellent sound absorption performance, its sound absorption frequency band is slightly narrower than the double-layer perforated panel. Figure 1 shows a single-layer HMPP structure. e structure is composed of MPP on the upper surface, a honeycomb core in the middle, and a bottom panel below [24]. e improved cellular structure of the honeycomb core is proposed to obtain better and adjustable sound absorption performance in this work. Its detailed structure is shown in Figure 2.
Under purpose of no change for the structure size, the screw and inner MPP are set in the unit cell of single-layer honeycomb structure which is shown in Figures 2(a) and 2(b). e inner thread of the MPP in the honeycomb core is matched with the screw and shown in Figure 2(c). e sectional view of the improved honeycomb core structure is shown in Figure 2 e inner MPP is equipped with 1 mm thickness and 5 mm height tubular structure to increase the contact area between the groove and honeycomb core, so as to better limit freedom within the rest of the direction of MPP. e diameter of the screw and bottom panel contact position is slightly smaller than that of the screw so that the screw is guaranteed to rotate freely while the inner microperforated panel moves up and down. As shown in Figure 2(g), the knob is connected with the screw inside the honeycomb core. Meanwhile, there is a pointer pointing to the scale values on the structure, which is convenient to control the rising height of the inner MPP. e outer wall of the knob has four grooves for better stress during rotation. e inner MPP's position can change a screw pitch when the knob is rotated one circle. To be specific, the inner MPP rises by 1 mm when the knob is rotated a circle clockwise. Rotating the knob can change the position of the inner MPP, which further changes the height of the back-cavity of the structure and ultimately changes the frequency corresponding to the maximum sound absorption coefficient of the structure. So, the cavity heights D 1 and D 2 described in this work have a wide range of variation.

Acoustoelectric Analogy.
According to Ma's theory of double-layer MPP and the method of acoustoelectric analogy, the equivalent sound source is the open circuit sound pressure and internal impedance which are 2p and ρ 0 c 0 . e acoustic impedance inside the honeycomb core can be regarded as the acoustic impedance of a doublelayer MPP [25]. e double-layer MPP and its equivalent circuit diagram are shown in Figure 3.where r i is the relative resistance of MPP i , m i is the relative mass of MPP i , j is the imaginary unit, ω is the circular frequency of the incident noise, Z Di is the relative impedance of cavity, D i is the height of cavity, ρ 0 is the density of air, c is the sound velocity in air at room temperature, f is the frequency of sound, μ is the kinetic viscosity coefficient for air, t i is the panel thickness, d i is the perforation diameter, p i is the perforation rate, and k i is the characteristic coefficient of MPP i .   Shock and Vibration So, the relative impedance of the structure can be written as Z: where MPP 1 is the upper MPP, MPP 2 is the inner MPP, D i is the height of cavity, D 1 is the length between MPP 1 and MPP 2 , and D 2 is the length between MPP 2 and the bottom panel.

Transfer Matrix.
Another method which can achieve calculation requirements is the transfer matrix method [25]. e matrix used in this work can be written as follows:   Shock and Vibration where T MPPi is the transfer matrix of MPP i , Z MPPi is the impedance of MPP i , T Di is the transfer matrix of the cavity, and k is the wave number. e total transfer matrix of the structure in this work can be written as en, the relative impedance can be written as follows: Sound absorption coefficient α of normal incidence can be got by substituting equations (2) and (5) into the following equation: (6) Figure 4 shows the theoretical results of acoustoelectric analogy and transfer matrix model in MATLAB. e structure parameters used are shown in Table 1. e heights of cavity D 1 and 2 D are 30 mm. As shown in Figure 4, when calculating the sound absorption coefficient of the double-layer MPP, the transfer matrix method is closer to the experiment results than the acoustoelectric analogy method; Zhang and Zhao had studied the differences between these two theoretical models. e neglect of the sound mass of the cavity leads to the inaccuracy of the acoustoelectric analogy method when considering above a certain frequency [22,26]. erefore, in the following study of this work, the sound absorption coefficient of the structure will be calculated by transfer matrix method.
It can be seen from the above theoretical formulas and Figure 5 that the impedance of the structure is affected by the parameters of MPP i and the cavity heights D 1 and 2 D . Assuming that the parameters of MPP are determined, the values of D 1 and 2 D directly affect the impedance value of the structure. e result in Figure 5 indeed confirms that the sound absorption performance of the structure can be adjusted by changing the values of D 1 and 2 D .

Finite Element Simulation
Finite element method (FEM) is an effective method to study complex structures. e pressure acoustic (frequency domain) module of COMSOL Multiphysics 5.4 software is used for simulation analysis in this work. e parameters of MPP and screw parameters are, respectively, shown in Tables 1  and 2. e parameters of the heights D 1 and D 2 are shown in Table 3. e model is divided into free tetrahedral meshes by using the meshing function in the software. e unit cell contains 50556 domain elements, 6840 boundary elements, and 700 edge elements [27]. e simulation grid is shown in Figures 6(a) and 6(b).
In simulation, position adjustment of the inner MPP leads to the height change of D 1 and D 2 , finally achieving the purpose of changing the sound absorption performance. Figure 7 is the simulation result of sound absorption coefficient.
According to the simulation results of Figure 7, there are two peaks of sound absorption coefficient curves between 0 Hz and 4000 Hz in simulation. e first peaks of curves appear near 1000 Hz, while the second ones move greatly with the changing of the position of inner MPP. e frequency corresponding to the peak value of the second absorption coefficient moves from 2000 Hz to 3000 Hz when D 2 changes from 15 mm to 45 mm, In addition, it shows a much better improvement of sound absorption coefficient with the value greater than 0.8 in the range of 600 Hz-1100 Hz, greater than 0.9 in the range of 2250-3250 Hz, and greater than 0.6 in the range of 700-3500 Hz.

Experimental Verification
In this work, the double-layer HMPP with adjustable height of back-cavity is fabricated by 3D printing technology. As shown in Figure 8, the honeycomb core structure with a diameter of 29 mm is selected for the sample which can be measured in an impedance tube according to ISO 10534-2 [28]. e detail parameters of samples are shown in Tables 1  and 2. e sound absorption coefficient of the sample is obtained by the method of exchanging channels which means measuring the sound pressure at two fixed positions and the transfer function of the two channels. e total sound pressure at microphone 1 and microphone 2 is calculated as follows: where p I is the amplitude of incident wave sound pressure, d is the distance between microphone 2 and the front surface of the specimen, p R is the amplitude of reflected wave sound pressure, and x is the distance between two microphones. e transfer functions of incident H 1 and reflected waves H R can be expressed as. 6 Shock and Vibration e transfer function of the total sound field H 12 can be obtained from p 1 and p 2 . us, the sound absorption coefficient α can be written as.
e AWA6290T transfer function acoustic absorption coefficient measurement system of Hangzhou Aihua Instrument Co., Ltd., is adopted in this work. e test schematic diagram and measurement system are shown in Figure 9. e sensitivity of the sensor needs to be calibrated before the experiment begins so that the sound pressure amplitude at frequency of 1000 Hz is about 94 db. In this test, the adjusted sensor sensitivity level is − 48.55. Figure 10 shows the experimental sound absorption performance of the sample when D 2 changes from 15 mm to 45 mm. e test frequencies range from 0 to 4000 Hz for samples. It can be found in Figure 10 that the sound absorption coefficient changed with the changing of position of inner MPP. Furthermore, there are two peaks of sound absorption coefficient between 500 Hz and 4000 Hz for samples, and when D 2 changes from 15 mm to 45 mm, the sound absorption coefficient of the structure in the range of 2297-3592 Hz is above 0.9 with the width of 1295 Hz and is above 0.5 in the range of 500-4000 Hz.
e frequencies corresponding to the first peak and the second peak of the sound absorption coefficient are extracted from the results. Considering the inner MPP at different heights from the bottom surface, the results can be drawn as Figure 11.     Shock and Vibration As shown in Figure 11, the first peak frequency of the sound absorption coefficient moves to the low frequencies when the height of the cavity 1 becomes smaller and the height of the cavity 2 increases; however, the frequency corresponding to the peak of the second sound absorption coefficient moves to the high frequency. It proves that the sound absorption performance of this structure can be controlled by changing the height of the back-cavity.
It is obviously seem in Figure 12 that theoretical and simulation results have the same changes as the experimental results. Meanwhile, in the theoretical and simulation results, the first maximum sound absorption coefficient corresponds to the same frequency, but the maximum sound absorption coefficient is slightly lower than the experimental results. For the frequency corresponding to the second maximum absorption coefficient, theoretical and experiment results have the same frequency, while the simulation results move slightly to the low frequency, and the maximum sound absorption coefficient is the same in the three methods.
As shown in Figure 13, the frequencies corresponding to the first peak and the second peak in theoretical and simulation results of samples were respectively compared with the experimental results. ere are errors in the 3D printed MPP, so the actual size of holes on MPP is slightly larger than the predetermined size, which made the resonant frequencies of the structure move towards high frequencies.
But the results of the three methods show that the structure can be used to adjust the sound absorption performance, so as to indirectly expand the sound absorption band.

Discussion and Conclusions
e main factors affecting the sound absorption performance of MPP are the cavity depth, aperture, thickness, and perforation rate of MPP. If the other three parameters are held constant, the resonant frequency of the structure is changed by changing the cavity depth, so as to achieve the purpose of adjustable sound absorption performance.
(1) According to the theory of double-layer MPP, the change of the peak frequency of sound absorption coefficient depends on the change of the back-cavity's height of the structure, which shows the feasibility of adjustable sound absorption performance of the structure (2) e height of the inner MPP can be controlled and adjusted by turning the knob to achieve the purpose of adjusting the sound absorption performance. e sound absorption coefficient of the structure in the range of 750-1250 Hz is above 0.8, 2297-3592 Hz is above 0.9, and 500-4000 Hz is above 0.5.
(3) eoretical, simulation, and experimental results have the same change rules. As the diameters of the microhole produced by 3D printing in the experiment are bigger than those of the theoretical and simulation results, the peak frequency in the experiment moves to the high frequency. Nonetheless, the sound absorption performance of the structure can still be predicted through theoretical or simulation results.  (4) e sound absorption performance of HMPP can be controlled and adjusted by adding a screw which controls the position of the inner MPP. When the sound absorber structures' parameters are limited, compared with the traditional sound absorption structure, the double-layer HMPP with adjustable sound absorption performance can be more widely applied.

Data Availability
Relevant research data can be obtained upon request from the corresponding author.

Conflicts of Interest
e authors declare that they have no conflicts of interest.