Building wall system with embedded double cavity sound absorbing energy storage structure

Abstract

The application provides a building wall system embedded with a double-cavity sound absorption energy storage structure, comprising a base wall, an acoustic impedance matching layer, a double-cavity sound wave resonance assembly, an acoustic-electric conversion unit, and an electric energy processing and storage unit; the acoustic impedance matching layer is laid on the surface of the base wall, the double-cavity sound wave resonance assembly is embedded in the acoustic impedance matching layer and the base wall, and an incident neck is arranged on the surface of the acoustic impedance matching layer; when the low-frequency coupling resonance frequency of the double-cavity sound wave resonance assembly is tuned to the first-order natural frequency of the base wall, a reverse-phase exciting force lagging behind the wall movement is generated by the high pressure of the fluid in the cavity in the resonance state; the piezoelectric composite diaphragm of the acoustic-electric conversion unit is sealed at the wide mouth of the second resonance cavity, and the double-cavity sound wave resonance assembly is used to generate alternating electric energy through the sound pressure amplification effect in the cavity; the electric energy processing and storage unit is electrically connected with the acoustic-electric conversion unit and comprises a rectification and filtering module and a super capacitor, which is used for converting the alternating electric energy into stable direct current and storing.

Description

Technical Field

[0001] This invention relates to a building wall, and more particularly to a building wall system with an embedded dual-cavity sound-absorbing and energy-storing structure. Background Technology

[0002] With the acceleration of modern urbanization and the continuous increase in building density, low-frequency noise and structural vibration problems caused by various electrical equipment inside buildings (such as large central air conditioners, water pumps, transformers, etc.) and external transportation are becoming increasingly prominent. These low-frequency disturbances can easily induce continuous resonant deformation and oscillation of the building's base walls near their natural frequencies, which not only seriously affects the comfort of the indoor living environment, but may also lead to fatigue damage to the building structure in the long run, threatening the safety of the building throughout its entire life cycle. Currently, traditional building noise reduction and vibration reduction methods mainly rely on laying sound-absorbing cotton, damping sound insulation boards, or thickening protective walls on the wall surface. However, in practical engineering applications, these existing technologies have the following significant drawbacks.

[0003] First, low-frequency control capabilities are severely inadequate. According to acoustic theory, the energy dissipation efficiency of traditional sound-absorbing materials is highly dependent on material thickness, and their absorption efficiency for long-wavelength low-frequency sound waves and mechanical vibrations is extremely low. To achieve the ideal low-frequency damping effect, it is often necessary to significantly increase the thickness and volume of the protective layer, which not only occupies valuable building interior space but also greatly increases the building's weight and construction costs. Second, there is a lack of energy capture and recycling mechanisms. Existing low-frequency energy-dissipating structures merely passively dissipate mechanical energy into unusable, weak heat energy through friction within the material's micropores, resulting in a significant waste of high-energy building structural resonance energy. How to efficiently convert this destructive building mechanical energy into reusable green electricity is a bottleneck that has not yet been effectively solved in the field of building energy conservation and physical protection. Third, there is an inability to cope with engineering construction deviations and a lack of precise tuning methods. Due to engineering deviations such as actual construction techniques, material inhomogeneity, and subsequent environmental degradation, there are often unavoidable deviations between the actual natural frequencies of building walls after construction and theoretical calculations. Traditional fixed noise reduction and vibration damping components have fixed acoustic characteristics after installation and cannot be dynamically adjusted. This can easily lead to a misalignment between the system's resonant frequency and the actual vibration frequency of the wall, resulting in a significant deterioration in the accuracy of energy capture and the damping countermeasure effect. Summary of the Invention

[0004] The purpose of this invention is to provide a building wall system with an embedded dual-cavity sound-absorbing and energy-storing structure, including a base wall, an acoustic impedance matching layer, a dual-cavity acoustic resonance assembly, an acoustic-electric transducer unit, and an energy processing and storage unit. The dual-cavity acoustic resonance assembly includes an incident neck, a first-stage resonance cavity, a connecting neck member, and a second-stage resonance cavity connected in sequence. The axis of the dual-cavity acoustic resonance assembly is perpendicular to the base wall. The acoustic impedance matching layer is laid on the surface of the base wall, and the dual-cavity acoustic resonance assembly is embedded in the acoustic impedance matching layer and the base wall. The incident neck is located in the acoustic... On the surface of the impedance matching layer, when the low-frequency coupling resonance frequency of the dual-cavity acoustic wave resonance component is tuned to the first-order natural frequency of the base wall, the high pressure of the fluid inside the cavity generates an anti-phase excitation force that lags behind the moving phase of the wall in the resonance state; the piezoelectric composite diaphragm of the acoustic-electric transducer unit is sealed at the wide opening of the second resonance cavity, and generates alternating electrical energy through the acoustic pressure amplification effect inside the cavity of the dual-cavity acoustic wave resonance component; the electrical energy processing and storage unit is electrically connected to the acoustic-electric transducer unit, and includes a rectifier filter module and a supercapacitor, which are used to convert the alternating electrical energy into stable direct current and store it.

[0005] Furthermore, the dual-cavity acoustic resonance assembly includes an incident neck, a connecting neck component, and two-stage Helmholtz resonant cavities. The two-stage Helmholtz resonant cavities include a first-stage resonant cavity and a second-stage resonant cavity. One end of the smaller inner diameter of the first-stage resonant cavity is connected to the incident neck, and the other end of its larger inner diameter is connected to one end of the connecting neck component. One end of the smaller inner diameter of the second-stage resonant cavity is connected to the other end of the connecting neck component. The larger inner diameter of the first-stage resonant cavity, the inner diameter of the connecting neck component, and the smaller inner diameter of the second-stage resonant cavity are equal. The incident neck, the connecting neck component, the first-stage resonant cavity, and the second-stage resonant cavity are coaxial. The connections between the incident neck, the connecting neck component, the first-stage resonant cavity, and the second-stage resonant cavity are sealed.

[0006] Compared with the prior art, the present invention has the following advantages: (1) The present invention sets up two-stage Helmholtz resonant cavities in series and uses the lumped parameter theory to tune the overall low-frequency coupling resonance frequency of the dual-cavity components to be strictly equal to the first-order natural frequency of the base wall. In the resonance state, the high pressure of the fluid in the cavity and the diaphragm at the wide opening generate an anti-phase excitation force. The phase hysteresis characteristic is used to push back the mechanical oscillation of the entire wall, thereby achieving efficient counter-impact and non-destructive capture of the low-frequency mechanical resonance energy of the wall without increasing the volume of the protective layer; (2) The present invention can introduce external sound waves and structural vibration energy into the second-stage resonant cavity, causing the spatial maximum sound pressure level at the end of the cavity. When magnified, the piezoelectric composite diaphragm sealed at the wide opening produces the maximum amplitude of chord bending deformation under the high sound pressure of resonance, so that its in-plane strain reaches the peak value. The system converts the originally destructive mechanical energy into alternating electrical energy under extremely high energy conversion efficiency and stores it in a supercapacitor, successfully realizing the green collection and recycling of building micro energy consumption; (3) The dynamic adjustment of the frustum-shaped second-stage resonance cavity of the present invention can calculate the target volume reduction ΔV, thereby driving and locking the diaphragm advance displacement ΔL, which can dynamically correct deviation and accurately change the effective internal volume of the second-stage resonance cavity, ensuring that the single component can accurately capture the actual resonance energy of the entire wall.

[0007] The present invention will now be further described with reference to the accompanying drawings. Attached Figure Description

[0008] Figure 1 This is a schematic diagram of the system structure of the present invention.

[0009] Figure 2 This is a schematic diagram of a dual-cavity acoustic resonator.

[0010] Figure 3 This is a circuit diagram of an energy processing and storage unit.

[0011] Figure 4 This is a simulation diagram of the sound pressure on the interior wall of a building without a dual-cavity acoustic resonator.

[0012] Figure 5 A simulation diagram of the sound pressure on the interior wall of a building using a dual-cavity acoustic resonator.

[0013] The attached diagram is labeled as follows: 1. Base wall; 2. Acoustic impedance matching layer; 3. Dual-cavity acoustic resonance assembly; 301. Incident neck; 302. Connecting neck component; 303. First-stage resonance cavity; 304. Second-stage resonance cavity; 4. Acousto-electric transducer unit; 401. Piezoelectric composite diaphragm; 5. Energy processing and storage unit. Detailed Implementation

[0014] Combination Figure 1A building noise reduction and vibration damping wall system with an embedded dual-cavity sound-absorbing and energy-storage structure includes a base wall 1, an acoustic impedance matching layer 2, a dual-cavity acoustic wave resonance assembly 3, an acoustic-electric transducer unit 4, and an energy processing and storage unit 5. The acoustic impedance matching layer 2, made of solid waste lightweight soil, is laid on the inner surface of the base wall 1 to form a layered protective wall structure. The dual-cavity acoustic wave resonance assembly 3 is embedded in the acoustic impedance matching layer 2 and the base wall 1, and includes a first-stage resonance cavity and a second-stage resonance cavity connected sequentially; the smaller inner diameter end of the first-stage resonance cavity faces the interior of the building, and the axis of the dual-cavity acoustic wave resonance assembly 3 is perpendicular to the base wall 1. The piezoelectric composite diaphragm 401 of the acoustic-electric transducer unit 4 is sealed at the wide opening of the second resonance cavity, generating electricity through the acoustic pressure amplification effect within the cavity. The energy processing and storage unit 5 is electrically connected to the acoustic-electric transducer unit 4 and includes a rectifier filter module and a supercapacitor, used to convert alternating electrical energy into stable direct current and store it.

[0015] The base wall 1 bears the entire system and oscillates to dissipate low-frequency resonant deformation mechanical energy in response to external disturbances; it has an inherent first-order natural frequency f. w When external disturbances excite the base wall 1 at its first natural frequency f w When structural oscillation occurs within the structure, the base wall 1 serves as the energy source supply end for transmitting reciprocating mechanical vibrations to subsequent layers of structure and components.

[0016] The acoustic impedance matching layer 2 is laid on the inner surface of the base wall 1, forming a layered protection with the base wall 1. The acoustic impedance matching layer 2 guides and physically converges acoustic energy in space. A dual-cavity acoustic wave resonance component 3 is pre-embedded inside the acoustic impedance matching layer 2, and its surface has a funnel-shaped or gradually hyperboloidal acoustic wave guiding recess area formed facing the acoustic symmetry center positioning point. This is used to utilize the spatial refraction and deflection effect to physically converge the incident sound waves towards the center with strong focusing, and at the same time, to constrain the flow of acoustic energy excited by multiple sources and the energy dissipation of materials through dielectric impedance matching.

[0017] The dual-cavity acoustic resonance assembly 3 is embedded in the acoustic impedance matching layer 2. It counteracts the mechanical vibration of the base wall 1 through low-frequency coupled resonance and achieves a significant spatial amplification of the sound pressure level at the end of the cavity. The dual-cavity acoustic resonance assembly 3 includes an incident neck 301, a first-stage resonance cavity 303, a connecting neck member 302, and a second-stage resonance cavity 304, which are connected in series coaxially and sealed. The overall low-frequency coupled resonance frequency f of the dual-cavity acoustic resonance assembly 3 is... L The frequency f is tuned to be exactly equal to the first natural frequency f of the base wall 1. w It is used to generate a reverse phase excitation force that lags behind the moving phase of the wall under the high pressure of the fluid in the cavity in the resonant state, so as to push back and counteract the mechanical vibration of the base wall 1 to reduce the amplitude of the whole wall; at the same time, the sound wave and the mechanical vibration energy of the structure are introduced into the second-stage resonant cavity 304 to stimulate the spatial sound pressure amplification effect.

[0018] The acoustic-electric transducer 4 has a piezoelectric composite diaphragm 401 sealed at the wide opening of the second-stage resonant cavity 304, which captures the resonant sound pressure and converts the whole-wall resonant mechanical energy into alternating electrical energy. At the tuned resonant frequency, the piezoelectric composite diaphragm 401 withstands the greatly amplified alternating sound pressure within the second-stage resonant cavity 304, causing the diaphragm to produce the maximum amplitude of string bending deformation and in-plane strain peak, thereby converting the dissipated whole-wall resonant mechanical energy into output alternating electrical energy with maximum transducing efficiency.

[0019] The power processing and storage unit 5 is electrically connected to the acoustic-electric transducer unit 4, regulating the high-frequency unstable alternating power into stable direct current and performing lossless temporary storage to provide power. The power processing and storage unit 5 includes at least a rectifier and filter module and a supercapacitor. The power processing and storage unit 5 receives the alternating power output from the acoustic-electric transducer unit 4, converts it into stable direct current through the rectifier and filter module, and inputs it into the supercapacitor for storage, thereby powering auxiliary electrical components, such as the Peltier refrigeration unit.

[0020] Combination Figure 2 The dual-cavity acoustic resonance assembly 3 includes two-stage Helmholtz resonators connected in series, an incident neck 301, and a connecting neck member 302. The two-stage Helmholtz resonators include a first-stage resonator 303 and a second-stage resonator 304. The first-stage resonator 303 has its smaller inner diameter end connected to the incident neck 301 and its larger inner diameter end connected to one end of the connecting neck member 302. The second-stage resonator 304 has its smaller inner diameter end connected to the other end of the connecting neck member 302. The larger inner diameter of the first-stage resonator 303, the inner diameter of the connecting neck member 302, and the smaller inner diameter of the second-stage resonator 304 are equal. The incident neck 301, the connecting neck member 302, the first-stage resonator 303, and the second-stage resonator 304 are coaxial, and the connections between them are sealed. The receiving end of the incident neck 301 faces indoors.

[0021] Combination Figure 3The power processing and storage unit 5 mainly includes an input terminal, a rectification and filtering module, an overvoltage protection module, a supercapacitor energy storage module, and a load output switch. The rectification and filtering module includes a full-wave rectifier bridge and a filter capacitor C1. The full-wave rectifier bridge consists of four low-dropout Schottky diodes (D1, D2, D3, D4). The two AC power output wires of the piezoelectric composite diaphragm PZT are connected to the two AC input terminals of the rectifier bridge. The DC positive output terminal (V+) of the rectifier bridge is connected to the positive terminal of the filter capacitor C1; the DC negative output terminal (GND) of the rectifier bridge is connected to the negative terminal of the filter capacitor C1, and preliminary ripple elimination is achieved through this parallel filter capacitor C1. The overvoltage protection module is a bidirectional transient voltage suppression diode DZ, which is connected in parallel across the filter capacitor C1 to prevent transient high voltage from generating in the piezoelectric diaphragm under strong vibrations, causing breakdown of the subsequent supercapacitor. The supercapacitor energy storage module is a supercapacitor C... super The positive terminal of the rectified and filtered DC power is connected to the supercapacitor C. super The positive and negative terminals are connected to the supercapacitor C. super The negative terminal is used to store electrical energy normally. Supercapacitor C super The positive and negative terminals are connected to external device units such as Peltier cooling units and wall-mounted low-power sensors via load output switch SW1, forming a complete power supply circuit.

[0022] The working principle of the acoustic-electric transducer unit 4 is as follows: external disturbances will cause the base wall 1 to produce low-frequency resonant deformation. Due to the overall low-frequency coupling resonant frequency f of the dual-cavity acoustic wave resonance component 3, L It has been pre-tuned to the wall's natural frequency f wThe air particles inside the system will also undergo extremely intense forced resonance at the same frequency. When the sound waves and the mechanical vibration energy of the structure are transmitted into the second-stage resonant cavity 304, the special structure of the frustum-shaped cavity's geometric contraction will cause a significant spatial amplification of the sound pressure level at the end of the cavity. This causes the piezoelectric composite diaphragm 401, sealed at the wide opening of the second-stage resonant cavity 304, to begin to withstand extremely high alternating sound pressure. Under the reciprocating thrust of the extremely high alternating sound pressure within the second-stage resonant cavity 304, the diaphragm is no longer a weak vibration, but rather produces maximum amplitude string bending deformation. This intense bending causes significant stretching and compression of the lattice structure inside the piezoelectric material, with the in-plane strain reaching its peak. With the mechanical deformation of the material lattice, the positive and negative charge centers inside the piezoelectric composite material undergo relative displacement, generating bound charges on the diaphragm surface. Since the sound pressure is alternating, the diaphragm surface will continuously generate bound charges with alternating directions, thereby forming alternating electrical energy at the output end. In the resonant state, since the motion phase of the fluid and the diaphragm usually lags behind the vibration of the base wall 1, when the base wall 1 deforms in one direction, the high pressure of the fluid in the resonant cavity and the rebound force of the diaphragm will push against each other in the opposite direction. This anti-phase excitation force can directly counteract the mechanical vibration of the wall and reduce the amplitude of the entire wall.

[0023] In this embodiment, the relationship between the two-stage Helmholtz resonator and the natural frequency of the wall needs to be considered during installation to determine the parameters of the two-stage Helmholtz resonator, as well as the incident neck 301 and the connecting neck member 302. That is, the overall low-frequency coupling resonant frequency f of the dual-cavity member is determined. L Tuned to the wall's natural frequency f w To determine the cross-sectional area and equivalent length of the incident neck 301 and the connecting neck member 302, as well as the effective internal volume of the first-stage resonant cavity 303 and the second-stage resonant cavity 304.

[0024] According to acoustic lumped parameter theory, the characteristic equation (angular frequency ω) of a two-cavity series system is ω 4 -Aω 2 +B=0, using the quadratic formula We can obtain two solutions ω. L 2 (Low-frequency mode) and ω H 2 (High-frequency modes). The specific derivation process is shown below.

[0025] According to the lumped parameter theory, when the wavelength of the sound wave is much larger than the size of the resonator, the continuous medium hydrodynamic problem can be simplified into a discrete mechanical / circuit system. The air in the incident neck 301 and the connecting neck member 302, due to inertia, is equivalent to a rigid slider, with corresponding acoustic masses M1 and M2 as follows:

[0026] M1=(ρ·L1) / S1,

[0027] M2=(ρ·L2) / S2,

[0028] Where M1 is the acoustic mass corresponding to the incident neck 301, M2 is the acoustic mass corresponding to the connecting neck member 302, ρ is the air density, L1 and L2 are the equivalent lengths of the incident neck 301 and the connecting neck member 302, respectively, and S1 and S2 are the cross-sectional areas of the incident neck 301 and the connecting neck member 302, respectively. In the two-stage resonant cavity, due to compression deformation, it is equivalent to a volume spring, with corresponding acoustic capacities C1 and C2 being...

[0029] C1=V1 / (ρ·c 2 ),

[0030] C2=V2 / (ρ·c 2 ),

[0031] Wherein, C1 is the acoustic volume corresponding to the first-stage resonance cavity 303, C2 is the acoustic volume corresponding to the second-stage resonance cavity 304, V1 and V2 are the effective internal volumes of the first-stage resonance cavity 303 and the second-stage resonance cavity 304 respectively, and c is the speed of sound in air.

[0032] Sound waves are incident from the outside, and the series-connected dual-cavity acoustic resonator 3 acoustically behaves as a second-order low-pass filter circuit: the external sound pressure p(t) pushes M1, and airflow enters C1; subsequently, the pressure difference inside C1 continues to push M2, and airflow enters C2. Let the acoustic volume velocity through the incident neck 301 be U1, and the acoustic volume velocity through the connecting neck member 302 be U2. Neglecting acoustic impedance, according to Kirchhoff's laws, we have:

[0033] ,

[0034] .

[0035] Applying the simple harmonic motion assumption to the above system of differential equations, and differentiating it twice with respect to time t, let... This can be transformed into a system of algebraic equations about U1 and U2:

[0036] ,

[0037] ,

[0038] Where, -ω 2 M1U1 and -ω 2M2U2 are the acoustic inertial forces generated by the reciprocating motion of air mass within the incident neck 301 and the connecting neck member 302, respectively, i.e., the resistance terms; 1 / C1 is the acoustic stiffness of the first resonant cavity, representing the volumetric elastic restoring force generated when the air inside the cavity is compressed; 1 / C2 is the acoustic stiffness of the second resonant cavity, which is the end point of the entire acoustic circuit since the end of the second resonant cavity is sealed by the diaphragm.

[0039] For the above system of algebraic equations to have non-zero solutions (i.e., the system can generate inherent resonance even without continuous external sound pressure), the determinant of its hydrodynamic coefficients must be zero. The standard 2×2 matrix determinant is expressed as follows:

[0040] ,

[0041] According to the rules of determinant calculation, the product of the main diagonal elements minus the product of the secondary diagonal elements equals 0. The specific expanded algebraic equation is as follows:

[0042] ,

[0043] Divide both sides of the equation by M1M2, substitute the expressions for sound mass and sound volume into the above equation, and eliminate density ρ, to obtain:

[0044] .

[0045] Using the quadratic formula, we get:

[0046] ,

[0047] ,

[0048] ;

[0049] Then, the overall low-frequency coupling resonance frequency f is obtained. L =ω L / 2π.

[0050] When external disturbances excite the base wall 1 at its natural frequency f w When low-frequency resonant deformation occurs, the base wall 1 begins to oscillate back and forth. To achieve the energy absorption effect, the overall low-frequency coupling resonant frequency f should be adjusted. L Tuning to f w That is, f L =f w Based on the length a, width b, and thickness h of the base wall 1, the Young's modulus of the wall material is E, its density ρ', its Poisson's ratio υ, and its first natural frequency f. w for:

[0051] .

[0052] Due to the f of the double-cavity component L It has been tuned to f w The air particles inside the component, including the incident neck 301, the connecting neck component 302, and the piezoelectric composite diaphragm 401 at the wide opening, will also experience extremely intense forced resonance at this frequency. In the resonant state, the fluid and diaphragm's motion phase typically lags behind the wall. When the wall deforms to the left, the high-pressure fluid inside the component pushes back to the right, using the anti-phase excitation force to counteract the mechanical vibration of the wall, thereby reducing the overall wall amplitude. Simultaneously, f L Tuning to f w At this time, the sound waves and structural mechanical vibration energy enter the second-stage resonant cavity 304, causing a huge spatial amplification of the cavity sound pressure level. At this time, the large-area piezoelectric composite diaphragm 401 sealed at the wide opening of the second-stage resonant cavity 304 bears extremely high alternating sound pressure. Under the resonant sound pressure, the diaphragm produces the maximum amplitude of string bending deformation. As the in-plane strain of the diaphragm reaches its peak, the system dissipates the resonant energy of the entire wall while converting this part of the mechanical energy that would originally damage the building structure into electrical energy with the maximum energy conversion efficiency, and inputs it into the supercapacitor for storage.

[0053] This embodiment considers the unavoidable engineering deviation between the theoretically calculated wall frequency and the actual constructed wall frequency. Therefore, it is necessary to dynamically adjust V2 to achieve precise capture and damping counterbalancing of the energy of the entire wall by a single component. In actual operation, the specific process of adjusting V2 to achieve precise capture and damping counterbalancing of the energy of the entire wall by a single component includes:

[0054] Step S210, according to the preset first-order natural frequency f w Or the actual first-order natural frequency f obtained by a vibration tester. w,test The target tuning volume value V2 of the second-stage resonance cavity 304 is obtained;

[0055] Step S220: The second-stage resonant cavity 304 is frustoconical. Based on the geometric contraction characteristics of the inner wall of the frustoconical shape, the cross-sectional area function S(x) of the cone at any axial depth x of the second-stage resonant cavity 304 is defined.

[0056] ,

[0057] Where Rmax and Rmin are the maximum and minimum inner diameters of the second-stage resonance cavity 304, respectively;

[0058] Step S230: The difference between the internal volume V of the second-stage resonance cavity 304 and the target tuning volume V2 is defined as the target volume reduction ΔV = V - V2; the diaphragm advance displacement ΔL is calculated, and the relationship between the diaphragm advance displacement ΔL and the target volume reduction ΔV is expressed by the following formula:

[0059] ;

[0060] Solving the above integral equation yields ΔL.

[0061] ;

[0062] Step S240: Push the diaphragm forward by ΔL and lock it in place.

[0063] This system can also be equipped with several device units that can be powered by the power processing and energy storage unit 5, such as a Peltier cooling unit, which is attached to the electrical installation area of ​​the building's interior wall and driven by the supercapacitor to provide heat dissipation for wall-mounted electrical appliances.

[0064] Combination Figure 4 , Figure 5 , Figure 4 This is an acoustic simulation diagram of the building without the addition of this sound absorption system. The sound source radiates sound waves that act directly on the wall surface. The overall sound pressure level of the wall surface is high, and the sound pressure peak in some areas is prominent. Continuous action can easily induce resonance and fatigue damage to the building structure. Figure 5 The acoustic simulation diagram inside the building after the addition of this sound absorption system demonstrates that the dual-cavity interconnected resonant chamber efficiently absorbs and concentrates sound waves in the target frequency band, resulting in a significant overall reduction in the sound pressure level on the wall and a marked attenuation of the peak value. The excitation effect of sound waves on the building structure is greatly reduced, effectively suppressing structural resonance, lowering the risk of fatigue cracking in components, and significantly improving the safety and service life of the building structure. This fully verifies the technical advantages of this system in building resonance protection.

Claims

1. A building wall system with an embedded dual-cavity sound-absorbing and energy-storing structure, characterized in that, The system includes a base wall, an acoustic impedance matching layer, a dual-cavity acoustic resonance assembly, an acoustic-electric transducer, and an energy processing and storage unit. The dual-cavity acoustic resonance assembly comprises an incident neck (301), a first-stage resonance cavity (303), a connecting neck member (302), and a second-stage resonance cavity (304) connected in sequence. The axis of the dual-cavity acoustic resonance assembly is perpendicular to the base wall. An acoustic impedance matching layer is laid on the surface of the base wall. The dual-cavity acoustic wave resonance component is embedded in the acoustic impedance matching layer and the base wall. The incident neck (301) is set on the surface of the acoustic impedance matching layer. When the low-frequency coupling resonance frequency of the dual-cavity acoustic wave resonance component is tuned to the first natural frequency of the base wall, the high pressure of the fluid in the cavity generates an anti-phase excitation force that lags behind the moving phase of the wall in the resonance state. The piezoelectric composite diaphragm of the acoustic-electric transducer is sealed at the wide opening of the second resonance cavity, generating alternating electrical energy through the sound pressure amplification effect within the dual-cavity acoustic resonance assembly. The power processing and storage unit is electrically connected to the acoustic-electric transduction unit and includes a rectifier and filter module and a supercapacitor, which are used to convert alternating power into stable direct current and store it. The small inner diameter end of the first-stage resonant cavity (303) is connected to the incident neck (301), and the large inner diameter end is connected to one end of the connecting neck member (302). The small inner diameter of the second-stage resonant cavity (304) is connected at one end to the connecting neck member (302) and at the other end. The large inner diameter of the first-stage resonant cavity (303), the inner diameter of the connecting neck member (302), and the small inner diameter of the second-stage resonant cavity (304) are equal. The incident neck (301), the connecting neck component (302), the first-stage resonant cavity (303), and the second-stage resonant cavity (304) are coaxial. The connection between the incident neck (301), the connecting neck component (302), the first-stage resonance cavity (303), and the second-stage resonance cavity (304) is sealed.

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