CN116246603A

CN116246603A - Resonance unit of frequency modulation ultrathin multifunctional low-frequency silencing device and application thereof

Info

Publication number: CN116246603A
Application number: CN202310262251.6A
Authority: CN
Inventors: 吴成昊; 管义钧; 孙宏祥; 葛勇; 袁寿其
Original assignee: Jiangsu University
Current assignee: Jiangsu University
Priority date: 2023-03-17
Filing date: 2023-03-17
Publication date: 2023-06-09

Abstract

The invention discloses a resonance unit of a frequency modulation and ultrathin multifunctional low-frequency silencing device and application thereof, wherein a square air resonant cavity is arranged in the resonance unit, the air resonant cavity is formed by surrounding two end surfaces and four spiral channels with the same structure, and the four spiral channels are arranged between the two end surfaces and are distributed in a central symmetry manner; the channel inlet and the channel outlet of the winding channel are communicated by a plurality of transverse serpentine bends and a plurality of longitudinal serpentine bends, and right-angle bends are arranged between the transverse serpentine bends and the longitudinal serpentine bends. The side length of the resonance unit reaches 1/11 lambda, the characteristic of depth sub-wavelength is achieved, the peak value of the acoustic energy absorption rate can reach more than 0.95, the side length of the resonance unit and the silencing effect of a low-frequency range can be guaranteed at the same time, the resonance unit has good acoustic absorption performance in the low-frequency range, the space occupation ratio of the resonance unit can reach 15%, and the space utilization rate can be effectively improved.

Description

Resonance unit of frequency modulation ultrathin multifunctional low-frequency silencing device and application thereof

Technical Field

The invention relates to the field of noise control, in particular to a resonance unit of a frequency modulation and ultrathin multifunctional low-frequency silencing device and application thereof.

Background

Noise pollution is the third most nuisance next to air pollution and water pollution, and noise cancellation means mainly focus on blocking in propagation paths and damping at sound sources. The low-frequency silencing/sound-insulating technology has wide practical application in the fields of building acoustics, mechanical production and the like, so that the research of the low-frequency silencing/sound-insulating technology is always focused on the scientific and engineering circles. Conventional sound damping/insulating materials mainly comprise porous and fibrous materials and micro-perforated plate structures with cavities. The performance of the traditional sound attenuation/insulation material strictly follows the law of mass density, and the problems of large side length and high density are brought in the low frequency range, so that the application range of the traditional sound attenuation/insulation material is limited. In recent years, the advent of acoustic metamaterials, and in particular acoustic supersurfaces, has provided new approaches to breaking through the limitations of traditional sound damping/insulating materials. The acoustic super surface has the characteristics of ultra-thin, openable and easy regulation, and the excellent sound wave control capability provides a theoretical scheme and a technical path for designing an ultra-thin and openable low-frequency silencing/sound-insulating structure.

The traditional resonance unit follows the law of mass density, the traditional resonance unit is required to increase the sound insulation amount by increasing the side length or the surface density of the unit, and the side length generally reaches 1/4 to 1/2 of the working wavelength, so that the problem of large side length and high density is faced in a low frequency range, or after the side length and the density are guaranteed, the sound energy density is lower in the low frequency range, the sound energy loss efficiency is low, and the sound insulation effect is poor, so that the traditional resonance unit cannot guarantee the sound insulation effect of the side length and the low frequency range of the resonance unit at the same time.

Disclosure of Invention

In order to realize the silencing effect of simultaneously guaranteeing the side length and the low frequency range of the resonance unit, the invention provides the resonance unit of the frequency modulation ultrathin multifunctional low frequency silencing device and the application thereof, wherein the channel inlet and the channel outlet of the winding channel are communicated by a plurality of transverse serpentine bends and a plurality of longitudinal serpentine bends, right-angle bends are arranged between the transverse serpentine bends and the longitudinal serpentine bends, the side length of the resonance unit is enabled to meet the deep sub-wavelength characteristic, the silencing effect of the side length and the low frequency range of the resonance unit can be guaranteed at the same time, and the ultrathin resonance unit has good sound absorption performance in the low frequency range.

The technical scheme adopted by the invention is as follows:

the resonance unit of the frequency modulation ultrathin multifunctional low-frequency silencing device is of an independent square resonance cavity structure, a square air resonance cavity is arranged in the resonance unit, the air resonance cavity is formed by surrounding two end faces and four winding channels with the same structure, the four winding channels are arranged between the two end faces, and the four winding channels are distributed in a central symmetry mode; the head and the tail of the curling channel are respectively provided with a sound channel inlet communicated with the outside and a sound channel outlet communicated with the air resonant cavity, so that the air resonant cavity is communicated with the outside through the curling channel;

the channel inlet and the channel outlet of the winding channel are communicated by a plurality of transverse serpentine bends or longitudinal serpentine bends; or is:

the channel inlet and the channel outlet of the winding channel are communicated by a plurality of transverse serpentine bends and a plurality of longitudinal serpentine bends, and right-angle bends are arranged between the transverse serpentine bends and the longitudinal serpentine bends.

Further, the serpentine transverse bends of the serpentine channel are four and the serpentine longitudinal bends are two; or the transverse serpentine bend is two and the longitudinal serpentine bend is four.

Further, the wall thickness t of the spiral channel is 1mm less than or equal to t less than or equal to 3mm, the width d of the spiral channel is 2mm less than or equal to d less than or equal to 6mm, and the side length w of the resonance unit is w=12×t+11×d.

Further, the resonance unit material adopts organic glass or resin.

The resonant units with the same parameters are arranged in an array mode and are arranged in front of the inner wall of the building space or the equipment, and any sound channel inlet of each resonant unit is opposite to the inner wall of the building space/the equipment and used for absorbing low-frequency sound waves in the building space or the equipment.

Further, the distance c between adjacent resonance units is 2w less than or equal to c less than or equal to 8w, and the distance q between the resonance units and the inner wall of the building space/equipment is q less than or equal to 20mm; the operating frequency range of the resonance unit applied to the inner wall of the building space/equipment is 310Hz-780Hz.

The utility model discloses a square pipeline/corridor/passageway, including resonance unit, square pipeline/corridor/passageway, the use of resonance unit, square pipeline/corridor/passageway one side or both sides inner wall are the recess that is provided with that is greater than resonance unit in array arrangement, resonance unit is located in the recess and trilateral being surrounded, arbitrary channel entry of resonance unit is just right square pipeline/corridor/passageway for the absorption of low frequency sound wave in the square pipeline/corridor/passageway.

Furthermore, the width e of the three-face gap between the resonance unit and the groove is less than or equal to 20mm, and the distance L between adjacent resonance units is w+2e less than or equal to L less than or equal to 7w; the operating frequency range of the resonance unit applied to the square pipe/corridor/passageway is 240Hz-790Hz.

The application of the resonance units is that a plurality of resonance units with the same parameters are arranged in an array into a multi-row structure for absorbing low-frequency sound waves in a non-closed environment

Furthermore, the resonance units with the same parameters are arranged in an array to form a double-row structure, and the interval a between adjacent resonance units in the same row is more than or equal to 1.2w and less than or equal to 1.6w; the interval b between two adjacent rows is more than or equal to 2.4w and less than or equal to 3w.

The beneficial effects of the invention are as follows:

the side length of the resonance unit reaches 1/11 lambda, the characteristic of deep sub-wavelength is achieved, the peak value of the acoustic energy absorption rate can reach more than 0.95, the side length of the resonance unit and the silencing effect of a low-frequency range can be guaranteed at the same time, the resonance unit has good sound absorption performance in the low-frequency range, the space occupation ratio of the resonance unit can reach 15%, and the space utilization rate can be effectively improved. In addition, the working frequency of the resonance unit can be adjusted through the wall thickness t of the spiral channel and the width d of the spiral channel, so that the resonance unit is convenient to be suitable for different working occasions.

When the resonance unit is applied to the square pipeline/corridor/channel, the sound insulation rate peak value of the resonance unit can still reach about 0.9 when the width of the square pipeline/corridor/channel is increased to 600mm, so that excellent sound insulation performance of the square pipeline/corridor/channel is reflected; and the working effect of the sound insulation device is hardly affected by the change of the distance L between two adjacent resonance units within the range of less than 500mm, so that the flexibility of selecting the distance between the two adjacent resonance units is reflected.

When the resonance unit is used for forming the sound insulation barrier, the sound insulation rate is lower than-10 dB in the frequency ranges of 550Hz-1450Hz and 1700Hz-2150Hz, the relative bandwidth is 90% and 23.4% respectively, the excellent ultra-wideband low-frequency sound insulation performance is shown, the sound insulation chamber is formed by the sound insulation barrier, the sound insulation rate of the sound insulation chamber in the frequency bands of 600Hz-1500Hz and 1700Hz-2000Hz is lower than 0.1, the corresponding relative bandwidth is 86% and 16% respectively, the excellent ultra-wideband all-dimensional low-frequency sound insulation effect is shown, and a certain gap exists between the adjacent resonance units, so that the excellent ventilation can be realized.

Drawings

FIG. 1 is a cross-sectional view of a resonant cell according to an embodiment of the present invention.

Fig. 2 is a 3D printed sample view of a resonant cell with one of its end faces removed according to an embodiment of the present invention.

Fig. 3 is a schematic diagram of a resonance unit applied to an inner wall of a building space/equipment according to a second embodiment of the present invention, where the schematic diagram of the resonance unit is a cross-sectional view.

FIG. 4 is a graph showing the absorption rate of acoustic energy of a second resonance unit according to an embodiment of the present invention.

FIG. 5 is a graph showing the variation of the wall thickness t of a second sinusoidal channel with respect to the operating frequency according to an embodiment of the present invention.

Fig. 6 is a graph showing the variation of the width d of the second sinusoidal channel with respect to the operating frequency according to the embodiment of the present invention.

Fig. 7 is a schematic diagram of a resonance unit applied to a square pipe/corridor/passageway according to a third embodiment of the present invention, wherein the schematic diagram of the resonance unit is a cross-sectional view.

FIG. 8 is a graph showing the frequency spectrum of the sound insulation rate of the third resonance unit according to the embodiment of the present invention.

Fig. 9 is a graph showing the relationship between the width H of the three-pipe and the peak value of the sound insulation rate according to the embodiment of the invention.

Fig. 10 is a graph showing the relationship between the three-phase resonance unit interval L and the peak value of the sound insulation rate according to the embodiment of the invention.

Fig. 11 is a schematic diagram of a sound-proof barrier formed by the resonance units according to the fourth embodiment of the present invention, and the schematic diagram of the resonance units is a cross-sectional view.

Fig. 12 is an experimental measurement device for sound absorption performance of a resonance unit according to a fourth embodiment of the present invention.

FIG. 13 is a graph of the acoustic transmittance spectrum of a resonating unit simulated and measured in accordance with a fourth embodiment of the present invention.

Fig. 14 is a schematic view of a sound insulation chamber formed by resonance units according to a fifth embodiment of the present invention, where the schematic view of the resonance units is a sectional view.

Fig. 15 is a graph of sound insulation for a five-simulation sound insulation chamber according to an embodiment of the present invention.

Reference numerals illustrate:

1. resonance unit, rigid wall, recess, 4, duct wall, 5, power amplifier, 6, data controller, 7, computer, 8, miniature microphone, 9, sound source, 10, sound absorbing sponge, 11, waveguide, 12, rigid support column, 101, channel outlet, 102, channel inlet, 103, crimped channel, 104.

Detailed Description

The present invention will be described in further detail with reference to the drawings, but the scope of the invention is not limited thereto.

Example 1

As shown in fig. 1 and fig. 2, the resonance unit of the muffler device is an independent square resonance cavity structure, and a square air resonance cavity is arranged in the resonance unit, the air resonance cavity is formed by surrounding two end surfaces 104 and four winding channels 103 with the same structure and positioned between the two end surfaces 104, and the four winding channels 103 are distributed in a central symmetry manner; the head and the tail of the curling channel 103 are respectively provided with a sound channel inlet 102 communicated with the outside and a sound channel outlet 101 extending towards the center of the air resonant cavity, so that the air resonant cavity is communicated with the outside through the curling channel 103; the channel inlet 102 and the channel outlet 101 of the winding channel 103 are communicated by four transverse serpentine bends and two longitudinal serpentine bends, and right-angle bends are arranged between the transverse serpentine bends and the longitudinal serpentine bends; or is: the channel inlet 102 and the channel outlet 101 of the winding channel 103 are communicated by two transverse serpentine bends and four longitudinal serpentine bends, and right-angle bends are arranged between the transverse serpentine bends and the longitudinal serpentine bends. The wall thickness t of the winding channel 103 is 1mm less than or equal to t less than or equal to 3mm, the width d of the winding channel 103 is 2mm less than or equal to d less than or equal to 6mm, and the side length w of the resonance unit is w=12×t+11×d. The resonance unit of the noise elimination device can be prepared by a 3D printing technology, and the used material can be one of organic glass and resin material.

Example two

As shown in fig. 3, the resonant units with the same parameters are arranged in an array manner and are arranged in front of the inner wall of a building space or equipment, any channel inlet 102 of each resonant unit is opposite to the inner wall of the building space/equipment to form a sound-damping wall structure, the sound energy absorption effect of the sound-damping wall is based on excitation of an intrinsic resonance mode of each resonant unit, the sound energy is absorbed into the interior of each resonant unit, the sound energy is dissipated through viscous friction between air and the wall in a narrow channel in the process, further, the sound energy absorption is realized, the sound-damping wall can be used for silencing and sound insulation of the building space and the equipment shell, noise pollution is reduced, and the array arrangement rule is as follows: the distance c between adjacent resonance units is more than or equal to 2w and less than or equal to 8w, and the distance q between the resonance units and the inner wall of the building space/equipment is less than or equal to 20mm.

Arranging the resonance units in front of the wall in an array mode according to the rule that the distance between the adjacent resonance units is c=600 mm and the distance between the resonance units and the wall is q=10 mm, enabling any channel inlet 102 of the resonance units to be opposite to the wall, namely, arranging two sides of the resonance units in parallel with the wall to form a silencing device of a silencing wall structure, enabling sound wave signals to be incident perpendicular to the wall, and enabling the used resonance unit parameters to be: the wall thickness t=2mm of the winding channel 103, the width d=6mm of the winding channel 103, the side length of the resonance unit is w=90mm, fig. 4 is a spectrogram of the acoustic energy absorption rate of the simulation experiment performed after the arrangement according to the above parameters and the above array, as can be seen from fig. 4, in the simulation experiment, the acoustic energy absorption rate of the silencing device is greater than 0.5 in the frequency range of 336Hz-365Hz, the relative bandwidth is 8.2%, the good low-frequency acoustic absorption performance is shown, the peak value is reached at the frequency of 352Hz, and the wavelength lambda is at the moment

Where v is the speed of sound and f is the frequency. The environmental sound velocity is 343m/s, the calculated wavelength lambda= 0.9744m, the side length w=90 mm of the resonance unit is 1/11 of the working wavelength, the characteristic of depth subwavelength is provided, the noise elimination effect of the resonance unit in a low-frequency range is guaranteed, the space ratio of the resonance unit is 15%, the space ratio calculation mode is the side length w of the resonance unit/the distance c between adjacent resonance units, and the noise elimination wall structure is provided with ultra-sparse characteristics.

The resonant units are arranged in front of the wall according to the rule that the distance between each two adjacent resonant units is c=600 mm, the distance between each resonant unit and the wall is q=10 mm, any channel inlet 102 of each resonant unit is opposite to the wall, the sound wave signal is vertically incident to the wall, the width d of each winding channel 103 is fixed to d=6 mm, the wall thickness t of each winding channel 103 is changed, the wall thickness t of each winding channel 103 is respectively set to be 1mm,2mm and 3mm, the changing relation between the wall thickness t of each winding channel 103 and the working frequency is shown in fig. 5, the working frequency of the sound-damping wall structure can be changed by adjusting the wall thickness t of each winding channel 103, the larger the wall thickness t of each winding channel 103 is, the working frequency of the sound-damping wall structure is smaller, and the peak frequency of the sound-absorbing frequency spectrum curve is changed within the range of 430Hz-700Hz, so that the adjustability of the working frequency of the sound-damping wall structure is shown.

The resonant units are arranged in front of the wall according to the rule that the distance between each two adjacent resonant units is c=600 mm, the distance between each resonant unit and the wall is q=10 mm, any channel inlet 102 of each resonant unit is opposite to the wall, the sound wave signal is vertically incident to the wall, the wall thickness t of each winding channel 103 is fixed to be t=2 mm, the width d of each winding channel 103 is changed, the widths d=3 mm,4mm and 5mm of each winding channel 103 are respectively set, the changing relation between the width d of each winding channel 103 and the working frequency is shown in fig. 6, the working frequency of the sound-absorbing wall structure can be changed by adjusting the width d of each winding channel 103, the larger the width d of each winding channel 103 is, the working frequency of the sound-absorbing wall structure is smaller, and the peak frequency of the sound-absorbing frequency spectrum curve is changed within the range of 394Hz-560Hz, so that the working frequency of the sound-absorbing wall structure is adjustable.

In addition, the working frequency of the sound-deadening wall structure can be scaled along with the integral structural parameters of the resonance unit, when all the structural parameters of the resonance unit are doubled, the working frequency of the sound-deadening wall structure is reduced to be one half of the original frequency, otherwise, if all the structural parameters of the resonance unit are reduced to be one half of the original frequency, the working frequency of the sound-deadening wall structure is doubled, and the working frequency is adjustable between 310Hz and 780Hz.

Example III

As shown in FIG. 7, the inner walls of one side or two sides of the square pipeline/corridor/passageway are arranged in an array and are provided with grooves 3 larger than the resonance units, the resonance units are positioned in the grooves 3 and surrounded on three sides, any sound channel inlet 102 of each resonance unit is opposite to the square pipeline/corridor/passageway to form a sound insulation device, the sound insulation device is used for absorbing low-frequency sound waves in the square pipeline/corridor/passageway, the sound insulation effect of the sound insulation device for the square pipeline/corridor/passageway is sound absorption and sound reflection caused by excitation of an intrinsic resonance mode of each resonance unit, the width e of a three-side gap between each resonance unit and each groove 3 is less than or equal to 20mm, and the distance L between every two adjacent resonance units is w+2e less than or equal to L less than or equal to 7w.

The inner wall of one side of the square pipeline is provided with two grooves 3 which are larger than resonance units and are arranged in an array manner, the two resonance units are positioned in the grooves 3 and are surrounded on three sides, any channel inlet 102 of each resonance unit is opposite to the square pipeline/corridor/channel to form a sound insulation device, acoustic signals are emitted in parallel with the pipeline, the gap width e between the resonance units and the grooves 3 is 10mm, the distance L between adjacent resonance units is 300mm, the pipeline with the width H being 400mm is adopted, and the parameters of the used resonance units are as follows: the wall thickness t=2mm of the winding channel 103, the width d=6mm of the winding channel 103, and the side length of the resonance unit is w=90mm. Fig. 8 is a graph of the acoustic energy absorption rate of the simulation experiment performed according to the above parameters and the above arrangement, and as can be seen from fig. 8, the sound insulation rate of the structure reaches 0.98 at 262Hz, excellent sound insulation effect is shown, the sound insulation rate exceeds 0.8 in the frequency band range of 250-276Hz, and the relative bandwidth reaches 10%. At the same time, the resonance unit does not affect the effective ventilation area of the duct.

The inner wall of one side of the square pipeline is provided with two grooves 3 which are larger than resonance units and are arranged in an array mode, the two resonance units are located in the grooves 3 and are surrounded on three sides, any channel inlet 102 of each resonance unit is opposite to the square pipeline/corridor/channel to form a sound insulation device, acoustic signals are emitted in parallel to the pipeline, the gap width e between each resonance unit and each groove 3 is 10mm, the distance L between every two adjacent resonance units is 300mm, and the parameters of the used resonance units are as follows: the wall thickness t=2mm of the winding channel 103, the width d=6mm of the winding channel 103, the side length of the resonance unit is w=90mm, and the width H of the pipeline is adjusted to obtain the relation change curve of the pipeline width H and the sound insulation rate peak value shown in fig. 9, and as can be seen from fig. 9, the sound insulation rate peak value is kept higher than 0.95 when the pipeline width H is increased to 500mm, and still can reach about 0.9 when the pipeline width is increased to 600mm, so that excellent pipeline sound insulation performance is realized.

The inner wall of one side of the square pipeline is provided with two grooves 3 which are larger than resonance units and are arranged in an array mode, the two resonance units are located in the grooves 3 and are surrounded on three sides, any channel inlet 102 of each resonance unit is opposite to the square pipeline/corridor/channel to form a sound insulation device, acoustic signals are emitted in parallel to the pipeline, the gap width e between the resonance units and the grooves 3 is=10mm, the pipeline with the width H=400mm is adopted, and parameters of the resonance units are as follows: the wall thickness t=2mm of the curling channel 103, the width d=6mm of the curling channel 103, the side length of each resonance unit is w=90mm, the adjacent resonance unit interval L is adjusted, the relation change curve of the adjacent resonance unit interval L and the sound insulation rate peak value shown in fig. 10 is obtained, as can be seen from fig. 10, the change of the interval L of the adjacent two resonance units within the range of below 500mm hardly affects the working effect of the sound insulation device, and the flexibility of selecting the interval of the adjacent two resonance units is reflected.

Example IV

As shown in FIG. 11, the resonant units with the same parameters are arranged in an array to form a multi-row structure to form a sound insulation barrier for absorbing low-frequency sound waves in a non-closed environment, and the sound insulation effect is based on the combined action of excitation of a plurality of intrinsic resonant modes of the resonant unit 1 and the forbidden band effect of a periodic structure, wherein the distance a between adjacent resonant units in the same row is equal to or less than 1.2w and equal to or less than 1.6w; the interval b between two adjacent rows is more than or equal to 2.4w and less than or equal to 3w.

Simulation is carried out by Comsol software, a resonance unit with the wall thickness t=2mm of the winding channel 103, the width d=3mm of the winding channel 103 and the side length w=57 mm of the resonance unit is constructed, and the material adopts the density 1180kg/m ³ Epoxy resin with longitudinal wave speed of 2720m/s and transverse wave speed of 1460m/s, and the simulated environment parameter is air density of 1.21kg/m ³ And the sound velocity 343m/s is achieved by arranging a plurality of resonance units in two rows in an array manner, wherein the interval a=80 mm between adjacent resonance units in the same row is equal to the interval b=160 mm between the two rows, sound waves are perpendicular to incidence of the sound insulation barrier, and the relationship between the sound insulation rate and the frequency of the sound insulation barrier formed by simulation is obtained, so that a simulated sound insulation rate spectrogram in FIG. 13 is obtained.

As shown in fig. 12, the simulation experiment is verified by adopting a four-sensor measurement method, the experimental device comprises a power amplifier 5, a data controller 6, a computer 7, a miniature microphone 8, a sound absorbing sponge 10 and a waveguide tube 11, a resonance unit to be tested is placed in the middle of the interior of the waveguide tube 11, four collecting points are arranged on the tube wall of the waveguide tube 11, the four collecting points are divided into two parts and are arranged on two sides of the tested sample, the miniature microphone 8 is arranged on the collecting points, the miniature microphone 8 is connected with the data controller 6 and is used for collecting and recording sound wave information, the data controller 6 is connected with the computer 7 and realizing the transmission of data and signals, the data controller 6 is connected with a sound source 9 through the power amplifier 5 and is used for realizing the control of the sound source 9, the sound source 9 is arranged at one end of the waveguide tube 11 and is used for emitting sound waves, and the two ends of the waveguide tube 11 are provided with the sound absorbing sponge 10 and are used for absorbing residual sound waves after the tested sample is subjected to sound insulation.

The size and material parameters of the adopted measured samples are the same as those of the simulation experiment, the two measured samples are arranged in parallel along the direction of the waveguide tube 11, the interval b=160 mm between the two measured samples, two rows of arrangement are realized, the waveguide tube 11 is composed of acrylic plates, the width of the waveguide tube 11 is 80mm, and the width of the waveguide tube is equal to a in the simulation experiment. The sound wave is emitted by the parallel waveguide tube 11, the miniature microphones 8 at the two ends of the measured sample collect sound wave information before and after sound insulation, and the sound wave information is transmitted to the computer 7 by the data controller 6 for recording and processing, so that a spectrogram of the measured sound transmittance in fig. 13 is obtained. As can be seen from fig. 13, the simulation and measurement results are better in accordance, the sound transmittance of the sound insulation barrier is lower than-10 dB in the frequency ranges of 550Hz-1450Hz and 1700Hz-2150Hz, the relative bandwidths are 90% and 23.4% respectively, excellent ultra-wideband low-frequency sound insulation performance is shown, a certain gap exists between every two adjacent resonance units, and good ventilation can be realized.

Example five

The sound insulation barrier in the fourth embodiment is formed into multiple surfaces to form a sound insulation chamber, in particular, the sound insulation chamber is formed by carrying out bearing on four rigid bearing columns 12, the four rigid bearing columns 12 are connected into four surfaces, two rows of resonance units with the same parameters are arranged on the four surfaces in an array manner to form a two-layer grid-like structure, and a four-surface sound insulation wall is formed.

The wall thickness t=2mm of the spiral channel 103 is adopted, the width d=3mm of the spiral channel 103, the side length of each resonance unit is w=57 mm, and the arrangement rule of the resonance unit array is as follows: the interval a=70 mm between adjacent resonance units in the same row, the interval b=150 mm between two rows, and the sound source point is arranged at the center O point of the sound insulation chamber. Fig. 15 is a sound insulation curve of a simulated sound insulation chamber, and as can be seen from fig. 15, the sound insulation rate of the sound insulation chamber in two frequency bands of 600Hz-1500Hz and 1700Hz-2000Hz is lower than 0.1, the corresponding relative bandwidths are 86% and 16% respectively, an excellent ultra-wideband omnibearing low-frequency sound insulation effect is shown, a certain gap exists between every two adjacent resonance units, and the ventilation performance is good.

The examples are preferred embodiments of the present invention, but the present invention is not limited to the above-described embodiments, and any obvious modifications, substitutions or variations that can be made by one skilled in the art without departing from the spirit of the present invention are within the scope of the present invention.

Claims

1. A resonance unit of a frequency modulation and ultrathin multifunctional low-frequency silencing device is characterized in that: the resonance unit is of an independent square resonance cavity structure, a square air resonance cavity is arranged in the resonance unit, the air resonance cavity is formed by surrounding two end faces (104) and four winding channels (103) which are arranged between the two end faces (104) and have the same structure, and the four winding channels (103) are distributed in a central symmetry manner; the head and the tail of the curling channel (103) are respectively provided with a sound channel inlet (102) communicated with the outside and a sound channel outlet (101) communicated with the air resonant cavity, so that the air resonant cavity is communicated with the outside through the curling channel (103);

the channel inlet (102) and the channel outlet (101) of the winding channel (103) are communicated by a plurality of transverse serpentine bends or longitudinal serpentine bends; or:

the channel inlet (102) and the channel outlet (101) of the winding channel (103) are communicated by a plurality of transverse serpentine bends and a plurality of longitudinal serpentine bends, and right-angle bends are arranged between the transverse serpentine bends and the longitudinal serpentine bends.

2. A resonant unit according to claim 1, characterized in that: the transverse serpentine turns of the serpentine channel (103) are four and the longitudinal serpentine turns are two; or the transverse serpentine bend is two and the longitudinal serpentine bend is four.

3. A resonant unit according to claim 2, characterized in that: the wall thickness t of the spiral channel (103) is 1mm less than or equal to t less than or equal to 3mm, the width d of the spiral channel (103) is 2mm less than or equal to d less than or equal to 6mm, and the side length w of the resonance unit is w=12×t+11×d.

4. A resonant unit according to claim 1, characterized in that: the resonance unit material adopts organic glass or resin.

5. Use of a resonance unit according to any one of claims 1-4, characterized in that: the resonance units with the same parameters are arranged in an array mode and are arranged in front of the inner wall of the building space or the equipment, and any sound channel inlet (102) of the resonance units is opposite to the inner wall of the building space/the equipment and used for absorbing low-frequency sound waves in the building space or the equipment.

6. Use of a resonant cell according to claim 5, characterized in that: the distance c between adjacent resonance units is 2w less than or equal to c less than or equal to 8w, and the distance q between the resonance units and the inner wall of the building space/equipment is q less than or equal to 20mm; the operating frequency range of the resonance unit applied to the inner wall of the building space/equipment is 310Hz-780Hz.

7. Use of a resonance unit according to any one of claims 1-4, characterized in that: the inner walls of one side or two sides of the square pipeline/corridor/channel are arranged in an array manner and are provided with grooves (3) which are larger than the resonance units, the resonance units are positioned in the grooves (3) and are surrounded on three sides, and any channel inlet (102) of each resonance unit is opposite to the square pipeline/corridor/channel and is used for absorbing low-frequency sound waves in the square pipeline/corridor/channel.

8. Use of a resonant cell according to claim 7, characterized in that: the width e of the three-face gap between the resonance unit and the groove (3) is less than or equal to 20mm, and the distance L between adjacent resonance units is w+2e less than or equal to L less than or equal to 7w; the operating frequency range of the resonance unit applied to the square pipe/corridor/passageway is 240Hz-790Hz.

9. Use of a resonance unit according to any one of claims 1-4, characterized in that: the resonance units with the same parameters are arranged in an array to form a multi-row structure and are used for absorbing low-frequency sound waves in a non-closed environment.

10. Use of a resonant cell according to claim 9, characterized in that: the resonance units with the same parameters are arranged in an array to form a double-row structure, and the interval a between adjacent resonance units in the same row is more than or equal to 1.2w and less than or equal to 1.6w; the interval b between two adjacent rows is more than or equal to 2.4w and less than or equal to 3w.