CN111561252A - Broadband ventilation sound insulation window unit structure and application thereof - Google Patents

Broadband ventilation sound insulation window unit structure and application thereof Download PDF

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CN111561252A
CN111561252A CN202010250511.4A CN202010250511A CN111561252A CN 111561252 A CN111561252 A CN 111561252A CN 202010250511 A CN202010250511 A CN 202010250511A CN 111561252 A CN111561252 A CN 111561252A
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helical
broadband
ventilation
horn
sound insulation
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王旭
李勇
孙曼
毛东兴
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Tongji University
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    • E—FIXED CONSTRUCTIONS
    • E06—DOORS, WINDOWS, SHUTTERS, OR ROLLER BLINDS IN GENERAL; LADDERS
    • E06B—FIXED OR MOVABLE CLOSURES FOR OPENINGS IN BUILDINGS, VEHICLES, FENCES OR LIKE ENCLOSURES IN GENERAL, e.g. DOORS, WINDOWS, BLINDS, GATES
    • E06B5/00—Doors, windows, or like closures for special purposes; Border constructions therefor
    • E06B5/20—Doors, windows, or like closures for special purposes; Border constructions therefor for insulation against noise
    • E06B5/205—Doors, windows, or like closures for special purposes; Border constructions therefor for insulation against noise windows therefor
    • E—FIXED CONSTRUCTIONS
    • E06—DOORS, WINDOWS, SHUTTERS, OR ROLLER BLINDS IN GENERAL; LADDERS
    • E06B—FIXED OR MOVABLE CLOSURES FOR OPENINGS IN BUILDINGS, VEHICLES, FENCES OR LIKE ENCLOSURES IN GENERAL, e.g. DOORS, WINDOWS, BLINDS, GATES
    • E06B7/00—Special arrangements or measures in connection with doors or windows
    • E06B7/02—Special arrangements or measures in connection with doors or windows for providing ventilation, e.g. through double windows; Arrangement of ventilation roses
    • G—PHYSICS
    • G10—MUSICAL INSTRUMENTS; ACOUSTICS
    • G10K—SOUND-PRODUCING DEVICES; METHODS OR DEVICES FOR PROTECTING AGAINST, OR FOR DAMPING, NOISE OR OTHER ACOUSTIC WAVES IN GENERAL; ACOUSTICS NOT OTHERWISE PROVIDED FOR
    • G10K11/00—Methods or devices for transmitting, conducting or directing sound in general; Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
    • G10K11/16—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
    • G10K11/161—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general in systems with fluid flow

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Abstract

The invention relates to a broadband ventilation sound insulation window unit structure and application thereof, wherein the broadband ventilation sound insulation window unit structure comprises an internal helical blade (1), a hollow pipe (2) and a thin-wall shell (3), the outer wall of the hollow pipe (2) is fixedly connected with the internal helical blade (1), the outer edge of the internal helical blade (1) is covered with the thin-wall shell (3), the internal helical blade (1) comprises a fixed helical layer (5) arranged around the center of the outer wall of the hollow pipe (2) and horn-shaped helical layers (4) arranged on two sides of the fixed helical layer (5), the helical blade of the fixed helical layer (5) is a blade with a fixed pitch, and the helical blade of the horn-shaped helical layer (4) is a helical blade with a pitch gradient change. Compared with the prior art, the invention has the advantages of improved sound insulation effect, wide application range and the like.

Description

Broadband ventilation sound insulation window unit structure and application thereof
Technical Field
The invention relates to the technical field of noise treatment equipment, in particular to a unit structure of a broadband ventilation sound insulation window and application thereof.
Background
The traditional sound barrier ignores the circulation of air while isolating noise, but there are many special occasions that ventilation is needed besides noise reduction, for example, natural ventilation in modern green buildings becomes a key measure, but the accompanying external noise is inevitably brought to residents. In order to achieve the effects of ventilation and sound insulation, a common strategy is to additionally install a ventilation pipeline paved with a sound lining or a perforated partition plate, and during actual application, the ventilation pipeline is generally designed into a zigzag winding path, but the ventilation pipeline can bring large pressure difference while ensuring enough noise reduction amount, so that the ventilation effect is further reduced. Therefore, the design of the ventilation and sound insulation device usually faces the trade-off problem of ventilation effect and noise reduction.
The new field of acoustic metamaterials is developing vigorously, and their unique sub-wavelength dimensions and functional properties exhibit absolute advantages in acoustic manipulation, such as anomalous refraction and reflection, acoustic holography, and compact perfect acoustic absorbers. The advent of acoustic metamaterials in recent years has also provided new possibilities for the manufacture of ventilated sound barriers, using local resonance elements (such as Helmholtz resonators, membranes and 1/4 wave-length tubes) to achieve low frequency noise control at the sub-wavelength scale. In addition, Fano interference is utilized in the design of the double structure, so that the air circulation effect of the device is further improved, and meanwhile, the effective low-frequency sound insulation performance is ensured. However, the former utilizes the principle of local resonance that can only act at the resonance frequency, while the latter Fano resonance means that it has a narrow band of sound insulation only near a single frequency point where interference occurs. However, the metamaterial generally used for sound insulation is designed only by focusing on the internal path of sound waves, the refractive index is not matched with air at the boundary of the structure, and only a narrow-band sound insulation effect can be achieved. Considering the situation that noise is generally broadband, designing a broadband sound barrier is still a great challenge. Although there have been studies to widen the effective sound absorption band by using multiple resonances, the bandwidth is limited or the ventilation effect is reduced to some extent. In addition, the conventional ventilation and sound insulation window is generally formed by paving sound absorption materials or sound absorption structures in a zigzag ventilation pipeline, which increases the flow resistance and is far less effective than the ventilation effect of a direct ventilation path.
Disclosure of Invention
The present invention aims to overcome the defects of the prior art and provide a unit structure of a broadband ventilating sound-insulating window and an application thereof.
The purpose of the invention can be realized by the following technical scheme:
the utility model provides a wide band ventilation sound proof window unit structure, includes inside helical blade, hollow tube and thin wall shell, the inside helical blade of outer wall fixed connection of hollow tube, the thin wall shell is established to inside helical blade's outer fringe cover, the hollow tube is the rigidity cylinder hollow tube, the thin wall shell is annular shell. Inside helical blade is including locating the outer wall central authorities of hollow tube fixed spiral layer all around and the horn type spiral layer of fixed spiral layer both sides, the helical blade on fixed spiral layer is the blade of fixed pitch, the helical blade on horn type spiral layer is pitch gradient change's helical blade. The spiral structure of the horn-shaped spiral layer is formed by surrounding a central opening of a hollow pipe and a horn-shaped spiral plate. The pitch of the helical blades of the horn-shaped helical layer increases in a gradient manner from the pitch of the helical blades close to the middle fixed helical layer to the pitch of the helical blades at the outer edge position.
The spiral path of the spiral blade of the fixed spiral layer is as follows:
Figure BDA0002435315550000021
in the formula, xfix、yfix、ZfixThe length of rotation, ω s, of the helical blades of the fixed helical layer in the x, y and z axes, respectivelyfixIs the angle the helical blade rotates, omega is the angle the helical blade rotates by 1mm, sfixThe length of the helix is the angle of rotation, in mm, s0And-s0Are respectively sfixThe maximum and minimum values that can be taken; z is a radical offix＝a·sfixRepresents s in the z direction of a change in fixed pitchfixTaking a as a coefficient to change linearly, a as a coefficient of the fixed pitch layer blade changing linearly in the z axis, D as the inner diameter of the hollow pipe, D as the outer diameter of the annular shell, rfixThe width of the blade changes when the helical blade rotates, and the change range is [ D/2, D/2 ]]。
The helical path of the helical blade of the horn-shaped helical layer is:
Figure BDA0002435315550000022
in the formula, xhorn、yhorn、zhornThe length of rotation of the helical blades of the horn-shaped helical layer in the x, y and z axes, shornThe length of the helix is the angle of rotation, in mm, s1And s2Are respectively shornThe maximum and minimum values that can be taken;
Figure BDA0002435315550000031
d is the inner diameter of the hollow tube, D is the outer diameter of the annular shell, r is the initial phase for ensuring the connection of the fixed pitch blade and the horn-shaped helical bladehornThe width of the blade changes when the helical blade rotates, and the change range is [ D/2, D/2 ]]。
In order to make the fixed pitch blade and the horn type helical blade capable of being jointed, the x, y and z axis coordinates of the two blades at the joint are equal, there is
Figure BDA0002435315550000032
The value is determined by the values of the two helical blade layers s at the junction. The horn-type spiral layers are e-exponential in the z-axis direction compared to the fixed spiral layers. The pitch P refers to the distance that a single blade rotates for one circle to pass on the axis, and then the pitch of the fixed spiral layer and the pitch of the horn type spiral layer are respectively inferred to be P according to two spiral mode expressions fix2 pi a/ω and
Figure BDA0002435315550000033
and the equivalent refractive index can be described as the ratio of the path of the wave propagating in the structure to its path in the z-direction:
Figure BDA0002435315550000034
in the formula, reThe equivalent radius of the spiral is shown,the fitting value is about 0.498D/2, and the proper equivalent refractive index n is designed at the boundary of the horn-shaped layers on the two sides2(± h) may overcome the impedance mismatch problem at the boundary.
The second purpose of the invention is to provide a broadband sound barrier, which comprises a plurality of the broadband ventilation sound insulation window unit structures which are uniformly spliced in a basic mode.
Preferably, the broadband sound barrier comprises a plurality of square frames which are uniformly spliced in a basic mode, each square frame is embedded with the broadband ventilation and sound insulation window unit structure, and the broadband ventilation and sound insulation window unit structure is in transition fit with the square frames.
Preferably, the broadband sound barrier comprises a plurality of solid cubes 1/4 cylinders with the same size and cut off at four corners, wherein the solid cubes are evenly spliced in a basic mode, and each solid cube is embedded with the broadband ventilation and sound insulation window unit structure which is in transition fit with the solid cubes.
Compared with the prior art, the invention has the following beneficial effects:
1) the broadband ventilation sound insulation window unit structure is provided with a hollow fixed spiral layer and horn-shaped spiral layers arranged on two sides of the fixed spiral layer, the spiral blades of the fixed spiral layer are blades with fixed screw pitches, the spiral blades of the horn-shaped spiral layer are spiral blades with gradient change of the screw pitches, and the spiral structure of the horn-shaped spiral layer is formed by a central hole and a horn-shaped spiral plate in a surrounding mode;
2) the invention relates to a unit structure of a broadband ventilation sound-insulation window, which is provided with a hollow tube, wherein a central opening brought by the hollow tube is divided by a cylindrical spiral plate through a rigid cylindrical shell, so that cross coupling between the hollow tube and the spiral plate can be eliminated, the hollow tube is designed to reserve a path for direct circulation of air, and the traditional ventilation sound-insulation window is usually formed by paving a sound-absorbing material or a sound-absorbing structure in a zigzag ventilation pipeline, so that the flow resistance is increased, and the ventilation effect is far less good than that of the path for direct ventilation;
3) the invention has simple structure, can balance the single dipole mode response size in the system by adjusting the screw pitch of the peripheral spiral structure so as to achieve the broadband sound insulation effect of a specific frequency band, and can prove that a sample piece with the thickness of 5cm (lambda/8) can effectively isolate 90% of incident sound wave energy in each direction within the frequency band range of 900Hz-1418 Hz.
Drawings
FIG. 1 is a sound insulation schematic diagram of monopole and dipole response coupling in a metamaterial unit;
FIG. 2 is an external view of the structure of the broadband ventilating and sound insulating window unit according to the present invention;
FIG. 3 is a schematic diagram of the internal structure of the spiral path of the unit structure of the broadband ventilation and sound insulation window of the present invention;
FIG. 4 is a graph illustrating the coupling principle of the unit structure of the broadband ventilating sound-proof window according to the present invention;
FIG. 5 is a schematic view of a sound pressure transmission curve of the broadband ventilation and sound insulation window unit structure according to the present invention;
FIG. 6 is a graph of energy transmission in an experimental test of a unit structure of a broadband ventilation and sound insulation window according to the present invention;
fig. 7 is a graph of sound pressure transmission coefficients at oblique incidence angles of 0 °, 30 ° and 60 ° of sound waves;
FIG. 8 is a schematic structural diagram of a combined sound barrier with a basic unit design of a unit structure of a broadband ventilating sound-proof window according to the present invention;
FIG. 9 is a schematic structural diagram of a combined sound barrier of another structure formed by using the unit structure of the broadband ventilating sound-proof window of the present invention;
the reference numbers in the figures indicate:
1. the inner helical blade, 2, the hollow tube, 3, the thin-wall shell, 4, the horn-shaped helical layer, 5, the fixed helical layer, 6, the unit structure of the broadband ventilation sound insulation window, 7, the square frame, 8, the ventilation position, 9 and the solid cube.
Detailed Description
The invention is described in detail below with reference to the figures and specific embodiments. It is to be understood that the embodiments described are only a few embodiments of the present invention, and not all embodiments. All other embodiments, which can be obtained by a person skilled in the art without any inventive step based on the embodiments of the present invention, shall fall within the scope of protection of the present invention.
For the ventilation and sound insulation window unit of the double structure, when it is treated as a whole system, the surface response thereof may be divided into a monopole response and a dipole response, and the coupling result thereof may form a sound insulation effect. The invention proposes a solution for homogenizing a ventilation barrier that incorporates an eigenmode analysis, i.e. the transmission or reflection behaviour of the sound barrier can be described in terms of its eigenmode. The results show that the amplitude of the transmitted or reflected sound wave can be determined by analyzing the intensity of each independent response mode of the structure. The subwavelength scale of a structure determines the physical properties that it can represent in its entirety by the green's function, regardless of the complex structure inside it. The green's function can be expanded as the sum of a series of eigenfunctions:
Figure BDA0002435315550000051
in the formula of omeganIs a characteristic angular frequency of order n; p is a radical ofn(x) And
Figure BDA0002435315550000052
the eigenfunctions of the nth order eigenmodes at x and x' and their conjugates, respectively; b isnRepresenting the mean bulk modulus corresponding to the n-order characteristic mode, wherein
Figure BDA0002435315550000053
pn(x) And
Figure BDA0002435315550000054
is the integral of sound pressure over volume, S is the cross-sectional area of the metamaterial unit, B is the bulk modulus in air, and has
Figure BDA0002435315550000055
ρ0And c0Density and speed of sound of air, respectively. In the one-dimensional acoustic wave propagation model, the response of the system can be expressed as a monopole response with two ends moving in the same phase
Figure BDA0002435315550000056
Dipole response to anti-phase motion
Figure BDA0002435315550000057
Can be described as:
Figure BDA0002435315550000058
Figure BDA0002435315550000059
in the formulae (2) and (3), h and-h respectively represent coordinate values of the front and rear surfaces of the cell on the z-axis, pn(h) And pnThe (-h) represents the sound pressure average value of the n-order characteristic frequency corresponding to two end faces of the system respectively. Monopole response for any particular metamaterial unit
Figure BDA00024353155500000510
And dipole response
Figure BDA00024353155500000511
Eigenvalue analysis can be performed to calculate the eigenfunction and eigenfrequency according to equations (2) and (3).
Based on the equivalent medium theory, the metamaterial unit can be equivalent to an equivalent medium model with the same thickness and equivalent wave number
Figure BDA00024353155500000512
Satisfies the equation:
Figure BDA00024353155500000513
once the single-dipole mode is determined,
Figure BDA00024353155500000514
it may also be determined:
Figure BDA0002435315550000061
and equivalent impedance
Figure BDA0002435315550000062
Can also be expressed as:
Figure BDA0002435315550000063
then, the transmission coefficient of the metamaterial unit can be calculated by the following formula:
Figure BDA0002435315550000064
in the formula Z0Represents the characteristic impedance (Z) of air0＝ρ0c0) And is
Figure BDA0002435315550000065
Formula (5) also illustrates when present
Figure BDA0002435315550000066
In the limit case, the imaginary part of the equivalent wave number tends to infinity
Figure BDA0002435315550000067
Time means that the incident sound wave is strongly attenuated. In a physical sense, monopole and dipole responses of equivalent sizes exist in the unit at the same time. As shown in FIG. 1, the best sound insulation results from the equivalent sizeThe single dipole responses of (a) add and cancel each other. Under certain specific conditions, when the acoustic reactance in the formula (6) is infinite, the transmission coefficient corresponding to the formula (7) becomes 0 theoretically. Both of the above cases may illustrate that such metamaterials exhibit acoustically hard boundaries. However, even if the acoustic metamaterial has a large air path, the acoustic metamaterial still has the appearance of total reflection. In addition to this, the present invention is,
Figure BDA0002435315550000068
the single dipole response curve has an intersection point at a specific frequency, so that the sound insulation frequency band can be further widened by creating a plurality of intersection points for response, and the single dipole modal response is equivalent in size within a specific frequency range.
Based on the theoretical analysis of the unit structure model, the invention relates to a unit structure of a broadband ventilation sound insulation window, which comprises internal helical blades 1, a hollow pipe 2 and a thin-wall shell 3. The hollow tube 2 is a rigid cylindrical hollow tube, the outer wall of the hollow tube 2 is fixedly provided with an internal helical blade 1, the outer end of the outer edge of the internal helical blade 1 is provided with a thin-wall shell 3, and the thin-wall shell 3 is an annular shell.
Inside helical blade 1 includes horn type spiral layer 4 and fixed spiral layer 5, and the central point that hollow tube 2 was located to fixed spiral layer 5 puts, and the helical blade of fixed spiral layer 5 is the blade of fixed pitch. The blades with fixed pitch can avoid the influence on the processing of the closest part of the pitch due to the narrow spacing of the blades.
The horn-shaped spiral layer 4 is arranged at the front side and the rear side of the fixed spiral layer 5, and the spiral blades of the horn-shaped spiral layer 4 are spiral blades with the pitch changing in a gradient manner. The pitch of the blades of the horn-type helical layer 4 is smallest in the portion near the middle fixed helical layer 5, and the pitch of the blades increases toward the outer edge position. The helical structure of the horn-shaped helical layer 4 is formed by surrounding a central opening and a horn-shaped helical plate, the central opening is connected with the hollow tube 2, the hollow tube 2 is a rigid cylindrical shell, and the central opening and the horn-shaped helical plate are divided by the rigid cylindrical shell, so that cross coupling between the central opening and the horn-shaped helical plate can be eliminated. The matching effect of the structure and air is increased by the cylindrical gradient spiral blade layer, and the structure can be equivalent to a matching layer.
The modal coupling theory shows that the equilibrium of the response intensity of the monopole and the dipole in the system can break through the limitation of a narrow working frequency range. The open channels (hollow tubes) in the center of the structure ensure sufficient air flow and have a refractive index of 1, the refractive index n varying in the presence of the outer, cylindrical, spiral path2(z), this horn-like spiral path design for two reasons: the refractive index of the front surface boundary and the rear surface boundary of the unit can overcome the problem of impedance mismatch in the traditional narrow-band sound insulation design problem, and the adjustability of surface response in the unit structure also ensures that the transmission sound energy of single dipole modal response is attenuated violently in a proper frequency range.
The geometrical parameters of the cell structure of the invention are shown in fig. 2: external diameter D, internal diameter D and thickness 2h, external diameter D is the external diameter of annular shell, and internal diameter D is the internal diameter of hollow tube 2, and the thickness 2h of whole unit structure is the height of annular shell. Fig. 3 is an internal detail of the helical blade: the cylindrical helical blade layers are in mirror symmetry and are connected by blades with fixed screw pitches. The blades with fixed pitch can avoid the influence on the processing of the closest pitch part caused by the narrow pitch of the blades, and the surface response of the unit can be controlled by adjusting the thickness ratio (L/2h) of the fixed pitch layer relative to the integral structure.
The parameter equation of the spiral path of the fixed spiral layer 5 of the present invention is:
Figure BDA0002435315550000071
in the formula (8), xfix、yfix、zfixThe length of rotation of the helical blades, r, of the fixed helical layer in the x, y and z axes, respectivelyfixRepresenting the variation of the width of the helical blade during rotation, ranging from half the internal diameter to half the external diameter, ω sfixDenotes the angle of rotation of the helical blade, ω is the angle of rotation of the helical blade by 1mm, sfixThe length of the helix is the angle of rotation, in mm, s0And-s0Are respectively sfixThe maximum and minimum values that can be taken; z is a radical offix＝a·sfixRepresents s in the z direction of a change in fixed pitchfixAnd a is a coefficient which linearly changes in the z axis of the fixed pitch layer blade.
Referring to the variable cross-section sono-ultrasonic material, the parameter equation of the spiral path of the horn-shaped spiral layer 4 of the invention is as follows:
Figure BDA0002435315550000072
in the formula (9), xhorn、yhorn、zhornThe length of rotation of the helical blades, r, of the horn-type helical layer in the x, y, z axeshornRepresenting the variation of the width of the helical blade during rotation, ranging from half the internal diameter to half the external diameter, shornThe length of the helix is the angle of rotation, in mm, s1And s2Are respectively shornThe maximum and minimum values that can be taken;
Figure BDA0002435315550000081
the initial phase for securing the connection of the fixed pitch blade and the cylindrical helical blade is shown. In order to join the fixed pitch blades and the cylindrical helical blades, the x, y and z axis coordinates of the two blades at the joint are equal, there is
Figure BDA0002435315550000082
The value is determined by the values of the two helical blade layers s at the junction. The horn-type spiral layer 4 has an e-exponential change in the z-axis direction compared to the fixed spiral layer 5. The pitch P refers to the distance that a single blade rotates once and travels on the axis, and then the pitches of the fixed spiral layer 5 and the horn-shaped spiral layer 4 can be inferred to be P respectively from the formula (8) and the formula (9)fix2 pi a/ω and
Figure BDA0002435315550000083
and the equivalent refractive index can be described as the ratio of the path of the wave propagating in the structure to its path in the z-direction:
Figure BDA0002435315550000084
in the formula, reRepresenting the equivalent radius of the helix, with a fitting value of about 0.498D/2, and designing a suitable equivalent refractive index n at the boundaries of the horn-shaped layers on both sides2(± h) may overcome the impedance mismatch problem at the boundary.
In order to verify the effectiveness of the structure of the present invention in isolating acoustic energy, the present embodiment is simulated, and table 1 shows the structural parameters in calculation and simulation.
Table 1 structural parameters in calculations and simulations
Figure BDA0002435315550000085
The validity of the model design can be simulated and verified through a pressure acoustic module in COMSOL Multiphysics software. First, the eigenfrequency of the structure can be calculated using eigenfrequency analysis according to equations (8) and (9) to further calculate the single dipole mode. Fig. 4 shows a spectrum diagram of a monopole dipole response, and the intersecting frequency points of the curves are 1006Hz and 1326Hz, which means that the responses of single dipole modes with the same intensity form a broadband sound insulation effect. In the simulation calculation of acoustic transmission in the frequency domain, the structural unit is placed in a cylindrical waveguide, and the helical structure can be regarded as an acoustic hard boundary, both ends of the waveguide are set as acoustic radiation conditions, and incident acoustic wave conditions are set only at one end. Fig. 5 shows that the results of the numerical calculation of equation (7) fit the simulated predicted graph trend of the transmittance, demonstrating modal coupling and isolation of acoustic energy at 1006Hz and 1326 Hz.
In addition to theoretical calculations and simulations, this example also employed experiments to verify the effectiveness of the inventive structure this example utilizes Br ü el&
Figure BDA0002435315550000086
the type 4206 type impedance tube is measured by a dual-load method, the test sample is 3D printed by using a photosensitive resin material, and the test principle is thatThe sound pressure transmission coefficient was measured by the transfer matrix method, and the energy transmission coefficient was calculated based on this, as shown in fig. 7. As can be seen from the experimental data, more than 90% of the acoustic energy can be isolated in the frequency range of 900-1418 Hz. Compared with the traditional local resonance unit, the broadband structure design enlarges the application range.
Furthermore, in practical applications, the sound barrier is not limited to normal incidence only. In fact, the acoustic meta-surface consisting of sub-wavelength elements means that the one-dimensional motion of the acoustic particles along a central or spiral path is constrained within the meta-material element, with the angle of incidence being negligible. In fig. 7, the transmission coefficients of the sound barrier at different oblique incidence angles are studied by the simulation calculation method, and the structure still has a broadband sound insulation characteristic under the condition of incidence at a certain angle, and the frequency point of complete sound insulation is completely matched with that of vertical incidence, and even the sound insulation effect of oblique incidence at other frequency bands is better.
The unit structure of the broadband ventilation sound insulation window can construct a ventilation sound insulation barrier with larger volume by combining and processing the basic units, and can be applied to green buildings. When the method is applied to the broadband ventilation sound barrier, the arrangement mode is a mode that a plurality of ventilation sound insulation window units are spliced on the basis. Fig. 8 and 9 show two splicing examples, where in fig. 8, the unit structures 6 of the broadband ventilation and sound insulation window are embedded into the square frame 7 and then arranged, the unit structures 6 of the broadband ventilation and sound insulation window are in transition fit with the square frame 7, and the ventilation area after splicing is the area of the hollow center of each ventilation and sound insulation window unit plus the redundant areas on the four corners. Fig. 9 shows the broadband ventilation and sound insulation window unit structure 6 embedded in a solid cube 9, and then 1/4 cylinders with the same size are cut off at each corner of the solid cube 9 and spliced, and the ventilation area of the structure is the hollow center of each ventilation and sound insulation window unit plus the hollow center of the cylinder formed by combination. The arrangement of the unit structure of the broadband ventilation and sound insulation window applied to the broadband ventilation and sound barrier through basic splicing can be in various forms, and the two splicing modes of fig. 8 and 9 are preferred embodiments of the invention and do not represent the only embodiment.
While the invention has been described with reference to specific embodiments, the invention is not limited thereto, and those skilled in the art can easily conceive of various equivalent modifications or substitutions within the technical scope of the invention. Therefore, the protection scope of the present invention shall be subject to the protection scope of the claims.

Claims (10)

1. The utility model provides a wide band ventilation sound proof window unitized construction, its characterized in that, includes inside helical blade (1), hollow tube (2) and thin-walled shell (3), the inside helical blade (1) of outer wall fixed connection of hollow tube (2), thin-walled shell (3) are established to the outer fringe cover of inside helical blade (1), inside helical blade (1) is including number section of thick bamboo type helical layer (4) of locating the outer wall central authorities of hollow tube (2) fixed helical layer (5) all around and fixed helical layer (5) both sides, the helical blade of fixed helical layer (5) is the blade of fixed pitch, the helical blade of number section of thick bamboo type helical layer (4) is the helical blade of pitch gradient change.
2. The broadband ventilation and sound insulation window unit structure according to claim 1, wherein the hollow tube (2) is a rigid cylindrical hollow tube.
3. The broadband ventilation and sound insulation window unit structure according to claim 1, wherein the helical structure of the horn-shaped helical layer (4) is formed by surrounding a central opening of the hollow tube (2) and a horn-shaped helical plate, and the pitch of the helical blades of the horn-shaped helical layer (4) is increased in a gradient manner from the pitch of the helical blades close to the pitch of the helical blades of the middle fixed helical layer (5) to the pitch of the helical blades at the position of the outer side edge.
4. The broadband ventilation and sound insulation window unit structure according to claim 1, wherein the thin-walled enclosure (3) is an annular enclosure.
5. The broadband ventilation and sound insulation window unit structure according to claim 1, wherein the helical path of the helical blade of the fixed helical layer (5) is:
Figure FDA0002435315540000011
in the formula, xfix、yfix、zfixThe rotation length of the helical blade of the fixed helical layer (5) on the x, y and z axes is changed, omega sfixIs the angle the helical blade rotates, omega is the angle the helical blade rotates by 1mm, sfixThe length of the helix is the angle of rotation, in mm, s0And-s0Are respectively sfixThe maximum and minimum values that can be taken; z is a radical offix＝a·sfixRepresents s in the z direction of a change in fixed pitchfixA is taken as the coefficient which is linearly changed, a is the coefficient of the fixed pitch layer blade which is linearly changed on the z axis, D is the inner diameter of the hollow pipe (2), D is the outer diameter of the thin-wall shell (3), rfixThe width of the blade changes when the helical blade rotates, and the change range is [ D/2, D/2 ]]。
6. The broadband ventilation and sound insulation window unit structure according to claim 3, wherein the helical path of the helical blade of the cylindrical helical layer (4) is as follows:
Figure FDA0002435315540000021
in the formula, xhorn、yhorn、zhornThe rotation lengths of the helical blades of the cylindrical helical layer (4) on the x, y and z axes are changed, shornThe length of the helix is the angle of rotation, in mm, s1And s2Are respectively shornThe maximum and minimum values that can be taken;
Figure FDA0002435315540000022
d is the inner diameter of the hollow pipe (2) and D is the outer part of the thin-wall shell (3) for ensuring the initial phase of the connection of the fixed-pitch blade and the horn-shaped helical bladeDiameter rhornThe width of the blade changes when the helical blade rotates, and the change range is [ D/2, D/2 ]]。
7. The broadband ventilation and sound insulation window unit structure according to claim 1, wherein the pitch of the fixed spiral layer (5) is PfixThe pitch of the horn-shaped spiral layer (4) is 2 pi a/omega
Figure FDA0002435315540000023
a is coefficient of linear change of fixed pitch layer blade in z axis, shornThe blades of the horn-shaped helical layer (4) are rotated by the length of the angular helix.
8. A broadband sound barrier using the broadband ventilation and sound insulation window unit structure of claim 1, comprising a plurality of the broadband ventilation and sound insulation window unit structures uniformly spliced in a basic manner.
9. The broadband sound barrier of claim 8, wherein the broadband sound barrier comprises a plurality of square frames uniformly spliced in a basic manner, each square frame having the broadband ventilation and sound insulation window unit structure embedded therein, and the broadband ventilation and sound insulation window unit structure is in transition fit with the square frame.
10. The broadband sound barrier of claim 8, wherein the broadband sound barrier comprises a plurality of basic uniformly spliced 1/4-cylinder solid cubes with four cut-outs of the same size, each solid cube having the broadband ventilation and sound insulation window unit structure embedded therein, the broadband ventilation and sound insulation window unit structure being transition-fitted with the solid cube.
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