Ventilation and sound insulation structure based on spiral channel and ventilation and sound insulation window

Abstract

The invention provides a ventilation and sound insulation structure based on a spiral channel and a ventilation and sound insulation window. The ventilation and sound insulation structure comprises an upper sealing plate, a lower sealing plate, a left side plate, a right side plate, a first spiral blade and a second spiral blade. The upper sealing plate and the lower sealing plate are oppositely arranged up and down at a certain distance; the left side plate and the right side plate are vertically arranged between the upper sealing plate and the lower sealing plate at a certain interval, so that sound absorption cavities are formed among the upper sealing plate, the lower sealing plate, the left side plate and the right side plate, and the upper sealing plate and the lower sealing plate extend outwards along the outer sides of the left side plate and the right side plate to form flanges; the first spiral blade and the second spiral blade are vertically arranged between the upper sealing plate and the lower sealing plate in a mutual spiral non-overlapping mode and located in the sound absorption cavity, the inner end of the first spiral blade is arranged in the center of the sound absorption cavity, and the outer end of the first spiral blade is arranged on the inner side of the left side plate. The inner end of the second spiral blade is arranged in the center of the sound absorption cavity, the outer end of the second spiral blade is arranged on the inner side of the right side plate, and the front and rear openings of the sound absorption cavity are communicated with the spiral channel. The sound insulation and ventilation door has a good sound insulation effect and ventilation performance.

Description

Technical Field

[0001] The present invention relates to a ventilation and sound insulation structure, in particular to a ventilation and sound insulation structure based on a spiral channel and a ventilation and sound insulation window. Background Art

[0002] With the acceleration of urbanization and the rise of industrialization, noise has had a significant impact on people's quality of life and health. Sound insulation technology is an effective acoustic noise control method. By using scientific sound insulation materials and reasonable structural design solutions, traditional sound insulation structures can reduce the interference of noise sources on the surrounding environment and effectively improve the comfort of living and working environments.

[0003] In some locations, effective noise isolation and air circulation are both necessary, posing a significant challenge to balancing ventilation and sound insulation. For example, airport terminals need to isolate the intense noise from aircraft takeoffs and landings, while also maintaining indoor air quality and comfort through ventilation systems. Residential buildings near busy highways or railways require a quiet living environment while ensuring fresh air circulation. However, since sound insulation requires a good seal, which restricts air circulation and compromises ventilation, these two requirements conflict. This makes it difficult for traditional sound insulation structures, such as those with folding ventilation sound insulation channels, to achieve both sound insulation and ventilation.

[0004] In addition, traditional sound insulation structures have the following shortcomings: 1. Traditional sound insulation structures are constrained by the "law of mass effect of sound insulation". To achieve better sound insulation effects, it is usually necessary to increase the density and thickness of the material, especially in the mid-frequency band (frequency band above 500Hz). If a higher sound insulation is to be obtained, its material consumption and volume will also increase significantly; 2. Once the traditional sound insulation structure is installed, its sound insulation performance is fixed and difficult to adjust flexibly. If the sound insulation effect is not ideal in the later stage, it is difficult to make effective improvements due to the lack of optimization space. Summary of the Invention

[0005] To address the above-mentioned technical problems, the present invention provides a ventilation and sound insulation structure and ventilation and sound insulation window based on a spiral channel. This structure overcomes the limitations of traditional sound insulation materials, such as their thickness, poor ventilation, and low flexibility, and offers the significant advantages of being lightweight, energy-efficient, and flexible to adjust, while also ensuring good air circulation. By utilizing the Fano resonance principle to regulate the propagation characteristics of sound waves, the present invention can achieve effective sound insulation across a wide mid-frequency band at a relatively thin thickness. This structure offers excellent sound insulation without compromising ventilation performance, bringing new technological breakthroughs and superior solutions to the field of acoustic sound insulation technology.

[0006] The technical solution adopted by the present invention to solve its technical problem is:

[0007] A ventilation and sound insulation structure based on a spiral channel, comprising an upper sealing plate, a lower sealing plate, a left side plate, a right side plate, a first spiral blade and a second spiral blade;

[0008] The upper sealing plate and the lower sealing plate are arranged relative to each other with a certain distance between them;

[0009] The left and right panels are vertically arranged at a certain distance between the upper and lower sealing panels, so that a sound absorption cavity that is closed up and down, left and right, and open front and back is formed between the upper and lower sealing panels, and the upper and lower sealing panels extend outward along the outer sides of the left and right panels to form flanges;

[0010] The first and second spiral blades are vertically arranged between the upper sealing plate and the lower sealing plate in a non-overlapping spiral manner and are located in the sound absorption cavity. The inner end of the first spiral blade is arranged at the center of the sound absorption cavity, and the outer end thereof is arranged at the inner side of the left plate. The inner end of the second spiral blade is arranged at the center of the sound absorption cavity, and the outer end thereof is arranged at the inner side of the right plate, so that the front opening of the sound absorption cavity is connected to the rear opening of the sound absorption cavity through the spiral channel between the first and second spiral blades.

[0011] Optionally, the first spiral blade and the second spiral blade are arranged in a clockwise and counterclockwise symmetrical Archimedean spiral.

[0012] Optionally, the coordinate equation of the Archimedean spiral is:

[0013]

[0014] Where α represents the distance from the starting point to the origin of the polar coordinates when θ=0°, and β represents the growth rate of the Archimedean spiral. represents the total angular displacement of the Archimedean spiral from the initial angle to the final angle, r represents the inner diameter of the spiral channel, R represents the outer diameter of the spiral channel, and θ represents the polar angle of the spiral channel.

[0015] Optionally, the inner diameter of the spiral channel is in the range of 1-5 mm, the outer diameter of the spiral channel is in the range of 32-40 mm, the polar angle of the spiral channel is in the range of 2π-6π, and the length L of the upper sealing plate and the lower sealing plate is in the range of 80-120 mm.

[0016] Optionally, the structure further includes a front baffle and a rear baffle, wherein the front baffle is arranged between the second spiral blade and the right side plate, and the rear baffle is arranged between the first spiral blade and the left side plate.

[0017] Optionally, the front and rear baffles are both concave arc-shaped plates.

[0018] Optionally, one end of the front baffle is tangentially arranged to the second spiral blade, and one end of the rear front baffle is tangentially arranged to the first spiral blade.

[0019] Optionally, the other end of the front baffle is arranged at the intersection of the right side plate and the upper and lower sealing plates, and the other end of the rear baffle is arranged at the intersection of the left side plate and the upper and lower sealing plates.

[0020] Correspondingly, the present invention also provides a ventilation and sound insulation window, comprising a plurality of the above-mentioned ventilation and sound insulation structures based on spiral channels, wherein the plurality of ventilation and sound insulation structures are arranged in a rectangular array, wherein each column comprises a plurality of ventilation and sound insulation structures stacked up and down, and the flanges of two adjacent ventilation and sound insulation structures in each row are in close contact, so that a ventilation channel is formed between the two adjacent ventilation and sound insulation structures, which is closed up and down, left and right, and open front and back.

[0021] The present invention provides the following beneficial effects: In its first aspect, it provides a spiral channel-based ventilation and sound insulation structure. Upper and lower sealing plates are provided at the top and bottom of the structure to form a vertically enclosed boundary, preventing sound wave leakage and providing structural support and wave guidance for the internal spiral channel. Left and right panels are provided on either side of the structure to define the ventilation channel boundary and form the outer shell of the central spiral cavity. Flanges are provided on the outer sides of the left and right panels of the upper and lower sealing plates to form equal-width ventilation channels on both sides of the structure. This straight-through path allows free air flow, thereby ensuring ventilation efficiency. A double spiral channel is formed by providing first and second spiral blades within the sound absorption cavity. This extends the propagation path of sound waves within the cavity, resulting in significant phase delay, reflection, and interference attenuation, thereby achieving excellent sound insulation performance. The present invention utilizes an acoustic metamaterial structure designed based on the Fano resonance principle to achieve effective sound insulation within a wide mid-frequency range in a thin configuration. Compared to traditional sound insulation materials that rely on increased mass and thickness, this invention overcomes the limitations of the "sound insulation mass law," reducing structural weight while maintaining sound insulation performance. In addition, the structural parameters of the present invention are adjustable, and the sound insulation frequency band can be flexibly designed and optimized according to the actual noise environment, thereby having the advantages of lightweight, broadband sound insulation and strong adaptability.

[0022] The second aspect of the present invention provides a ventilated soundproof window, which is formed by arranging multiple ventilated soundproof structures in a rectangular array, and forming a ventilation channel between two adjacent ventilated soundproof structures in each row, which is closed in the top, bottom, left, right, and right, and open in the front and back. The double helix channel can significantly reduce the interference of sound wave propagation and maintain excellent sound insulation effect. The ventilation channel can achieve efficient air circulation capacity and significantly improve the smoothness of airflow. The ventilated soundproof window of the present invention supports modular combination and can be spliced ​​by multiple unit arrays to meet the needs of large-area sound insulation and ventilation. This scalability enables it to adapt to a variety of application scenarios from small indoor soundproof windows to large-scale industrial or public facilities. At the same time, the modular design facilitates transportation, installation and maintenance, further reducing the cost of use. Compared with the defect of traditional soundproof windows that rely on sealing and have insufficient ventilation performance, the present invention breaks through the technical bottleneck of difficulty in balancing ventilation and sound insulation performance, and provides an innovative solution for scenarios that require a quiet environment and air circulation needs.

[0023] The present invention achieves dual optimization of ventilation and sound insulation performance through ingenious structural design. The ventilation channels on both sides of the structure are specifically designed for air circulation, ensuring smooth airflow, achieving efficient air circulation capacity, and effectively improving ventilation performance. The spiral channels, through their unique design, play a sound insulation role, significantly reducing interference with sound wave propagation and maintaining excellent sound insulation. Through the combined design of ventilation channels and spiral channels, the present invention successfully solves the technical bottleneck of traditional soundproof windows that are difficult to achieve both ventilation and sound insulation. It can be applied to scenarios such as airport terminals and residential buildings near transportation hubs that require both quietness and ventilation. Moreover, the optimized layout and lightweight design of the spiral channels and the hollow channels on both sides can effectively reduce airflow resistance and reduce ventilation system energy consumption. At the same time, it reduces the dependence on heavy sound insulation materials, significantly reduces the weight of the structure, saves material costs, achieves energy conservation and environmental protection goals, and meets the requirements of modern green buildings and energy conservation and emission reduction. The lightweight design not only saves space, but also improves the flexibility and aesthetics of the structure, and can adapt to various architectural styles and environmental requirements. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] The present invention will be further described below with reference to the accompanying drawings and embodiments, in which:

[0025] Figure 1 This is a schematic diagram of the structure of the ventilation and sound insulation structure based on the spiral channel provided by the present invention. Figure 1 ;

[0026] Figure 2 This is a schematic diagram of the structure of the ventilation and sound insulation structure based on the spiral channel provided by the present invention. Figure 2 ;

[0027] Figure 3 This is a schematic structural diagram of the ventilation and sound insulation window provided by the present invention;

[0028] Figure 4 This is a performance verification flow chart of the spiral channel-based ventilation and sound insulation structure provided by the present invention;

[0029] Figure 5 This is a schematic diagram of the principle of sound waves passing through the spiral channel-based ventilation and sound insulation structure provided by the present invention;

[0030] Figure 6 This is a diagram of a sound insulation calculation model for a spiral channel-based ventilation and sound insulation structure provided by the present invention;

[0031] Figure 7 This is a sound insulation finite element model diagram of the ventilation and sound insulation structure based on the spiral channel provided by the present invention;

[0032] Figure 8 This is a comparison diagram of acoustic simulation and experiment of the ventilation and sound insulation structure based on the spiral channel provided by the present invention;

[0033] Figure 9 1 is a diagram showing acoustic simulation results of the ventilation and sound insulation structure provided by the present invention at different incident angles;

[0034] Figure 10 This is a sound insulation calculation model diagram of the ventilation sound insulation window provided by the present invention;

[0035] Figure 11 This is a sound insulation finite element model diagram of the ventilation and sound insulation window provided by the present invention;

[0036] Figure 12 This is a comparison chart of acoustic simulation and experiment of the ventilation sound insulation window provided by the present invention;

[0037] Figure 13 This is a test diagram of the ventilation experiment of the ventilation sound insulation window provided by the present invention;

[0038] Figure 14 This is a diagram showing the experimental results of the ventilation performance of the ventilation and sound insulation window provided by the present invention;

[0039] Figure 15 It is a schematic diagram of the change of sound wave transmission loss and frequency with outer diameter provided by the present invention.

[0040] In the figure: 100 - ventilation and sound insulation structure based on spiral channel, 101 - upper sealing plate, 102 - lower sealing plate, 103 - left side plate, 104 - right side plate, 105 - first spiral blade, 106 - second spiral blade, 107 - sound absorption cavity, 108 - flange, 109 - front baffle, 110 - rear baffle, 200 - tachometer, 300 - fan. DETAILED DESCRIPTION

[0041] To make the objectives, technical solutions, and advantages of the present invention more clear, the technical solutions in the embodiments of the present invention will be clearly and completely described below in conjunction with the accompanying drawings of the embodiments of the present invention. Obviously, the described embodiments are part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts shall fall within the scope of protection of the present invention.

[0042] In the description of the present invention, it should be noted that the terms "center", "longitudinal", "lateral", "upper", "lower", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside" and the like to indicate directions or positional relationships are based on the directions or positional relationships shown in the accompanying drawings and are only for the convenience of describing the present invention and simplifying the description. They do not indicate or imply that the devices or elements referred to must have a specific direction, be constructed and operate in a specific direction, and therefore should not be understood as limiting the present invention. In addition, the terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance.

[0043] 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 an indirect connection through an intermediate medium, or it can be internal communication between two components. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to the specific circumstances. In addition, in the description of the present invention, unless otherwise specified, "multiple" and "several" mean two or more.

[0044] like Figure 1 、 Figure 2 As shown, the present invention provides a ventilation and sound insulation structure 100 based on a spiral channel, comprising an upper sealing plate 101, a lower sealing plate 102, a left side plate 103, a right side plate 104, a first spiral blade 105 and a second spiral blade 106;

[0045] The upper sealing plate 101 and the lower sealing plate 102 are arranged relative to each other with a certain distance between them.

[0046] The left side panel 103 and the right side panel 104 are vertically arranged at a certain distance between the upper sealing panel 101 and the lower sealing panel 102, so that a sound absorption cavity 107 that is closed up and down and left and right and open front and back is formed between the upper sealing panel 101, the lower sealing panel 102, the left side panel 103 and the right side panel 104. The upper and lower sealing panels extend outward along the outer sides of the left and right side panels to form flanges 108.

[0047] The first and second spiral blades are vertically arranged between the upper sealing plate and the lower sealing plate in a non-overlapping spiral manner and are located in the sound absorption chamber 107. The inner end of the first spiral blade is arranged at the center of the sound absorption chamber, and the outer end thereof is arranged on the inner side of the left plate. The inner end of the second spiral blade is arranged at the center of the sound absorption chamber, and the outer end thereof is arranged on the inner side of the right plate, so that the front opening of the sound absorption chamber is connected to the rear opening of the sound absorption chamber through the spiral channel between the first and second spiral blades.

[0048] In this embodiment, the upper sealing plate is arranged directly above the lower sealing plate. The upper and lower sealing plates are the same rectangular plates. The direction in which the flange extends is the width direction of the upper and lower sealing plates. The width of the upper and lower sealing plates is W, and their length is L. The left and right side plates are arranged between the upper and lower sealing plates along the length direction. The left and right side plates are the same rectangular plates. The height H of the left and right side plates is equal to the distance between the upper and lower sealing plates. The length of the left and right side plates is equal to the length of the upper and lower sealing plates. The distance between the left and right side plates is less than the width W of the upper and lower sealing plates. The width of the flange is S, the distance between the left and right side plates is W-2S; the cavity between the inner ends of the first and second spiral blades forms the inner circle of the spiral channel; the inner diameter r of the spiral channel is half the distance between the inner ends of the first and second spiral blades; the outer diameter R of the spiral channel is the distance between the center between the inner ends of the first and second spiral blades and the outer end of the first or second spiral blade; the height of the first and second spiral blades is equal to the distance between the upper and lower sealing plates; the thickness of the upper and lower sealing plates, the left and right plates are equal, and the thickness is represented by b. The entire structure of the present invention can be manufactured using ABS resin using 3D printing.

[0049] In one embodiment, Figure 1 、 Figure 2 As shown, the first spiral blade and the second spiral blade are arranged in a clockwise and counterclockwise symmetrical Archimedean spiral, that is, the spiral channel is an Archimedean spiral channel, and the Archimedean spiral coordinate equation is:

[0050]

[0051] Where α represents the distance from the starting point to the polar coordinate origin when θ = 0° (unit: mm), β represents the growth rate of the Archimedean spiral (unit: mm / °), represents the total angular displacement of the Archimedean spiral from the initial angle to the final angle (unit: rad), r represents the inner diameter of the spiral channel, R represents the outer diameter of the spiral channel, and θ represents the polar angle of the spiral channel.

[0052] In one embodiment, Figure 1 、 Figure 2As shown, the inner diameter r of the spiral channel ranges from 1 to 5 mm, the outer diameter R of the spiral channel ranges from 32 to 40 mm, the polar angle θ of the spiral channel ranges from 2π to 6π, and the length L of the upper and lower sealing plates ranges from 80 to 120 mm.

[0053] Through experimental analysis, the present invention found that the structural parameters of the ventilation sound insulation structure have an impact on the transmission loss, and the following optimized parameters were obtained: inner diameter r is [1-5] mm, outer diameter R is [32-40] mm, polar angle θ is [2π-6π], and length L is [80-120] mm. While maintaining a constant inner diameter, the ventilation area can be effectively controlled by adjusting the outer diameter of the structure. Five outer diameter parameters of 32, 34, 36, 38, and 40 mm were selected for comparative research. The corresponding ventilation rates were 36%, 32%, 28%, 24%, and 20%, respectively. The results of the influence of outer diameter on transmission loss are shown in the figure below. Figure 15 As shown. Figure 15 It can be seen that the acoustic performance of the structure under different parameters changes. As the outer diameter R value increases (the ventilation rate decreases accordingly), the acoustic coupling effect between the Archimedean spiral channel and the adjacent cavity is significantly enhanced, resulting in a significant narrowing of the working frequency bandwidth. At the same time, the transmission loss within the working frequency band continues to increase. Therefore, when designing this structure, it is necessary to balance the relationship between the working frequency band bandwidth and the transmission loss.

[0054] The embodiments of the present invention adopt a channel design based on an Archimedean spiral to form a new ventilation and sound insulation structure based on Archimedean spiral acoustic metamaterials. It achieves sound insulation through a unique geometric design. By optimizing the airflow path and mirror-symmetrical arrangement, it significantly improves the symmetry and flow efficiency of the channel. The Archimedean spiral design not only achieves optimal space utilization but also produces a linear resonance effect, controls the frequency distribution of the fundamental frequency and higher-order modes, significantly reduces interference in sound wave propagation, enhances sound insulation performance, and maintains good ventilation.

[0055] The embodiments of the present invention achieve highly effective sound insulation across a wide frequency band (525Hz to 895Hz), capable of simultaneously blocking noise across multiple frequency ranges, with particular excellence in controlling mid-frequency noise. Through optimized structural design, the present invention overcomes the limitations of traditional sound insulation technologies, which are typically limited to specific frequency bands, ensuring consistent sound insulation across a wide frequency range. This broadband sound insulation capability makes the present invention suitable for complex noise environments and meets the sound insulation needs of diverse scenarios.

[0056] In one embodiment, Figure 1 、 Figure 2As shown, the structure further includes a front baffle 109 and a rear baffle 110. The front baffle 109 is disposed between the second spiral blade 106 and the right side plate 104, and the rear baffle 110 is disposed between the first spiral blade 105 and the left side plate 103. The front and rear baffles can guide sound waves so that they smoothly enter the spiral channel, thereby improving the sound insulation effect.

[0057] In one embodiment, Figure 1 、 Figure 2 As shown, both the front and rear baffles are concave arc-shaped plates, which can better guide sound waves and further improve the sound insulation effect. More preferably, one end of the front baffle is tangent to the second spiral blade, and one end of the rear baffle is tangent to the first spiral blade. The other end of the front baffle is located at the intersection of the right side panel and the upper and lower sealing plates, and the other end of the rear baffle is located at the intersection of the left side panel and the upper and lower sealing plates. This can further guide sound waves and further improve the sound insulation effect.

[0058] Correspondingly, such as Figure 3 As shown, the present invention also provides a ventilation and sound insulation window, including a plurality of ventilation and sound insulation structures 100 based on spiral channels, wherein the plurality of ventilation and sound insulation structures are arranged in a rectangular array of multiple rows and columns, wherein each column includes a plurality of ventilation and sound insulation structures stacked up and down, and the flanges of two adjacent ventilation and sound insulation structures in each row are in close contact, so that a ventilation channel is formed between the two adjacent ventilation and sound insulation structures, which is closed up and down, left and right, and open front and back.

[0059] The spiral channel-based ventilation and sound insulation structure (hereinafter referred to as ASMs ventilation and sound insulation structure) and ventilation and sound insulation window provided by the present invention were designed according to the geometric parameters in Table 1, and their ventilation and sound insulation performance was verified through experiments.

[0060] Table 1 Geometric parameters of ASMs ventilation and sound insulation structure

[0061] outer diameter inner diameter Polar angle thickness long Width high Flange width R(mm) r(mm) θ(°) b(mm) L(mm) W(mm) H(mm) S(mm) 37.9 3.15 3π 1 100 100 100 12.1

[0062] The performance verification flow chart of this test scheme is as follows Figure 4 As shown, it includes: analysis of sound waves passing through ASMs ventilation and sound insulation structure, establishment of COMSOL finite element simulation model, verification of sound insulation performance of ASMs ventilation and sound insulation structure, verification of the wide range of incident angles of ASMs ventilation and sound insulation structure, verification of sound insulation performance of ventilation and sound insulation windows, and verification of ventilation performance of ventilation and sound insulation windows.

[0063] The situation of sound waves passing through the ventilation and sound insulation structure based on the spiral channel provided by the present invention is as follows Figure 5 As shown, the specific steps are as follows: the characteristic impedance A of air is R1=p1c1, and the characteristic impedance B of the ventilation sound insulation structure is R2=p2c2, where ρ1 and c1 are the air density and air sound speed respectively, and ρ2 and c2 are the density and sound speed of the ventilation sound insulation structure respectively.

[0064] There is a plane acoustic wave (p i ,v i ) is incident vertically on the interface of the ventilation and sound insulation structure provided by the present invention, a part of the sound wave will be reflected in the air, forming a reflected wave (p 1r ,v 1r ); the other part penetrates the structure, recorded as (p 2t ,v 2t ), when the sound wave (p 2t ,v 2t ) travels to another interface of the ventilation and sound insulation structure, part of it will be reflected back to the structure due to the change of characteristic impedance, which is recorded as (p 2r ,v 2r ), the rest of the air penetrates into the air behind the structure and is recorded as (p t ,v t ), since the air extends to infinity, the transmitted wave (p t ,v t ) no longer reflects. p refers to the sound pressure of the sound wave, v refers to the speed of the sound wave, Figure 5 The arrow in the middle indicates the direction of velocity, for example, the vertically incident sound wave p i The reflected part of the sound wave is p 1r , the arrow part and p i On the contrary, the transmission part is p 2t , the arrow still points forward.

[0065] Each wave can be expressed as:

[0066]

[0067] In formula (1), the transmitted wave propagates along the positive direction of the coordinate axis, which is equivalent to the coordinate origin moving to the left by a distance L, which can be expressed as:

[0068]

[0069] The sound field in the air to the left of the structure is (p i ,v i ) and (p 1r ,v 1r ) is superimposed, the sound field in the medium on the right side of the structure is only (p t ,v t ), the sound field in the ventilation sound insulation structure is (p 2t ,v 2t ) and (p 2r ,v 2r ) of the superposition.

[0070] At x = 0, the sound pressure continuity and normal particle velocity continuity conditions are:

[0071]

[0072] The continuity conditions of sound pressure and normal particle velocity at x = D are:

[0073]

[0074] Since each wave is a plane wave, we have:

[0075]

[0076] Substituting Equation (5) into Equation (3) and Equation (4), the transmitted wave (p t ,v t ) and the sound pressure of the incident wave (p i ,v i )’s sound pressure ratio:

[0077]

[0078] Where,

[0079] From this, the sound intensity transmission coefficient can be obtained:

[0080]

[0081] The sound insulation capacity of the ventilation sound insulation structure is described by the sound transmission loss (i.e. sound insulation), which is defined as

[0082]

[0083] This test plan uses COMSOL software to perform simulation calculations on the performance verification of the ASMs ventilation and sound insulation structure. The sound insulation calculation model and finite element model of the ASMs ventilation and sound insulation structure are as follows: Figure 6 、 Figure 7 As shown. Figure 7 As shown in the figure, the finite element model consists of three main parts: the square air waveguide area on both sides and the sound insulation unit in the middle. The simulation and experimental results of the transmission loss of the ASMs ventilation sound insulation structure in the frequency domain are shown in the figure. Figure 8As shown, it can be observed that the transmission loss graph shows an asymmetric Fano line shape, and the ASMs ventilated sound insulation structure has complete transmission peaks at 471Hz and 984Hz, achieving efficient sound wave transmission and showing energy leakage. This asymmetric resonance will produce two anti-resonance points after the first complete transmission peak, at 565Hz and 851Hz respectively. The sound waves show total reflection at this frequency, achieving the purpose of sound insulation. At 525-895Hz (defined as the working frequency band), the transmission loss of the ventilated sound insulation structure is greater than 13.5dB, and can reach a maximum of 35dB. It can be seen that the ventilated sound insulation structure provided by the present invention breaks through the limitation of the narrow working frequency range, can block the propagation of broadband sound waves, and specifically can block more than 90% of the incident sound waves in the 525-895Hz range. The overall trend of the experimental results and the simulation results is basically consistent.

[0084] In practice, the function of the ASMs ventilation and sound insulation structure should not be limited to normal incidence. Considering the subwavelength characteristics of the proposed acoustic metamaterial structure, it is expected that silence will also occur under oblique incidence. In order to verify this expectation, the sound insulation performance of the proposed ASMs ventilation and sound insulation structure under oblique incidence was simulated by numerical simulation. The sound wave was incident at 0° normal incidence and 15°, 30° and 45° oblique incidence, and the distribution of the transmission loss of the ASMs ventilation and sound insulation structure in the frequency domain was obtained as shown in the figure below. Figure 9 As shown. The simulation results show that the broadband characteristics are observable within a wide range of incident angles. Complete blockage under oblique incidence occurs at exactly the same frequency as under normal incidence. When sound waves are incident at different angles, the present invention can exhibit excellent broadband characteristics. Even under large changes in the incident angle, its sound insulation performance remains stable. The characteristic frequency points and sound insulation frequency bands under oblique incidence are the same as those under vertical incidence. It can be seen that the present invention has a high degree of adaptability to normal and oblique incident sound waves in terms of sound insulation performance. Whether it is normal or oblique incidence, the design of the present invention can maintain excellent sound insulation effects. Compared with the shortcomings of traditional soundproof windows that are only good for normal incident sound waves and the sound insulation effect is significantly reduced under oblique incidence, the present invention uses acoustic metamaterials and spiral channel design to ensure effective blocking of multi-angle sound waves. This adaptability to the angle of incidence enables it to cope with complex noise environments, perform multi-directional noise control, and provide a reliable solution for sound insulation needs in multiple scenarios.

[0085] In order to study the performance of this new type of ventilation and sound insulation window, this experiment uses a 5×5 array design of ASMs ventilation and sound insulation structure to obtain the following Figure 3 The ventilated soundproof windows shown. Figure 10 、 Figure 11The sound insulation calculation model and finite element model established using COMSOL software for simulating ventilated soundproof windows are presented. To realistically simulate the semi-anechoic chamber environment, the boundaries surrounding the geometric model are defined as perfectly matched layers to ensure that sound waves are non-reflective upon reaching the boundaries, thereby preventing the impact of boundary interference on the sound field. The boundaries of the ventilated soundproof windows are defined as hard sound field boundaries, i.e., rigid boundary conditions, and the boundary material properties do not affect the simulation results. In the ventilated soundproof window model, special consideration is given to the acoustic energy dissipation caused by thermoviscous effects within the airflow channel. By introducing thermoviscous boundary layer impedance, the acoustic impedance characteristics of the tiny airflow channel are simulated, reflecting the acoustic behavior within the actual airflow channel.

[0086] Figure 12 The transmission loss characteristics of the ventilation sound insulation window provided by the present invention are shown. The results are obtained by comparing the experimental data obtained by finite element simulation calculation and semi-anechoic chamber experiment. Figure 12 It can be observed that the ventilation soundproof window exhibits an obvious asymmetric resonance effect. After the full transmission peak (about 471Hz), two significant anti-resonance points appear, located at 565Hz and 851Hz respectively. From the frequency range, the structure has a good sound insulation effect in the range of 525Hz to 895Hz, indicating that it can effectively weaken the transmission of sound waves in this frequency band. In addition, the simulation curve and the experimental curve show good consistency in the frequency range and the attenuation level of transmission loss. This shows that the finite element model can accurately reflect the actual acoustic performance of the ventilation soundproof window and verify the sound insulation effect of the designed structure.

[0087] Next, the ventilation characteristics of the ventilation sound insulation window provided by the present invention are experimentally evaluated. Figure 13 As shown, an electric fan 300 is placed at the entrance, and the handheld velocimeter 200 is used to measure the wind speed at the outlet five times with and without the ventilation and sound insulation window provided by the present invention. The handheld velocimeter is placed in a specific position, the fan is turned on and adjusted to five different gears in turn, and the corresponding wind speed values ​​are recorded respectively. This set of data is A. Subsequently, the ventilation and sound insulation window provided by the present invention is placed under the same test environment, and the handheld velocimeter is located in the same measurement position. The electric fan is again adjusted to the five gears corresponding to the previous ones, and five wind speed values ​​are measured and obtained one by one. This set of data is recorded as B. By calculating the ratio B / A of the corresponding data of B and A, the ratio of wind speed change with and without the ventilation and sound insulation window can be obtained, that is, the ventilation rate. The ventilation rate can intuitively reflect the ventilation rate characteristics of the window, and provides a key quantitative basis for evaluating its ventilation performance. The ventilation performance of the ventilation and sound insulation window provided by the present invention is as follows. Figure 14The experimental results show that the velocity at the outlet of the experimental test channel (measurement position of the handheld velocimeter) is linearly dependent, and the ventilation rate is about 27%, indicating that the air flow is reduced by about one third.

[0088] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, rather than to limit it. Although the present invention has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the aforementioned embodiments, or make equivalent replacements for some of the technical features therein. These modifications or replacements do not deviate the essence of the corresponding technical solutions from the spirit and scope of the technical solutions of the various embodiments of the present invention, and should all fall within the scope of protection of the claims attached to the present invention.

Claims

1. A ventilation and sound insulation structure based on a spiral channel, characterized in that: It includes an upper sealing plate, a lower sealing plate, a left side plate, a right side plate, a first spiral blade and a second spiral blade; The upper sealing plate and the lower sealing plate are arranged relative to each other with a certain distance between them; The left and right panels are vertically arranged at a certain distance between the upper and lower sealing panels, so that a sound absorption cavity that is closed up and down, left and right, and open front and back is formed between the upper and lower sealing panels, and the upper and lower sealing panels extend outward along the outer sides of the left and right panels to form flanges; The first and second spiral blades are vertically arranged between the upper sealing plate and the lower sealing plate in a non-overlapping spiral manner and are located in the sound absorption cavity. The inner end of the first spiral blade is arranged at the center of the sound absorption cavity, and the outer end thereof is arranged at the inner side of the left plate. The inner end of the second spiral blade is arranged at the center of the sound absorption cavity, and the outer end thereof is arranged at the inner side of the right plate, so that the front opening of the sound absorption cavity is connected to the rear opening of the sound absorption cavity through the spiral channel between the first and second spiral blades.

2. The ventilation and sound insulation structure based on the spiral channel according to claim 1, characterized in that: The first spiral blade and the second spiral blade are arranged in a clockwise and counterclockwise symmetrical Archimedean spiral.

3. The ventilation and sound insulation structure based on the spiral channel according to claim 2, characterized in that: The coordinate equation of the Archimedean spiral is: α=r,β=(Rr) / θ, Where α represents the distance from the starting point to the origin of the polar coordinates when θ=0°, and β represents the growth rate of the Archimedean spiral. represents the total angular displacement of the Archimedean spiral from the initial angle to the final angle, r represents the inner diameter of the spiral channel, R represents the outer diameter of the spiral channel, and θ represents the polar angle of the spiral channel.

4. The ventilation and sound insulation structure based on the spiral channel according to claim 3, characterized in that: The inner diameter r of the spiral channel is in the range of 1-5 mm, the outer diameter R of the spiral channel is in the range of 32-40 mm, the polar angle θ of the spiral channel is in the range of 2π-6π, and the length L of the upper and lower sealing plates is in the range of 80-120 mm.

5. The ventilation and sound insulation structure based on the spiral channel according to claim 1, characterized in that: The structure further comprises a front baffle and a rear baffle, wherein the front baffle is arranged between the second spiral blade and the right side plate, and the rear baffle is arranged between the first spiral blade and the left side plate.

6. The ventilation and sound insulation structure based on the spiral channel according to claim 5, characterized in that: The front and rear baffles are both concave arc-shaped plates.

7. The ventilation and sound insulation structure based on the spiral channel according to claim 5 or 6, characterized in that: One end of the front baffle is tangentially arranged to the second spiral blade, and one end of the rear front baffle is tangentially arranged to the first spiral blade.

8. The ventilation and sound insulation structure based on the spiral channel according to claim 7, characterized in that: The other end of the front baffle is arranged at the intersection of the right side plate, the upper sealing plate and the lower sealing plate, and the other end of the rear baffle is arranged at the intersection of the left side plate, the upper sealing plate and the lower sealing plate.

9. A ventilation and sound insulation window, characterized in that: The invention comprises a plurality of spiral channel-based ventilation and sound insulation structures according to any one of claims 1 to 8, wherein the plurality of ventilation and sound insulation structures are arranged in a rectangular array, and each column comprises a plurality of ventilation and sound insulation structures stacked up and down, and the flanges of two adjacent ventilation and sound insulation structures in each row are in close contact, so that a ventilation channel that is closed up and down, left and right, and open front and back is formed between the two adjacent ventilation and sound insulation structures.

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