CN116261089A - Structural-acoustic device and verification method for large non-reciprocal transfer of sound energy using NES - Google Patents

Structural-acoustic device and verification method for large non-reciprocal transfer of sound energy using NES Download PDF

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CN116261089A
CN116261089A CN202211596414.6A CN202211596414A CN116261089A CN 116261089 A CN116261089 A CN 116261089A CN 202211596414 A CN202211596414 A CN 202211596414A CN 116261089 A CN116261089 A CN 116261089A
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金江明
肖岳鹏
黄景啸
卢奂采
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Zhejiang University of Technology ZJUT
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Abstract

利用NES实现声能量大非互易传递的结构声装置,包括声腔一、管道、声腔二、薄膜和声腔三,管道两端分别与声腔一和声腔二连接,声腔二居中安装在声腔三的顶面上,两声腔连接的居中处设有通孔三;薄膜通过夹具安装在声腔二与声腔三之间,并完全遮蔽通孔三。声腔一与声腔三侧面分别开有通孔一和通孔二,正向激励时体积速度声源通过通孔一与声腔一连接,并密闭通孔二;反向激励时体积速度声源通过通孔二与声腔三连接,并密闭通孔一。本发明还提供利用NES实现声能量大非互易传递的结构声装置的验证方法。本发明利用正向激励时发生靶向能量转移,而反向激励时没有靶向能量转移的特性,实现了声能量的大非互易传递,为管道低频噪声控制提供了方法。

Figure 202211596414

Using NES to realize the structure-acoustic device with large and non-reciprocal transmission of sound energy, including acoustic chamber 1, pipe, acoustic chamber 2, membrane and acoustic chamber 3, the two ends of the pipe are respectively connected with acoustic chamber 1 and acoustic chamber 2, and acoustic chamber 2 is installed in the center on the top of acoustic chamber 3 On the surface, a through hole three is provided in the middle of the connection between the two sound chambers; the film is installed between the sound chamber two and the sound chamber three through a clamp, and completely covers the through hole three. There are through holes 1 and 2 respectively on the sides of the acoustic chamber 1 and the three sides of the acoustic chamber. When positively excited, the volume velocity sound source is connected to the acoustic chamber 1 through the through hole 1, and the through hole 2 is sealed; Hole two is connected with acoustic chamber three, and through hole one is airtight. The invention also provides a verification method for a structure-acoustic device that utilizes the NES to realize the non-reciprocal transfer of large acoustic energy. The invention utilizes the property that targeted energy transfer occurs during forward excitation, but there is no targeted energy transfer during reverse excitation, thereby realizing large non-reciprocal transfer of acoustic energy and providing a method for pipeline low-frequency noise control.

Figure 202211596414

Description

利用NES实现声能量大非互易传递的结构声装置及验证方法Structural acoustic device and verification method for realizing large non-reciprocal transmission of acoustic energy using NES

技术领域Technical Field

本发明涉及利用声人工结构调控声能量控制技术,尤其涉及利用NES实现声能量大非互易传递的结构声装置及验证方法。The present invention relates to a technique for controlling acoustic energy by using an acoustic artificial structure, and in particular to a structural acoustic device and a verification method for realizing large non-reciprocal transmission of acoustic energy by using NES.

背景技术Background Art

在弹性介质中,由于缺乏实现电磁整流偏置的效应,弹性介质系统都严格遵循瑞利互易定理。系统的互易性阻碍了声波不对称单向传递的实现,如果实现声能量的不对称大非互易传递,就可以设计出声二极管、声单向透镜、隔声体和拓扑绝缘体等新型声学元件。在电磁学中,由于二极管的出现,引发了第二次工业革命,上述新型声学元件同样在声通信、声纳系统结构设计、噪声控制、成像控制等领域具有广泛的应用价值,是结构声学、声学超材料领域的研究热点。In elastic media, due to the lack of electromagnetic rectification bias effects, elastic medium systems strictly follow the Rayleigh reciprocity theorem. The reciprocity of the system hinders the realization of asymmetric unidirectional transmission of sound waves. If the asymmetric large non-reciprocal transmission of sound energy is realized, new acoustic elements such as acoustic diodes, acoustic one-way lenses, sound insulators and topological insulators can be designed. In electromagnetism, the emergence of diodes triggered the second industrial revolution. The above-mentioned new acoustic elements also have a wide range of application values in acoustic communications, sonar system structure design, noise control, imaging control and other fields, and are research hotspots in the fields of structural acoustics and acoustic metamaterials.

非线性声系统具有分岔、随系统能量变化的共振频率等线性系统不具有的特性,因而可实现声能量的大非互易传递。Cochelin等学者研究了结构声系统中的能量转移现象,将大振幅非线性薄膜与线性声系统相耦合,构建了非线性能量阱实现了声系统中的靶向目标能量转移,研究表明利用非线性能量阱机理可以实现声波的定向传递,为低频噪声控制提供了新的方法。Nonlinear acoustic systems have characteristics that linear systems do not have, such as bifurcation and resonance frequency that changes with system energy, which can achieve large non-reciprocal transfer of acoustic energy. Cochelin and other scholars studied the energy transfer phenomenon in structural acoustic systems, coupled large-amplitude nonlinear films with linear acoustic systems, and constructed nonlinear energy wells to achieve targeted energy transfer in acoustic systems. The study showed that the use of nonlinear energy well mechanisms can achieve directional transmission of sound waves, providing a new method for low-frequency noise control.

公开号为CN 112857553 A发明的耦合薄膜非线性能量阱的声腔的降噪性能实验装置和方法,结合薄膜非线性能量阱的靶向能量传递特性进一步地抑制了声腔内的低频噪声。公开号为CN 114758642 A发明的一种基于电声非线性能量阱的薄板辐射噪声抑制装置,通过增加电声结构并优化设计背腔体积、扬声器背腔体积、反馈增益等参数,使非线性能量阱最优靶能量传递现象的激励下阈值减小了19倍。但以上方案主要研究的都是声能量单方向的抑制或传递,并未对声能量的双向传递进行研究。The noise reduction performance experimental device and method of the acoustic cavity coupled with a thin film nonlinear energy well invented with publication number CN 112857553 A, combined with the targeted energy transfer characteristics of the thin film nonlinear energy well, further suppress the low-frequency noise in the acoustic cavity. The thin plate radiation noise suppression device based on the electroacoustic nonlinear energy well invented with publication number CN 114758642 A, by increasing the electroacoustic structure and optimizing the back cavity volume, the speaker back cavity volume, the feedback gain and other parameters, reduces the threshold under excitation of the nonlinear energy well optimal target energy transfer phenomenon by 19 times. However, the above schemes mainly study the unidirectional suppression or transfer of acoustic energy, and do not study the bidirectional transfer of acoustic energy.

公开号为CN 114613349 A发明的实现声能量非互易传递的Duffing振子型结构声装置,利用非线性薄膜简化为单自由的Duffing振子在弱非线性区的非线性共振和强非线性区的分岔机理实现了声能量的非互易传递,为空气介质中声能量非对称传递提供了新思路,但该方案是单自由度系统的声能量传递,未开展两自由度或多自由度系统具有非线性能量阱机理的声非互易能量传递的研究。The Duffing oscillator-type structural acoustic device for realizing nonreciprocal transfer of acoustic energy, invented with publication number CN 114613349 A, realizes nonreciprocal transfer of acoustic energy by utilizing the nonlinear resonance of a Duffing oscillator simplified to a single freedom in a weak nonlinear region and the bifurcation mechanism in a strong nonlinear region, which provides a new idea for asymmetric transfer of acoustic energy in an air medium. However, this scheme is for acoustic energy transfer in a single-degree-of-freedom system, and no research has been conducted on acoustic nonreciprocal energy transfer in a two-degree-of-freedom or multi-degree-of-freedom system with a nonlinear energy sink mechanism.

发明内容Summary of the invention

为现有声能量非互易传递装置研究的进一步发展,提出了一种利用NES实现声能量大非互易传递的结构声装置,为空气介质中实现声能量非互易传递以及管道低频噪声控制提供了新方法。For the further development of the existing research on non-reciprocal transfer of acoustic energy, a structural acoustic device which uses NES to achieve large non-reciprocal transfer of acoustic energy is proposed, which provides a new method for achieving non-reciprocal transfer of acoustic energy in air medium and controlling low-frequency noise in pipelines.

本发明采用的技术方案是:利用NES实现声能量大非互易传递的结构声装置,包括管道(2)、薄膜(5)、以及不同尺寸的正方体声腔一(1)、正方体声腔二(4)和正方体声腔三(6),所述管道(2)的长度远远大于其直径,管道(2)的两端分别与声腔一(1)、声腔二(4)密封连接,且声腔一(1)通过管道(2)与声腔二(4)连通;The technical solution adopted by the present invention is: a structural acoustic device that uses NES to achieve large non-reciprocal transmission of acoustic energy, comprising a pipe (2), a film (5), and a cube acoustic cavity one (1), a cube acoustic cavity two (4), and a cube acoustic cavity three (6) of different sizes, wherein the length of the pipe (2) is much greater than its diameter, and the two ends of the pipe (2) are respectively sealed and connected to the acoustic cavity one (1) and the acoustic cavity two (4), and the acoustic cavity one (1) is connected to the acoustic cavity two (4) through the pipe (2);

所述声腔二(4)居中叠放安装在声腔三(6)的顶面上,声腔二(4)顶面设有便于安装薄膜(5)的端盖(3),端盖(3)与声腔二(4)密封连接;声腔二(4)与声腔三(6)连接的壁面居中处开有连通声腔二(4)和声腔三(6)的通孔三(H3),通孔三(H3)内密封连接有薄膜夹具(7);薄膜夹具(7)包括环形上夹盖和环形下夹盖,薄膜(5)夹持在上夹盖和下夹盖之间,薄膜夹具(7)和薄膜(5)完全遮蔽通孔三(H3);所述声腔一(1)远离管道(2)的一侧表面开有通孔一(H1),声腔三(6)朝向管道(2)的一侧表面开有通孔二(H2);声腔一(1)、管道(2)、声腔二(4)和声腔三(6)里传输介质均为空气;The second acoustic cavity (4) is centrally stacked and installed on the top surface of the third acoustic cavity (6). The top surface of the second acoustic cavity (4) is provided with an end cover (3) for facilitating the installation of a film (5), and the end cover (3) is sealed and connected to the second acoustic cavity (4). A through hole ( H3 ) for connecting the second acoustic cavity (4) and the third acoustic cavity (6) is opened in the center of the wall surface where the second acoustic cavity (4) and the third acoustic cavity (6) are connected, and a film clamp (7) is sealed and connected in the third through hole ( H3 ). The film clamp (7) includes an annular upper clamp cover and an annular lower clamp cover, and the film (5) is clamped between the upper clamp cover and the lower clamp cover, and the film clamp (7) and the film (5) completely cover the third through hole ( H3 ). The first through hole ( H1 ) is opened on the surface of the first acoustic cavity (1) away from the pipeline (2), and the second through hole ( H2 ) is opened on the surface of the third acoustic cavity (6) facing the pipeline (2). ); the transmission medium in the acoustic cavity 1 (1), the pipe (2), the acoustic cavity 2 (4) and the acoustic cavity 3 (6) is air;

当正向激励时体积速度声源通过通孔一(H1)与声腔一(1)连接,并密闭通孔二(H2);正向激励时所述装置内部形成内共振,声能量发生靶向目标能量转移,从线性振子管道(2)不可逆且高效地传递至非线性振子薄膜(5),并由薄膜(5)向声腔三(6)传递,在声腔三(6)中可以测得较高的响应声压;When positively excited, the volume velocity sound source is connected to the acoustic cavity one ( 1 ) through the through hole one (H1), and the through hole two ( H2 ) is sealed; when positively excited, internal resonance is formed inside the device, and the acoustic energy undergoes targeted energy transfer, and is irreversibly and efficiently transferred from the linear oscillator pipe (2) to the nonlinear oscillator film (5), and then transferred from the film (5) to the acoustic cavity three (6), and a higher response sound pressure can be measured in the acoustic cavity three (6);

当反向激励时体积速度声源通过通孔二(H2)与声腔三(6)连接,并密闭通孔一(H1),且输入声波波长远大于正方体声腔一(1)、正方体声腔二(4)和正方体声腔三(6)的尺寸;反向激励时所述装置未发生内共振,大部分声能量仍停留在声腔三(6)中,声能量传递效率低,在声腔一(1)中测得的响应声压较低;当正向激励和反向激励时系统响应存在较大差异时,所述装置存在大非互易性。When reversely excited, the volume velocity sound source is connected to the sound cavity three (6) through the through hole two ( H2 ), and the through hole one ( H1 ) is sealed, and the wavelength of the input sound wave is much larger than the size of the cube sound cavity one (1), the cube sound cavity two (4) and the cube sound cavity three (6); when reversely excited, the device does not have internal resonance, most of the sound energy still remains in the sound cavity three (6), the sound energy transfer efficiency is low, and the response sound pressure measured in the sound cavity one (1) is low; when there is a large difference in the system response during forward excitation and reverse excitation, the device has a large non-reciprocity.

进一步,所述管道(2)采用不锈钢制成,管道(2)内径的截面半径为17.5mm,管道(2)的长度为1.75m;所述声腔一(1)、声腔二(4)和声腔三(6)均采用亚克力制成,且均呈正方体形;声腔一(1)和声腔二(4)的腔体边长均为0.2m,声腔三(6)的腔体边长为0.3m;薄膜(5)采用硅胶制成,薄膜(5)的厚度为0.1mm,薄膜(5)的半径为19mm。Furthermore, the pipe (2) is made of stainless steel, the cross-sectional radius of the inner diameter of the pipe (2) is 17.5 mm, and the length of the pipe (2) is 1.75 m; the acoustic cavity 1 (1), the acoustic cavity 2 (4), and the acoustic cavity 3 (6) are all made of acrylic and are all in a cube shape; the cavity side lengths of the acoustic cavity 1 (1) and the acoustic cavity 2 (4) are both 0.2 m, and the cavity side length of the acoustic cavity 3 (6) is 0.3 m; the film (5) is made of silicone, the thickness of the film (5) is 0.1 mm, and the radius of the film (5) is 19 mm.

进一步,给定管道的半径Rt、管道的长度L、薄膜的半径Rm、薄膜的密度ρm、薄膜的厚度h、薄膜的泊松比v、薄膜的杨氏模量E、薄膜的阻尼系数η、正方形声腔一的体积V1、正方形声腔二的体积V2、正方形声腔三的体积V3、声源激励幅值Qs、激励频率ωs、空气密度ρa和声速c0,进行理论建模,然后进行仿真和实验验证,步骤如下:Furthermore, given the radius R t of the pipe, the length L of the pipe, the radius R m of the film, the density ρ m of the film, the thickness h of the film, the Poisson's ratio v of the film, the Young's modulus E of the film, the damping coefficient η of the film, the volume V 1 of the square acoustic cavity one, the volume V 2 of the square acoustic cavity two, the volume V 3 of the square acoustic cavity three, the sound source excitation amplitude Q s , the excitation frequency ω s , the air density ρ a and the sound speed c 0 , theoretical modeling is performed, and then simulation and experimental verification are performed. The steps are as follows:

1)分别建立管道、非线性薄膜和声腔三类组成单元的理论模型、三类单元耦合而成的系统控制方程表达式以及声能量的非互易量的判定式:1) The theoretical models of the three types of components, namely, pipes, nonlinear membranes and acoustic cavities, the expressions of the system control equations coupled by the three types of units, and the determination formula of the non-reciprocal amount of acoustic energy are established respectively:

管道的理论模型:由于管道的长度远大于其直径,因此可被假设为一维波导,分别假设ua和px为管道末端声介质位移和管道内声压,结合声波波动方程和Rayleigh-Ritz简化,并引入空气阻尼系数cf,可获得管道控制方程:Theoretical model of the pipeline: Since the length of the pipeline is much larger than its diameter, it can be assumed to be a one-dimensional waveguide. Assuming u a and p x are the displacement of the acoustic medium at the end of the pipeline and the sound pressure in the pipeline respectively, combining the acoustic wave equation and Rayleigh-Ritz simplification, and introducing the air damping coefficient c f , the pipeline control equation can be obtained:

Figure BDA0003993010820000041
Figure BDA0003993010820000041

其中,in,

Figure BDA0003993010820000051
Figure BDA0003993010820000051

薄膜的理论模型:采用Von Karman非线性板壳模型,结合Kelvin-Viogt粘弹性本构模型,建立薄膜的控制方程;然后采用抛物线函数作为薄膜一阶模态振型函数,通过Rayleigh-Ritz降价建模方法,获得非线性薄膜的控制方程:Theoretical model of the film: The Von Karman nonlinear plate-shell model is combined with the Kelvin-Viogt viscoelastic constitutive model to establish the control equation of the film; then the parabolic function is used as the first-order modal vibration function of the film, and the control equation of the nonlinear film is obtained through the Rayleigh-Ritz price reduction modeling method:

Figure BDA0003993010820000052
Figure BDA0003993010820000052

其中qm为薄膜中心的横向位移,pm为薄膜所受的声压;f1m为有预应力时薄膜的线性一阶固有频率,由实验测量获得,f0m为无预应力的薄膜的共振频率;k1和k3分别为薄膜的线性刚度和立方非线性刚度,Sm为薄膜的面积;ma0是薄膜大振幅运动带动周边空气运动的附加质量,根据实验结果确定;其他参数由下列公式给出:Where qm is the lateral displacement of the center of the film, pm is the sound pressure on the film; f1m is the linear first-order natural frequency of the film with prestress, obtained by experimental measurement, f0m is the resonant frequency of the film without prestress; k1 and k3 are the linear stiffness and cubic nonlinear stiffness of the film, respectively, Sm is the area of the film; ma0 is the additional mass of the surrounding air driven by the large amplitude motion of the film, determined according to experimental results; other parameters are given by the following formulas:

Figure BDA0003993010820000053
Figure BDA0003993010820000053

声腔的理论模型:当声波波长远大于声腔尺寸,刚性壁封闭声腔内的声压可认为是均布的,可获得声腔内声压方程:Theoretical model of acoustic cavity: When the wavelength of the sound wave is much larger than the size of the acoustic cavity, the sound pressure in the acoustic cavity closed by the rigid wall can be considered to be uniformly distributed, and the sound pressure equation in the acoustic cavity can be obtained:

Figure BDA0003993010820000054
Figure BDA0003993010820000054

结合公式(1)、(3)和(5)可得系统控制方程:Combining formulas (1), (3) and (5), we can get the system control equation:

正向激励时:When positively motivated:

Figure BDA0003993010820000061
Figure BDA0003993010820000061

Figure BDA0003993010820000062
Figure BDA0003993010820000062

反向激励时:When the reverse incentive:

Figure BDA0003993010820000063
Figure BDA0003993010820000063

Figure BDA0003993010820000064
Figure BDA0003993010820000064

其中,in,

Figure BDA0003993010820000065
Figure BDA0003993010820000065

正向激励时正方形声腔三(6)为响应声腔,反向激励时正方形声腔一(1)为响应声腔,其腔内声压分别为:When the square sound cavity is positively excited, the third square sound cavity (6) is the response sound cavity, and when the square sound cavity is negatively excited, the first square sound cavity (1) is the response sound cavity. The sound pressures in the cavities are:

Figure BDA0003993010820000066
Figure BDA0003993010820000066

Figure BDA0003993010820000067
Figure BDA0003993010820000067

装置系统声能量传递的互易量NR由下式定义:The reciprocity NR of the acoustic energy transfer of the device system is defined by the following formula:

Figure BDA0003993010820000068
Figure BDA0003993010820000068

可根据公式(11)判定该装置是否是大非互易系统。Whether the device is a large non-reciprocal system can be determined according to formula (11).

本发明的原理是:在固定频率激励下,管道2的一阶声模态共振可简化为单自由度线性振子,薄膜5的大变形振动可看作为非线性刚度占主要的非线性振子,管道2与薄膜5通过声腔二4中的空气以弱线性刚度进行耦合,因此该结构声系统可简化由线性振子和非线性振子构成的两自由度系统。通过理论研究分析,可以发现:在一定声源高激励范围内,正向激励时系统内部形成内共振,声能量发生靶向目标能量转移,从线性振子管道2不可逆且高效地传递至非线性振子薄膜5,并由薄膜5向正方形声腔三6传递,在正方形声腔三6中可以测得较高的响应声压;而反向激励时系统未发生内共振,大部分声能量仍停留在正方形声腔三6中,声能量传递效率低,在正方形声腔一1中测得的响应声压较低;由于正向和反向激励时系统响应存在显著差异,因此该声系统存在大非互易性。The principle of the present invention is that under fixed frequency excitation, the first-order acoustic modal resonance of the pipe 2 can be simplified to a single-degree-of-freedom linear oscillator, the large deformation vibration of the film 5 can be regarded as a nonlinear oscillator with a dominant nonlinear stiffness, and the pipe 2 and the film 5 are coupled with weak linear stiffness through the air in the acoustic cavity 2 4, so the structural acoustic system can simplify the two-degree-of-freedom system composed of a linear oscillator and a nonlinear oscillator. Through theoretical research and analysis, it can be found that within a certain range of high excitation of the sound source, an internal resonance is formed inside the system during forward excitation, and the acoustic energy undergoes targeted energy transfer, which is irreversibly and efficiently transferred from the linear oscillator pipe 2 to the nonlinear oscillator film 5, and then transferred from the film 5 to the square acoustic cavity 3 6, and a higher response sound pressure can be measured in the square acoustic cavity 3 6; while the system does not undergo internal resonance during reverse excitation, most of the acoustic energy still remains in the square acoustic cavity 3 6, the acoustic energy transfer efficiency is low, and the response sound pressure measured in the square acoustic cavity 1 is low; since there is a significant difference in the system response during forward and reverse excitation, the acoustic system has a large non-reciprocity.

根据声学系统中互易性的定义,本发明提出采用互换激励点和响应点的位置,然后根据两点响应声压比值来验证系统非互易性的方法,具体为在系统输入声源强度不变的情况下,把激励输入点和响应输出点的位置互换,分别测量互换前后响应点处的声压,然后通过这两处响应声压的比值,确定非互易量的大小,当两者的比值较大时,可以判定其为大非互易系统。According to the definition of reciprocity in an acoustic system, the present invention proposes a method of interchanging the positions of an excitation point and a response point, and then verifying the non-reciprocity of the system based on the ratio of the response sound pressures at the two points. Specifically, when the intensity of the system input sound source remains unchanged, the positions of the excitation input point and the response output point are interchanged, and the sound pressures at the response points before and after the interchange are measured respectively. Then, the size of the non-reciprocal quantity is determined by the ratio of the response sound pressures at the two points. When the ratio between the two is large, it can be determined that it is a large non-reciprocal system.

本发明的有益效果是:本发明利用结构声系统中的非线性能量阱机理,构建了能够实现声能量大非互易传递的结构声装置,为空气介质中实现声能量非互易传递提供了新的设计思路,在管道低频噪声控制领域具有重大应用价值。The beneficial effects of the present invention are as follows: the present invention utilizes the nonlinear energy sink mechanism in the structural acoustic system to construct a structural acoustic device capable of realizing large non-reciprocal transfer of acoustic energy, provides a new design idea for realizing non-reciprocal transfer of acoustic energy in the air medium, and has great application value in the field of pipeline low-frequency noise control.

附图说明BRIEF DESCRIPTION OF THE DRAWINGS

图1是本发明装置的结构示意图。FIG. 1 is a schematic structural diagram of the device of the present invention.

图2是本发明薄膜夹具的结构示意图。FIG. 2 is a schematic structural diagram of a film clamp of the present invention.

图3是本发明装置简化的两自由度系统示意图。FIG. 3 is a simplified two-degree-of-freedom system schematic diagram of the device of the present invention.

图4是本发明装置在相同频率,不同源强激励下薄膜平均速度的实验和仿真结果曲线对比图。FIG. 4 is a curve comparison of the experimental and simulation results of the average film velocity of the device of the present invention under the same frequency and different source strength excitation.

图5是本发明装置在相同频率,不同源强激励下响应声压的实验和仿真结果曲线对比图。FIG. 5 is a curve comparison of the experimental and simulation results of the response sound pressure of the device of the present invention under the same frequency and different source strength excitation.

图6是本发明装置在相同频率,不同源强激励下声能量非互易量的实验和仿真结果曲线对比图。FIG. 6 is a curve comparison diagram of the experimental and simulation results of the non-reciprocal amount of acoustic energy of the device of the present invention under the same frequency and different source intensity excitations.

附图标记说明:1、声腔一;2、管道;3、端盖;4、声腔二;5、薄膜;6、声腔三;7、薄膜夹具。Explanation of the accompanying drawings: 1. Acoustic cavity one; 2. Pipe; 3. End cover; 4. Acoustic cavity two; 5. Film; 6. Acoustic cavity three; 7. Film clamp.

具体实施方式DETAILED DESCRIPTION

下面将结合附图对本发明专利的技术方案进行清楚、完整地描述,显然,所描述的实施例是本发明一部分实施例,而不是全部的实施例。基于本发明中的实施例,本领域普通技术人员在没有做出创造性劳动前提下所获得的所有其他实施例,都属于本发明保护的范围。The technical solution of the present invention will be described clearly and completely below in conjunction with the accompanying drawings. Obviously, the described embodiments are part of the embodiments of the present invention, not all of them. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

在本发明的描述中,需要说明的是,如出现术语“中心”、“上”、“下”、“左”、“右”、“竖直”、“水平”、“内”、“外”等指示的方位或位置关系为基于附图所示的方位或位置关系,仅是为了便于描述本发明和简化描述,而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作,因此不能理解为对本发明的限制。此外,如出现术语“第一”、“第二”、“第三”仅用于描述目的,而不能理解为指示或暗示相对重要性。In the description of the present invention, it should be noted that the orientations or positional relationships indicated by the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc. are based on the orientations or positional relationships shown in the drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as limiting the present invention. In addition, the terms "first", "second", and "third" are only used for descriptive purposes and cannot be understood as indicating or implying relative importance.

在本发明的描述中,需要说明的是,除非另有明确的规定和限定,如出现术语“安装”、“相连”、“连接”应做广义理解,例如,可以是固定连接,也可以是可拆卸连接,或一体地连接;可以是机械连接,也可以是电连接;可以是直接相连,也可以通过中间媒介间接相连,可以是两个元件内部的连通。对于本领域的普通技术人员而言,可以具体情况理解上述术语在本发明中的具体含义。In the description of the present invention, it should be noted that, unless otherwise clearly specified and limited, the terms "installed", "connected", and "connected" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or it can be indirectly connected through an intermediate medium, or it can be the internal communication of two components. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

如图1所示,所述装置由声腔一1、管道2、声腔二4、薄膜5和声腔三6组成;管道2两端分别与声腔一1和声腔二4进行密封连接,声腔二4居中安装在声腔三6的顶面上,声腔二4顶面设有端盖3用以方便安装薄膜5,端盖3与声腔二4通过密封圈和螺栓进行密封连接;声腔二4与声腔三6连接的居中处设有通孔三H3,薄膜5通过夹具安装在声腔二4与声腔三6之间,并完全遮蔽通孔三H3,薄膜夹具7通过螺钉和密封圈与声腔进行密封连接。声腔一1与声腔三6侧面分别开有通孔一H1和通孔二H2,正向激励时体积速度声源通过通孔一H1与声腔一1连接,并密闭通孔二H2,反向激励时体积速度声源通过通孔二H2与声腔三6连接,并密闭通孔一H1As shown in Figure 1, the device consists of a sound cavity 1, a pipe 2, a sound cavity 4, a film 5 and a sound cavity 3 6; the two ends of the pipe 2 are sealed and connected to the sound cavity 1 1 and the sound cavity 2 4 respectively, the sound cavity 2 4 is centrally installed on the top surface of the sound cavity 3 6 , the top surface of the sound cavity 2 4 is provided with an end cover 3 for convenient installation of the film 5, and the end cover 3 and the sound cavity 2 4 are sealed and connected by a sealing ring and a bolt; a through hole three H3 is provided in the center of the connection between the sound cavity 2 4 and the sound cavity 3 6, the film 5 is installed between the sound cavity 2 4 and the sound cavity 3 6 by a clamp, and completely covers the through hole three H3 , and the film clamp 7 is sealed and connected to the sound cavity by screws and a sealing ring. A through hole 1 H1 and a through hole 2 H2 are respectively opened on the sides of the sound cavity 1 1 and the sound cavity 3 6. During forward excitation, the volume velocity sound source is connected to the sound cavity 1 1 through the through hole 1 H1 and the through hole 2 H2 is sealed. During reverse excitation, the volume velocity sound source is connected to the sound cavity 3 6 through the through hole 2 H2 and the through hole 1 H1 is sealed.

声腔和管道里的传输介质均为空气。管道2材料为不锈钢,管道2内径的截面半径为17.5mm,管道2长度为1.75m;声腔材料均为亚克力,且均为正方形,其中声腔一1和声腔二4的腔体边长皆为0.2m,声腔三6的腔体边长为0.3m;薄膜5材料为硅胶,薄膜5厚度为0.1mm,薄膜5的作用半径为19mm。The transmission medium in the acoustic cavity and the pipe is air. The pipe 2 is made of stainless steel, the cross-sectional radius of the inner diameter of the pipe 2 is 17.5 mm, and the length of the pipe 2 is 1.75 m; the acoustic cavity is made of acrylic and is square, where the side lengths of the acoustic cavity 1 and the acoustic cavity 2 4 are both 0.2 m, and the side length of the acoustic cavity 3 6 is 0.3 m; the film 5 is made of silicone, the thickness of the film 5 is 0.1 mm, and the effective radius of the film 5 is 19 mm.

如图2所示,所述薄膜夹具7由上下两部分构成,薄膜均匀平整地安装在夹具中间,以减少安装时产生的预应力,同时为保证薄膜边界条件的稳定性,需要在夹具内环安装橡胶垫;然后夹具上下两部分通过螺钉进行紧固。As shown in Figure 2, the film clamp 7 consists of two parts, the upper and lower parts. The film is installed evenly and flatly in the middle of the clamp to reduce the prestress generated during installation. At the same time, in order to ensure the stability of the film boundary conditions, a rubber pad needs to be installed on the inner ring of the clamp; then the upper and lower parts of the clamp are fastened by screws.

如图3所示,在固定频率激励下,管道2的一阶声模态共振可简化为单自由度线性振子,薄膜5的大变形振动可看作为非线性刚度占主要的非线性振子,管道2与薄膜5通过声腔二4中的空气以弱线性刚度进行耦合,因此该结构声系统可简化由线性振子和非线性振子构成的两自由度系统。在一定声源强度激励范围内,正向激励时系统内部形成内共振,声能量发生靶向目标能量转移,从线性振子管道2不可逆且高效地传递至非线性振子薄膜5,并由薄膜5向声腔三6传递,在声腔三6中可以测得较高的响应声压;反向激励时系统未发生内共振,大部分声能量仍停留在声腔三6中,声能量传递效率低,在声腔一1中测得的响应声压较低;由于正向和反向激励时系统响应存在显著差异,因此该声系统存在大非互易性。As shown in Fig. 3, under fixed frequency excitation, the first-order acoustic modal resonance of pipe 2 can be simplified to a single-degree-of-freedom linear oscillator, and the large deformation vibration of film 5 can be regarded as a nonlinear oscillator dominated by nonlinear stiffness. Pipe 2 and film 5 are coupled with weak linear stiffness through the air in acoustic cavity 2 4, so the structural acoustic system can be simplified to a two-degree-of-freedom system composed of a linear oscillator and a nonlinear oscillator. Within a certain range of sound source intensity excitation, an internal resonance is formed inside the system during forward excitation, and the acoustic energy undergoes targeted energy transfer, which is irreversibly and efficiently transferred from the linear oscillator pipe 2 to the nonlinear oscillator film 5, and then transferred from the film 5 to the acoustic cavity 3 6, where a higher response sound pressure can be measured; during reverse excitation, the system does not undergo internal resonance, and most of the acoustic energy remains in the acoustic cavity 3 6, with low acoustic energy transfer efficiency, and the response sound pressure measured in the acoustic cavity 1 is low; since there is a significant difference in the system response during forward and reverse excitation, the acoustic system has a large non-reciprocity.

基于权利要求1或2所述的利用NES实现声能量大非互易传递的结构声装置验证方法,其特征在于:给定管道2的半径Rt、管道2的长度L、薄膜5的半径Rm、薄膜5的密度ρm、薄膜5的厚度h、薄膜5的泊松比υ、薄膜5的杨氏模量E、薄膜5的阻尼系数η、正方形声腔一1的体积V1、正方形声腔二4的体积V2、正方形声腔三6的体积V3、声源激励幅值Qs、激励频率ωs、空气密度ρa和声速c0,进行理论建模,然后进行仿真和实验验证,步骤如下:The structural acoustic device verification method for realizing large non-reciprocal transfer of acoustic energy by using NES according to claim 1 or 2 is characterized in that: given the radius R t of the pipe 2, the length L of the pipe 2, the radius R m of the film 5, the density ρ m of the film 5, the thickness h of the film 5, the Poisson's ratio υ of the film 5, the Young's modulus E of the film 5, the damping coefficient η of the film 5, the volume V 1 of the square acoustic cavity 1, the volume V 2 of the square acoustic cavity 2, the volume V 3 of the square acoustic cavity 3, the sound source excitation amplitude Q s , the excitation frequency ω s , the air density ρ a and the sound speed c 0 , theoretical modeling is performed, and then simulation and experimental verification are performed, and the steps are as follows:

1)分别建立管道、非线性薄膜和声腔三类组成单元的理论模型、三类单元耦合而成的系统控制方程表达式以及声能量的非互易量的判定式:1) The theoretical models of the three types of components, namely, pipes, nonlinear membranes and acoustic cavities, the expressions of the system control equations coupled by the three types of units, and the determination formula of the non-reciprocal amount of acoustic energy are established respectively:

管道的理论模型:由于管道的长度远大于其直径,因此可被假设为一维波导,分别假设ua和px为管道末端声介质位移和管道内声压,结合声波波动方程和Rayleigh-Ritz简化,并引入空气阻尼系数cf,可获得管道控制方程:Theoretical model of the pipeline: Since the length of the pipeline is much larger than its diameter, it can be assumed to be a one-dimensional waveguide. Assuming u a and p x are the displacement of the acoustic medium at the end of the pipeline and the sound pressure in the pipeline respectively, combining the acoustic wave equation and Rayleigh-Ritz simplification, and introducing the air damping coefficient c f , the pipeline control equation can be obtained:

Figure BDA0003993010820000111
Figure BDA0003993010820000111

其中,in,

Figure BDA0003993010820000112
Figure BDA0003993010820000112

薄膜的理论模型:采用Von Karman非线性板壳模型,结合Kelvin-Viogt粘弹性本构模型,建立薄膜的控制方程;然后采用抛物线函数作为薄膜一阶模态振型函数,通过Rayleigh-Ritz降价建模方法,获得非线性薄膜的控制方程:Theoretical model of the film: The Von Karman nonlinear plate-shell model is combined with the Kelvin-Viogt viscoelastic constitutive model to establish the control equation of the film; then the parabolic function is used as the first-order modal vibration function of the film, and the control equation of the nonlinear film is obtained through the Rayleigh-Ritz price reduction modeling method:

Figure BDA0003993010820000121
Figure BDA0003993010820000121

其中qm为薄膜中心的横向位移,pm为薄膜所受的声压;f1m为有预应力时薄膜的线性一阶固有频率,由实验测量获得,f0m为无预应力的薄膜的共振频率;k1和k3分别为薄膜的线性刚度和立方非线性刚度,Sm为薄膜的面积;ma0是薄膜大振幅运动带动周边空气运动的附加质量,根据实验结果确定;其他参数由下列公式给出:Where qm is the lateral displacement of the center of the film, pm is the sound pressure on the film; f1m is the linear first-order natural frequency of the film with prestress, obtained by experimental measurement, f0m is the resonant frequency of the film without prestress; k1 and k3 are the linear stiffness and cubic nonlinear stiffness of the film, respectively, Sm is the area of the film; ma0 is the additional mass of the surrounding air driven by the large amplitude motion of the film, determined according to experimental results; other parameters are given by the following formulas:

Figure BDA0003993010820000122
Figure BDA0003993010820000122

声腔的理论模型:当声波波长远大于声腔尺寸,刚性壁封闭声腔内的声压可认为是均布的,可获得声腔内声压方程:Theoretical model of acoustic cavity: When the wavelength of the sound wave is much larger than the size of the acoustic cavity, the sound pressure in the acoustic cavity closed by the rigid wall can be considered to be uniformly distributed, and the sound pressure equation in the acoustic cavity can be obtained:

Figure BDA0003993010820000123
Figure BDA0003993010820000123

结合公式(1)、(3)和(5)可得系统控制方程:Combining formulas (1), (3) and (5), we can get the system control equation:

正向激励时:When positively motivated:

Figure BDA0003993010820000124
Figure BDA0003993010820000124

Figure BDA0003993010820000125
Figure BDA0003993010820000125

反向激励时:When the reverse incentive:

Figure BDA0003993010820000131
Figure BDA0003993010820000131

Figure BDA0003993010820000132
Figure BDA0003993010820000132

其中,in,

Figure BDA0003993010820000133
Figure BDA0003993010820000133

正向激励时正方形声腔三(6)为响应声腔,反向激励时正方形声腔一(1)为响应声腔,其腔内声压分别为:When the square sound cavity is positively excited, the third square sound cavity (6) is the response sound cavity, and when the square sound cavity is negatively excited, the first square sound cavity (1) is the response sound cavity. The sound pressures in the cavities are:

Figure BDA0003993010820000134
Figure BDA0003993010820000134

Figure BDA0003993010820000135
Figure BDA0003993010820000135

装置系统声能量传递的互易量NR由下式定义:The reciprocity NR of the acoustic energy transfer of the device system is defined by the following formula:

Figure BDA0003993010820000136
Figure BDA0003993010820000136

可根据公式(11)判定该装置是否是大非互易系统。Whether the device is a large non-reciprocal system can be determined according to formula (11).

本发明分别建立管道、非线性薄膜和声腔三类组成单元的理论模型、三类单元耦合而成的系统控制方程表达式以及声能量的非互易量的判定式:The present invention establishes theoretical models of three types of components, namely, pipelines, nonlinear films and acoustic cavities, expressions of system control equations formed by coupling the three types of units, and determination formulas for the non-reciprocal amount of acoustic energy:

本发明中管道的长度远大于其直径,因此可被假设为一维波导,分别假设ua和px为管道末端声介质位移和管道内声压,结合声波波动方程和Rayleigh-Ritz简化,并引入空气阻尼系数cf,可获得管道控制方程为公式(1)。In the present invention, the length of the pipeline is much larger than its diameter, so it can be assumed to be a one-dimensional waveguide. Assuming u a and p x are the acoustic medium displacement at the end of the pipeline and the sound pressure in the pipeline respectively, combining the acoustic wave equation and Rayleigh-Ritz simplification, and introducing the air damping coefficient c f , the pipeline control equation can be obtained as formula (1).

本发明中薄膜的振动是大幅度的,线性理论将不再适用,因此采用Von Karman非线性板壳模型,结合Kelvin-Viogt粘弹性本构模型,建立薄膜的控制方程;然后采用抛物线函数作为薄膜一阶模态振型函数,通过Rayleigh-Ritz降价建模方法,获得非线性薄膜的控制方程为公式(3)。In the present invention, the vibration of the film is large, and the linear theory will no longer be applicable. Therefore, the Von Karman nonlinear plate-shell model is used in combination with the Kelvin-Viogt viscoelastic constitutive model to establish the control equation of the film; then a parabolic function is used as the first-order modal vibration function of the film, and the control equation of the nonlinear film is obtained as formula (3) through the Rayleigh-Ritz price reduction modeling method.

本发明中声腔尺寸远小于声波波长,因此刚性壁封闭声腔内的声压可认为是均布的,可获得声腔内声压方程为公式(5)。In the present invention, the size of the acoustic cavity is much smaller than the wavelength of the sound wave, so the sound pressure in the acoustic cavity closed by the rigid wall can be considered to be uniformly distributed, and the sound pressure equation in the acoustic cavity can be obtained as formula (5).

结合以上分别建立的各部件理论模型,可获得系统在正向和反向激励时的系统控制方程分别为公式(6)和公式(7)、响应声腔的声压响应公式分别为公式(9)和(10)。系统声能量传递的互易量NR由公式(11)定义。Combining the theoretical models of the components established above, the system control equations for the system under forward and reverse excitation are formulas (6) and (7), and the sound pressure response formulas of the response sound cavity are formulas (9) and (10). The reciprocity NR of the system sound energy transfer is defined by formula (11).

系统声能量传递可通过公式(11)计算系统非互易量的大小,来可以判定其是否为非互易系统。The acoustic energy transfer of the system can be calculated by the size of the system non-reciprocal quantity using formula (11), so as to determine whether it is a non-reciprocal system.

实验中通过低源强激励下扫频测得到薄膜的一阶固有频率为62Hz;薄膜的非线性立方刚度通过对薄膜大变形数据的测量结果拟合确定,本发明中采用100um厚度的PDMS薄膜,通过拟合实验数据得其立方非线性刚度k3为3.0×106N/m3In the experiment, the first-order natural frequency of the film was measured by sweeping frequency under low source strength excitation and was found to be 62 Hz. The nonlinear cubic stiffness of the film was determined by fitting the measurement results of the large deformation data of the film. In the present invention, a 100 um thick PDMS film was used, and its cubic nonlinear stiffness k 3 was found to be 3.0×10 6 N/m 3 by fitting the experimental data.

实验中为了输出高源强激励,设计了由8英寸的JL Subwoofer和Brüel&

Figure BDA0003993010820000151
的体积速度源强探头组成的高源强体积速度声源;采用Brüel&
Figure BDA0003993010820000152
的1/4英寸传声器测量正向、反向激励时系统的响应声腔以及管道中心点的声压;采用激光多普勒测振仪(型号:Polytech PSV400)测量薄膜中心点的振动速度。In order to output high source intensity excitation in the experiment, a 8-inch JL Subwoofer and Brüel &
Figure BDA0003993010820000151
The high source intensity volume velocity sound source is composed of volume velocity source intensity probes; using Brüel &
Figure BDA0003993010820000152
A 1/4-inch microphone was used to measure the response cavity of the system and the sound pressure at the center of the pipe during forward and reverse excitations. A laser Doppler vibrometer (model: Polytech PSV400) was used to measure the vibration velocity at the center of the film.

实验结果和理论研究结果分析:Analysis of experimental results and theoretical research results:

如图4至图6所示,在低源强激励下,薄膜平均速度以及响应声压随着输入源强的增加几乎都接近线性增加,此时系统存在较低的声能量非互易量。但由于系统存在非线性,管道声压响应被非线性薄膜的硬化效应所限制,输入源强越大管道声压响应被限制的现象越明显,直到输入能量超过门槛值,系统进入强非线性相互作用区,声能量非互易量达到最大值。在高源强激励下,反向激励时薄膜平均速度以及响应声压仍线性增加,而在正向激励时,薄膜平均速度以及响应声压却平缓增加,声能量非互易传递量减少。As shown in Figures 4 to 6, under low source intensity excitation, the average velocity of the film and the response sound pressure increase almost linearly with the increase of the input source intensity. At this time, the system has a low amount of acoustic energy nonreciprocity. However, due to the nonlinearity of the system, the pipe sound pressure response is limited by the hardening effect of the nonlinear film. The greater the input source intensity, the more obvious the phenomenon of the pipe sound pressure response being limited, until the input energy exceeds the threshold value, the system enters the strong nonlinear interaction region, and the acoustic energy nonreciprocity reaches the maximum value. Under high source intensity excitation, the average velocity of the film and the response sound pressure still increase linearly during reverse excitation, but during forward excitation, the average velocity of the film and the response sound pressure increase gently, and the amount of acoustic energy nonreciprocity transfer decreases.

图4至图6中理论分析结果和实验结果总体上是吻合的,验证了系统理论模型,并揭示了该结构声装置实现声能量非互易传递的机理,实现了接近3.5倍的声能量大非互易传递效果,为管道低频噪声控制提供了新方法。The theoretical analysis results and experimental results in Figures 4 to 6 are generally consistent, which verifies the theoretical model of the system and reveals the mechanism of the structural acoustic device to achieve non-reciprocal transfer of acoustic energy, achieving a non-reciprocal transfer effect of nearly 3.5 times the acoustic energy, providing a new method for pipeline low-frequency noise control.

本说明书实施例所述的内容仅仅是对发明构思的实现形式的列举,本发明的保护范围不应当被视为仅限于实施例所陈述的具体形式,本发明的保护范围也及于本领域技术人员根据本发明构思所能够想到的等同技术手段。The contents described in the embodiments of this specification are merely an enumeration of the implementation forms of the inventive concept. The protection scope of the present invention should not be regarded as limited to the specific forms described in the embodiments. The protection scope of the present invention also extends to equivalent technical means that can be conceived by those skilled in the art based on the inventive concept.

Claims (3)

1.利用NES实现声能量大非互易传递的结构声装置,其特征在于:包括管道(2)、薄膜(5)、以及不同尺寸的正方体声腔一(1)、正方体声腔二(4)和正方体声腔三(6),所述管道(2)的长度远远大于其直径,管道(2)的两端分别与声腔一(1)、声腔二(4)密封连接,且声腔一(1)通过管道(2)与声腔二(4)连通;1. A structural acoustic device for realizing large non-reciprocal transmission of acoustic energy by using NES, characterized in that it comprises a pipe (2), a film (5), and a cube acoustic cavity one (1), a cube acoustic cavity two (4), and a cube acoustic cavity three (6) of different sizes, wherein the length of the pipe (2) is much greater than its diameter, and the two ends of the pipe (2) are respectively sealedly connected to the acoustic cavity one (1) and the acoustic cavity two (4), and the acoustic cavity one (1) is connected to the acoustic cavity two (4) through the pipe (2); 所述声腔二(4)居中叠放安装在声腔三(6)的顶面上,声腔二(4)顶面设有便于安装薄膜(5)的端盖(3),端盖(3)与声腔二(4)密封连接;声腔二(4)与声腔三(6)连接的壁面居中处开有连通声腔二(4)和声腔三(6)的通孔三(H3),通孔三(H3)内密封连接有薄膜夹具(7);薄膜夹具(7)包括环形上夹盖和环形下夹盖,薄膜(5)夹持在上夹盖和下夹盖之间,薄膜夹具(7)和薄膜(5)完全遮蔽通孔三(H3);所述声腔一(1)远离管道(2)的一侧表面开有通孔一(H1),声腔三(6)朝向管道(2)的一侧表面开有通孔二(H2);声腔一(1)、管道(2)、声腔二(4)和声腔三(6)里传输介质均为空气;The second acoustic cavity (4) is centrally stacked and installed on the top surface of the third acoustic cavity (6). The top surface of the second acoustic cavity (4) is provided with an end cover (3) for facilitating the installation of a film (5), and the end cover (3) is sealed and connected to the second acoustic cavity (4). A through hole ( H3 ) for connecting the second acoustic cavity (4) and the third acoustic cavity (6) is opened in the center of the wall surface where the second acoustic cavity (4) and the third acoustic cavity (6) are connected, and a film clamp (7) is sealed and connected in the third through hole ( H3 ). The film clamp (7) includes an annular upper clamp cover and an annular lower clamp cover, and the film (5) is clamped between the upper clamp cover and the lower clamp cover, and the film clamp (7) and the film (5) completely cover the third through hole ( H3 ). The first through hole ( H1 ) is opened on the surface of the first acoustic cavity (1) away from the pipeline (2), and the second through hole ( H2 ) is opened on the surface of the third acoustic cavity (6) facing the pipeline (2). ); the transmission medium in the acoustic cavity 1 (1), the pipe (2), the acoustic cavity 2 (4) and the acoustic cavity 3 (6) is air; 当正向激励时体积速度声源通过通孔一(H1)与声腔一(1)连接,并密闭通孔二(H2);正向激励时所述装置内部形成内共振,声能量发生靶向目标能量转移,从线性振子管道(2)不可逆且高效地传递至非线性振子薄膜(5),并由薄膜(5)向声腔三(6)传递,在声腔三(6)中可以测得较高的响应声压;When positively excited, the volume velocity sound source is connected to the acoustic cavity one ( 1 ) through the through hole one (H1), and the through hole two ( H2 ) is sealed; when positively excited, internal resonance is formed inside the device, and the acoustic energy undergoes targeted energy transfer, and is irreversibly and efficiently transferred from the linear oscillator pipe (2) to the nonlinear oscillator film (5), and then transferred from the film (5) to the acoustic cavity three (6), and a higher response sound pressure can be measured in the acoustic cavity three (6); 当反向激励时体积速度声源通过通孔二(H2)与声腔三(6)连接,并密闭通孔一(H1),且输入声波波长远大于正方体声腔一(1)、正方体声腔二(4)和正方体声腔三(6)的尺寸;反向激励时所述装置未发生内共振,大部分声能量仍停留在声腔三(6)中,声能量传递效率低,在声腔一(1)中测得的响应声压较低;当正向激励和反向激励时系统响应存在较大差异时,所述装置存在大非互易性。When reversely excited, the volume velocity sound source is connected to the sound cavity three (6) through the through hole two ( H2 ), and the through hole one ( H1 ) is sealed, and the wavelength of the input sound wave is much larger than the size of the cube sound cavity one (1), the cube sound cavity two (4) and the cube sound cavity three (6); when reversely excited, the device does not have internal resonance, most of the sound energy still remains in the sound cavity three (6), the sound energy transfer efficiency is low, and the response sound pressure measured in the sound cavity one (1) is low; when there is a large difference in the system response during forward excitation and reverse excitation, the device has a large non-reciprocity. 2.如权利要求1所述的利用NES实现声能量大非互易传递的结构声装置,其特征在于:所述管道(2)采用不锈钢制成,管道(2)内径的截面半径为17.5mm,管道(2)的长度为1.75m;所述声腔一(1)、声腔二(4)和声腔三(6)均采用亚克力制成,且均呈正方体形;声腔一(1)和声腔二(4)的腔体边长均为0.2m,声腔三(6)的腔体边长为0.3m;薄膜(5)采用硅胶制成,薄膜(5)的厚度为0.1mm,薄膜(5)的半径为19mm。2. The structural acoustic device for realizing large non-reciprocal transmission of acoustic energy by using NES as claimed in claim 1, characterized in that: the pipe (2) is made of stainless steel, the cross-sectional radius of the inner diameter of the pipe (2) is 17.5 mm, and the length of the pipe (2) is 1.75 m; the acoustic cavity 1 (1), the acoustic cavity 2 (4) and the acoustic cavity 3 (6) are all made of acrylic and are all in the shape of a cube; the cavity side lengths of the acoustic cavity 1 (1) and the acoustic cavity 2 (4) are both 0.2 m, and the cavity side length of the acoustic cavity 3 (6) is 0.3 m; the film (5) is made of silicone, the thickness of the film (5) is 0.1 mm, and the radius of the film (5) is 19 mm. 3.基于权利要求1或2所述的利用NES实现声能量大非互易传递的结构声装置验证方法,其特征在于:给定管道(2)的半径Rt、管道(2)的长度L、薄膜(5)的半径Rm、薄膜(5)的密度ρm、薄膜(5)的厚度h、薄膜(5)的泊松比υ、薄膜(5)的杨氏模量E、薄膜(5)的阻尼系数η、正方形声腔一(1)的体积V1、正方形声腔二(4)的体积V2、正方形声腔三(6)的体积V3、声源激励幅值Qs、激励频率ωs、空气密度ρa和声速c0,进行理论建模,然后进行仿真和实验验证,步骤如下:3. A method for verifying a structural acoustic device using NES to achieve large non-reciprocal transfer of acoustic energy based on claim 1 or 2, characterized in that: given the radius Rt of the pipe (2), the length L of the pipe (2), the radius Rm of the film (5), the density ρm of the film (5), the thickness h of the film (5), the Poisson's ratio υ of the film (5), the Young's modulus E of the film (5), the damping coefficient η of the film (5), the volume V1 of the square acoustic cavity one (1), the volume V2 of the square acoustic cavity two (4), the volume V3 of the square acoustic cavity three (6), the sound source excitation amplitude Qs , the excitation frequency ωs , the air density ρa and the sound speed c0 , theoretical modeling is performed, and then simulation and experimental verification are performed, the steps are as follows: 1)分别建立管道、非线性薄膜和声腔三类组成单元的理论模型、三类单元耦合而成的系统控制方程表达式以及声能量的非互易量的判定式:1) The theoretical models of the three types of components, namely, pipes, nonlinear membranes and acoustic cavities, the expressions of the system control equations coupled by the three types of units, and the determination formula of the non-reciprocal amount of acoustic energy are established respectively: 管道的理论模型:由于管道的长度远大于其直径,因此可被假设为一维波导,分别假设ua和px为管道末端声介质位移和管道内声压,结合声波波动方程和Rayleigh-Ritz简化,并引入空气阻尼系数cf,可获得管道控制方程:Theoretical model of the pipeline: Since the length of the pipeline is much larger than its diameter, it can be assumed to be a one-dimensional waveguide. Assuming u a and p x are the displacement of the acoustic medium at the end of the pipeline and the sound pressure in the pipeline respectively, combining the acoustic wave equation and Rayleigh-Ritz simplification, and introducing the air damping coefficient c f , the pipeline control equation can be obtained:
Figure FDA0003993010810000031
Figure FDA0003993010810000031
其中,in,
Figure FDA0003993010810000032
Figure FDA0003993010810000032
薄膜的理论模型:采用Von Karman非线性板壳模型,结合Kelvin-Viogt粘弹性本构模型,建立薄膜的控制方程;然后采用抛物线函数作为薄膜一阶模态振型函数,通过Rayleigh-Ritz降价建模方法,获得非线性薄膜的控制方程:Theoretical model of the film: The Von Karman nonlinear plate-shell model is combined with the Kelvin-Viogt viscoelastic constitutive model to establish the control equation of the film; then the parabolic function is used as the first-order modal vibration function of the film, and the control equation of the nonlinear film is obtained through the Rayleigh-Ritz price reduction modeling method:
Figure FDA0003993010810000033
Figure FDA0003993010810000033
其中qm为薄膜中心的横向位移,pm为薄膜所受的声压;f1m为有预应力时薄膜的线性一阶固有频率,由实验测量获得,f0m为无预应力的薄膜的共振频率;k1和k3分别为薄膜的线性刚度和立方非线性刚度,Sm为薄膜的面积;ma0是薄膜大振幅运动带动周边空气运动的附加质量,根据实验结果确定;其他参数由下列公式给出:Where qm is the lateral displacement of the center of the film, pm is the sound pressure on the film; f1m is the linear first-order natural frequency of the film with prestress, obtained by experimental measurement, f0m is the resonant frequency of the film without prestress; k1 and k3 are the linear stiffness and cubic nonlinear stiffness of the film, respectively, Sm is the area of the film; ma0 is the additional mass of the surrounding air driven by the large amplitude motion of the film, determined according to experimental results; other parameters are given by the following formulas:
Figure FDA0003993010810000041
Figure FDA0003993010810000041
声腔的理论模型:当声波波长远大于声腔尺寸,刚性壁封闭声腔内的声压可认为是均布的,可获得声腔内声压方程:Theoretical model of acoustic cavity: When the wavelength of the sound wave is much larger than the size of the acoustic cavity, the sound pressure in the acoustic cavity closed by the rigid wall can be considered to be uniformly distributed, and the sound pressure equation in the acoustic cavity can be obtained:
Figure FDA0003993010810000042
Figure FDA0003993010810000042
结合公式(1)、(3)和(5)可得系统控制方程:Combining formulas (1), (3) and (5), we can get the system control equation: 正向激励时:When positively motivated:
Figure FDA0003993010810000043
Figure FDA0003993010810000043
Figure FDA0003993010810000044
Figure FDA0003993010810000044
反向激励时:When the reverse incentive:
Figure FDA0003993010810000045
Figure FDA0003993010810000045
Figure FDA0003993010810000046
Figure FDA0003993010810000046
其中,in,
Figure FDA0003993010810000047
Figure FDA0003993010810000047
正向激励时正方形声腔三(6)为响应声腔,反向激励时正方形声腔一(1)为响应声腔,其腔内声压分别为:When the square sound cavity is positively excited, the third square sound cavity (6) is the response sound cavity, and when the square sound cavity is negatively excited, the first square sound cavity (1) is the response sound cavity. The sound pressures in the cavities are:
Figure FDA0003993010810000051
Figure FDA0003993010810000051
Figure FDA0003993010810000052
Figure FDA0003993010810000052
装置系统声能量传递的互易量NR由下式定义:The reciprocity NR of the acoustic energy transfer of the device system is defined by the following formula:
Figure FDA0003993010810000053
Figure FDA0003993010810000053
可根据公式(11)判定该装置是否是大非互易系统。Whether the device is a large non-reciprocal system can be determined according to formula (11).
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