TW201404984A - Particle swarm method for optimizing sound absorbing panel structure - Google Patents

Abstract

The invention relates to a particle swarm method for optimizing sound absorbing panel structure, comprising the following steps: construction of a hybrid type sound absorbing system for full frequency and tuning, identification of an object to be achieved for system optimization, provision of an objective function for the best design strategy of the object, provision of a resource constraint formulation for proceeding with optimal calculation, initialization of parameters before the optimal calculation, namely, encoding of parameters to generate an initial position and an initial velocity of particles, and then calculation the initialized parameters with the objective function to get an answer to obtain a fitness value of the objective function of the particles, and comparison the fitness value of the objective function with the best fitness value of the objective function of the particles which are searched. If the error of the global best value is smaller than or equal to the preset minimum value or the iteration number is reached to the preset number, the calculation is completed. Otherwise, the optimal calculation for the parameters is continued.

Description

Method for optimizing sound absorbing panel structure by particle group method

The invention relates to a method for optimizing the structure of a sound absorbing panel by a particle group method, in particular to a four-dimensional transmission matrix method with a one-dimensional plane wave (low-order wave) and a particle swarm method for full-frequency and tuned hybrid type. The optimal operation analysis of the multi-variable design parameters of the sound absorbing system is to quickly and effectively seek the optimal solution of the numerical values of the parameters to eliminate the full-frequency (low-frequency, intermediate-frequency, high-frequency, pure-tone) reflected sounds in the factory.

According to the sound wave, the sound wave is a form of sound propagation. The sound wave can be transmitted by gas, liquid and solid, and its transmission mode includes reflection, refraction, diffraction, etc.; due to the development of scientific and technological civilization, life is full of various noises, such as vehicles. Engine noise, horn sound, aircraft or air-conditioning compressors, etc. Excessive noise often seriously affects mood and destructs the quality of life, especially the residents living on the elevated roads, the noise of the cars passing by, whether day or night It is quite annoying. Others are the generator room, machine room, factory and other places in the basement of the building. They are also the source of most noise, and “sound absorption” is one of the noise prevention methods, mainly to prevent the reflection and refraction of sound, or Reduce the energy of the sound wave itself to reduce its vibration and reduce the noise.

For example, there is a high level of echo in the closed factory, which not only directly endangers the health of employees, but also violates the 300 articles on volume exposure agents of the Labor Safety and Health Act. The amount of regulation, and the adverse effects of the above-mentioned noise, also indirectly lead to the decline of productivity and product quality, which in turn affects the competitiveness and production profit of the overall manufacturing business system; for the pursuit of sophisticated and high-quality precision process plants, the impact is huge In order to eliminate noise or avoid noise interference with others, the simplest and most common way is to provide sound insulation board (cotton) or sound absorbing board (cotton) on the surface of each wall and compartment in the factory to make sound waves. It is absorbed by these soundproofing or sound absorbing materials to block the transmission of sound waves, thereby reducing the echo in the factory.

However, at present, the control and research on effectively reducing the echo and noise reduction in the factory are only improved in the aspects of sound absorbing materials, sound absorbing originals, changing the structure of the sound absorbing panels or adding noise absorbing equipment, and the design parameters for the sound absorbing panels. It is also limited to the discussion of a single variable, so it lacks the ability to design and optimize the elasticity, and most of the sound insulation board (cotton) or sound-absorbing board (cotton) are set up in a trial and error manner, by selecting one by one. The sound absorbing panel is used for the analysis of the sound field in the closed building. The selection of materials is limited, and the design parameters cannot be adjusted. Therefore, a system of sound absorbing design with systematic, holistic and multi-variable design parameters is developed. Improved methods to control the echo in the factory do have its necessity.

Nowadays, the inventor is in view of the above-mentioned existing methods of reducing the echo and noise control in the factory, and there are still many defects in the actual implementation. Therefore, it is a tireless spirit, and with its rich professional knowledge and years of practical experience. The invention was assisted and improved, and the present invention was developed based on this.

The main object of the present invention is to provide a four-dimensional transfer matrix method of one-dimensional plane wave (low-order wave) and particle swarm optimization method for optimal operation analysis of multi-variable design parameters of a full-frequency and tuned hybrid sound absorbing system. And effectively seek the best numerical solution of the parameters, to eliminate the full frequency (low frequency, intermediate frequency, high frequency, pure tone) reflected sound in the factory.

In order to achieve the above-mentioned implementation object, the inventors propose a method for optimizing the structure of the sound absorbing panel by the particle group method, which at least includes the following steps: First, constructing a full frequency and tuning mixing type sound absorbing system, when the full frequency cum tuning type When the sound absorbing system is optimized by the particle swarm method, the required parameters are the shape, configuration and material properties of the components of the full-frequency and tuned hybrid sound absorbing system; after that, the above-mentioned full-frequency and tuned hybrid sound absorbing is defined. The goal to be achieved after the system is optimized; then, the objective function of the target optimal design strategy is provided; then, the resource limit of the parameter is provided; the connection is continued, the parameters are initialized, and the parameters are encoded to generate the initial position and initial velocity of the particle After that, the initialization parameters are substituted into the objective function solution to obtain the objective function adaptation value of the particle, and the fitness value of the objective function is compared with the optimal objective function value searched by the particle. The optimal objective function adaptation value is The individual's best value (pbest) and the group's best value (gbest) owned by the individual particles; finally, if the group is the most Value is better than or equal to a predetermined minimum value or when the number of iterations reaches the preset number of times, the operation is ended; otherwise repeat Step VI.

A method of optimizing a sound absorbing panel structure by a particle swarm method as described above, wherein the objective function includes maximizing sound absorption rate or minimizing sound power level (SWL) One of them.

The method of optimizing the structure of the sound absorbing panel by the particle group method as described above, wherein the full frequency and tuning mixed sound absorbing system is constructed based on the one-dimensional plane wave theory and the acoustic impedance of the Homer Holtz resonance chamber.

Furthermore, the full frequency and tuning hybrid sound absorbing system can be composed of a plurality of carrier plates and a plurality of punching plates connected to the carrier plate, wherein the carrier plate defines at least one tuning resonance cavity with an opening, and the punching plate Forming at least one sound absorbing body with the carrier plate; and the hole of the punching plate may further be provided with at least one tuning tube; in addition, the tuning resonance cavity or the sound absorbing body may be respectively provided with at least one layer of sound absorbing cotton.

The method for optimizing the structure of the sound absorbing panel by the particle group method as described above, wherein the component shape parameter of the full frequency cum tuning mixing type sound absorbing system may be selected from the group consisting of a punching inner diameter, a punching plate thickness, a punching plate opening ratio, and a sound absorbing cotton. The group of thicknesses may have a component configuration parameter selected from the group consisting of an air layer thickness, a tuning resonance neck diameter, a tuning resonance neck length, and a resonance cavity volume, and the component material property parameters include a sound absorbing cotton stream. impedance.

Therefore, the present invention provides a multi-variable design parameter optimization analysis of a full-frequency and tuned hybrid sound absorbing system in a closed factory by a one-dimensional plane wave (low-order wave) four-turn transmission matrix method and a particle swarm method. The system and the overall flexible design method are required to design the full-frequency and tuned hybrid sound absorbing system required in the limited space with optimized parameters, which can not only eliminate the full frequency (low frequency, intermediate frequency) in the closed building. , high frequency, pure tone) reflected sound, can also avoid the traditional method of trial and error, the material, manpower and time caused by the existing sound absorbing panels The waste of cost and inconvenience.

The object of the present invention and its structural and functional advantages will be explained in conjunction with the specific embodiments according to the structure shown in the following drawings, so that the reviewing committee can have a more in-depth and specific understanding of the present invention.

First, in the present specification, the direction facing the sound wave is the outward direction, and the direction from the outward direction toward the punching plate (2) is set from the outside to the inside.

Referring to the first figure, the flow chart of the method for optimizing the structure of the sound absorbing panel by the particle group method of the present invention mainly includes the following steps: Step 1 (S1): constructing a full frequency and tuning hybrid type. In the sound absorbing system, when the full-frequency and tuned hybrid sound absorbing system is optimized by the particle swarm method, the required parameters are the shape, configuration and material properties of the components of the full-frequency and tuned hybrid sound absorbing system; (S2): defining the desired goal after the optimization of the above-mentioned full-frequency and tuning hybrid sound absorbing system; step 3 (S3): providing an objective function of the target optimal design strategy; wherein the objective function includes maximizing sound absorption Sound absorption coefficient or one of the sound power level (SWL) is minimized; step four (S4): resource-limited formula for providing parameters; step five (S5): initializing parameters and encoding parameters To produce particles Initial position and initial velocity; Step 6 (S6): Substituting particles into the objective function to obtain the objective function fitness value of the particle, comparing the fitness value of the objective function with the optimal objective function value searched by the particle Wherein, the optimal objective function adaptation value is the individual best value (pbest) and the global best value (gbest) possessed by the individual particle; and step 7 (S7): if the group When the error of the global best value (gbest) is less than or equal to a preset minimum value or the number of iterations reaches a preset number of times, the operation ends; otherwise, the step 6 is repeated (S6); wherein the condition for ending the operation is two One type is that after the particles are updated, the group optimal value error of the group has completely converged to a preset minimum value, that is, the parameters of the target particle can conform to the full frequency and tuning mixed sound absorption system that the user wants to construct. The objective function requirement; the other is that the number of iterations reaches a target number of iterations, and the number of iterations of the target is pre-determined by the user, representing the particle swarm optimization algorithm. The number of executions (i.e., the position of the particle itself and the number of particles in each particle velocity updates); particle group is generally preferred to accelerate the completion of the algorithm, the termination condition may be developed as a target number of iterations.

It is worth noting that the particle swarm optimization method used in the present invention is one of the methods used in optimizing engineering problems, and the theory of Particle Swarm Optimization is the most theoretical. As early as 1995, two scholars, Kennedy and Eberhart, proposed that the concept mainly comes from the clustering behavior of birds and fish, using the concept of the movement of birds or fish (meaning particles) to find the best solution in the search space. In each optimization operation, each particle is responsible for a part of the region-optimized parameter search. During the search process, each particle records the individual best value (pbest) that it has found. There is a moving target in the search process, and each particle will move to the best value of all the particles (gbest) in the current particle, in addition to the individual best value that it has found so far. The solution achieves the effect of global optimization.

Please refer to the second figure, which is a schematic diagram of a full-frequency and tuned hybrid sound absorbing system according to a preferred embodiment of the present invention (mixed type A sound absorbing panel), which can be further proved by the following specific embodiments. The flow of the steps of the present invention is applicable to the scope of the present invention, but is not intended to limit the scope of the present invention in any form. In the present embodiment, the full-frequency and tuned hybrid sound absorbing system can have a plurality of carrier plates (1) and a plurality of them connected thereto. The punching plate (2) is configured, wherein the supporting plate (1) defines a tuning resonance chamber (3) having an opening, and has a punch on both sides of the neck (31) of the tuning resonance chamber (3) The sound absorbing body (4) formed by the orifice plate (2) and the carrier plate (1), and the sound absorbing body (4) is provided with at least one layer of sound absorbing cotton (5), which is a layer in the embodiment, but is not limited to one layer. Furthermore, the full-frequency and tuned hybrid sound absorbing system of the present invention is constructed based on the one-dimensional plane wave theory and the acoustic impedance of the Helmholtz resonance chamber; as can be seen from the second figure, the present embodiment The full-range and tuned hybrid sound absorbing system is a sound absorbing body (4) formed by a single-layer punching plate (2) and Homerho The tuning resonance chamber (3) is composed of; firstly, for the sound absorbing body (4) formed by the single-layer punching plate (2), when the sound wave propagates in the medium mm, the distance between the point L and the point 2 is The relationship between the sound pressure P and the sound particle velocity μ matrix can be expressed as follows: Where K _mm is the acoustic constant and Z _mm is the acoustic impedance; therefore, the relationship between the sound pressure P of point 0 and point 1 in the second figure and the sound particle velocity μ matrix can be expressed as: Similarly, the sound-absorbing cotton (5) with a thickness of Df has a matrix relationship between the sound pressure P of the points 1 and 2 and the sound particle velocity μ: Where K _fiber is the acoustic constant of the sound particle in the sound absorbing cotton (5); the above function is rewritten with a special forward impedance and wave constant as: Next, the forward impedance Z _{3 on the} surface of the punching plate (2) can be expressed in a matrix pattern as follows: Expanding the above formula and using a special forward impedance and wave constant, the forward impedance Z _{3 of the} surface of the punching plate (2) can be expressed as a complex version as follows: Where q is the thickness of the punching plate (2), d is the inner diameter of the punching hole, f is the resonance frequency, N is the number of punching holes per 1 m ² of the punching plate (2), and ρ ₀ is the air density; therefore, for positive For the incident sound wave, the positive sound absorption rate α ₁ of the sound absorbing body (4) formed by the single-layer punching plate (2) is:

Then, for the tuning resonance chamber (3), because the tuning resonance chamber (3) structure is closed with a certain volume of cavities in the middle, and through a certain depth of small holes and the sound field space, the sound absorption principle can be used by Homer Respirators (Helmholtz Resonator, HR) to illustrate; when the depth and aperture of the hole is much smaller than the wavelength of the sound wave, the elastic deformation of the air plug in the neck is small, can be regarded as a mass to deal with, close the cavity The volume is much larger than the neck of the hole, and it has the function of an air spring. When the external incident acoustic wave frequency is equal to the natural resonance frequency of the system itself, the air column in the neck of the hole generates severe vibration due to resonance. During the vibration process, the air The plug and the neck of the neck are rubbed to consume energy; in this embodiment, it is assumed that the characteristic size of the tuning resonance chamber (3) is smaller than the wavelength of the acoustic wave, and the air (31) of the air incident on the tuning resonance chamber (3) can be regarded as a block shape. Particle, in this resonance process, air adiabatic extrusion can be regarded as a spring, considering the internal and external sound field end effect parameters ( l ₂ and l ₂ ), add it to the modal to calculate the neck ( 31) Fluid transport The inertia effect; in addition, the opening in the neck (31) under the premise of less than tuning resonance chamber (3) of the cross section, in contact with a flange at the end of which the end effect sound field parameters _{(l. 1} and l ₂ ) for , where r _k is the radius of the neck (31) of the tuning resonance chamber (3); and for the simplified block mode of the Homholtz tuning resonance chamber (3), the resonance frequency f _res is Where c _o is the sound velocity, S _k is the tuning resonance cavity (3) the sectional area of the neck (31), L _k = D ₁ is the length of the tuning resonance cavity (3) neck (31), V _c is the tuning The volume of the resonance chamber (3), l _T is the tuning sound chamber (3) The end effect parameter of the total sound field of the tube to the main tube, which can be expressed as l _T = l ₁ + l ₂ = 1.698 r _k ; therefore, the tuning resonance The acoustic impedance Z _{(h) of the} cavity (3) can be expressed as: R _res is the resistance impedance of the sound, L _res is the inductance impedance of the sound, C _res is the capacitance impedance of the sound; and when the radius of the neck (31) of the tuning resonance chamber (3) is r _k , the acoustic resistance R of the sound _Res can generally be expressed as: Among them, the wave constant Characteristic impedance When k _o r _k <0.5, the sound wave is a low-frequency sound wave (planar wave), so the high-order wave can be ignored. Finally, the acoustic impedance Z _{(h) of the} tuning resonance chamber (3 ₎ can be expressed as: among them, , , Therefore, for a forward incident sound wave, the Helmholtz tuning resonance chamber (3) has a positive sound absorption rate α ₂ of: In summary, the average sound absorption rate of the full frequency and tuning hybrid sound absorbing system of this embodiment can be expressed as: Wherein, S ₁ is the sectional area of the neck (31) of the tuning resonance chamber (3), and the sectional area of the resonance chamber (3) of the S _{2 is} tuned; then, the average sound absorption rate of the above system is maximized as the objective function of the embodiment. Therefore, the objective function OBJ = α _sys (in this embodiment) ), =( f , p %, d , q , D ₁ ); where p % is the opening ratio of the punching plate (2), D ₁ = Df (the thickness of the sound absorbing cotton) + L (the thickness of the air layer) + q (punching The thickness of the plate is the length of the neck (31) of the tuning resonance chamber (3), and the limit of the particle group method parameter (PSO parameter) is ω , which means the inertial weight coefficient = (0.4, 0.6, 0.8, 1.0, 1.2), p represents the particle population size = (100, 200, 400, 800), and Iter _max is the maximaliteration number = (100, 200, 400, 800); notably, in another embodiment, The objective function may be to minimize the sound power level (SWL), wherein the definition of the sound power level is derived from the sound intensity level, defined as Where W is the sound power in watts, and W ₀ is the standard reference power, taking 10 ^-12 watts as the reference, so the above equation can be rewritten as SWL = 10log ₁₀ W +120 dB .

Please refer to the third figure, which is a schematic diagram of a full-frequency and tuned hybrid sound absorbing system according to a second preferred embodiment of the present invention (mixed B-type sound absorbing panel), wherein the neck (31) of the tuning resonance chamber (3) is The extension tube type, and for the simplified extension tube Helmholtz tuning resonance chamber (3) in the block mode, the resonance frequency f _res is: Wherein, the end effect parameters of the sound field ( l ₁ and l ₂ ) are divided into l ₁ =0.7 r _k (the end point where the blue phase cannot be connected) and l ₂ =0.849 r _k (the end point with the flange connection), And l _T = l ₁ + l ₂ = 1.549 r _k ; therefore, the acoustic impedance Z of the tuning resonance chamber (3) is:

Please refer to the fourth figure, which is a schematic diagram of a full-frequency and tuned hybrid sound absorbing system according to a third preferred embodiment of the present invention (mixed C-type sound absorbing panel), which is different from the above-described preferred embodiment. The sound absorbing body (4) on both sides of the neck (31) of the resonance chamber (3) is not provided with sound absorbing cotton (5); again, as shown in the fifth figure, the fourth preferred embodiment of the present invention (mixed D A schematic diagram of a full-frequency and tuned hybrid sound absorbing system of a type of sound absorbing panel, which differs from the above-described three preferred embodiments in that at least one layer of sound absorbing cotton (5) is provided in the tuning resonance chamber (3), and in this embodiment In the example, there is a two-layer sound absorbing cotton (5); and for a simplified block mode with a sound absorbing cotton (5) tuning sound chamber (3), the resonance frequency f _res is: among them, And the resistance of the acoustic impedance can be expressed as: = k _o {[1+0.0858( f / R _f ) ^-0.70 ]+ j [-0.1749( f / R _f ) ^-0.59 ]}; therefore under low frequency acoustic wave (planar wave) conditions ( kr _k <0.5), this Internal sound field endpoint effect Can be simplified to Therefore, the final sound field end effect parameter ( Divided with l ₂ ) (with flanged end points), and l ₂ =0.849 r _k (end of flange connection).

It should be noted that the method for optimizing the structure of the sound absorbing panel by the particle group method of the present invention can also be applied to the full frequency and tuning mixed sound absorbing system of the single layer, double layer or three layer sound absorbing panels, please refer to the sixth to eighth pictures. As shown, the particle size method is used to quickly and efficiently find the value of the optimal parameter; and the principle of optimization is similar to the solution process. The sound absorbing body formed by the single-layer punching plate (2) of a preferred embodiment thereof is shown. (4), no longer repeat here; the following table is the aperture ratio, punching inner diameter, tuning resonance cavity neck of the full-frequency and tuning mixing type sound absorbing system of the single-layer, double-layer or three-layer sound absorbing panel of the present invention. Data length table such as length and other parameters of the optimized sound power level (SWL): where p % is the opening of the punching plate (2), d is the inner diameter of the punching hole, D ₀ = Df ₁ (the thickness of the sound absorbing cotton) + L ₁ (air layer thickness) + q ₁ (punching plate thickness), DDL = D ₀ - q ₁ - q ₂ - DD _f , DD _f = Df ₁ + Df ₂ , xx 5 = Df ₁ / DD _f / (1- Df ₁ / DD _f ), xx 6= Df ₂ / DD _f /(1- Df ₁ / DD _f ), xx 7= L ₂ / DDL /(1- L ₁ / DDL ).

In addition, please refer to the ninth to tenth drawings, which are respectively schematic diagrams of the full-frequency and tuned hybrid sound absorbing system of the eighth to ninth preferred embodiments of the present invention, wherein the holes (21) of the punching plate (2) are available. Further, at least one tuning tube (22) is provided. The ninth figure is provided with a tuning tube (22) in a sound absorbing body (4), and the tenth figure is provided with two tuning tubes (22) in a sound absorbing body (4). Further, please refer to the eleventh to twelfth drawings, which are schematic diagrams of the full-frequency and tuned hybrid sound absorbing system according to the tenth to eleventh preferred embodiments of the present invention, which are attached to the punching plate (2). A three-layer sound absorbing body (4) is formed between the wall and the wall, wherein one tuning tube (22) can span the three layers of sound absorbing body (4), and the other tuning tube (22) spans two layers of sound absorbing bodies (4), such as In the eleventh figure, in addition, sound absorbing cotton (5) may be provided in the sound absorbing body (4) as shown in Fig. 12.

In addition, please refer to the thirteenth to fifteenth figures, which are respectively twelve of the invention ~ The fourteen preferred embodiment of the full frequency and tuning mixed sound absorption system schematic diagram, the thirteenth figure is provided in the three sound absorption body (4) with a corresponding length of the three tuning tube (22), and close to the perforated plate (2) The sound absorbing body (4) is provided with sound absorbing cotton (5); the fourteenth figure is provided with a tuning tube (22) traversing the sound absorbing body (4); and the fifteenth drawing is The sound absorbing body (4) is provided with sound absorbing cotton (5); in summary, the full frequency and tuning mixing type sound absorbing system is similar to the solution process by a particle group method optimization principle. The sound absorbing body formed by the layer punching plate will not be described here; it is worth noting that the number of the punching plate (2), the number of the sound absorbing body (4), and the tuning of the full frequency and tuning mixing type sound absorbing system of the present invention are The number and position of the tubes (22) and the arrangement of the sound absorbing cotton (5) are only a preferred embodiment. Due to the numerous conditions, it is difficult to enumerate them one by one. Here, only the types of structures listed above are explained and explained. The status and characteristics of the application, after reading and understanding the guidance of the present invention, the related quantity and position change should be regarded as the equivalent change or repair of the present invention. Decoration.

From the above description of the method and the description of the structure of the sound absorbing panel optimized by the particle group method, the present invention has the following advantages:

1. The present invention provides an industry-required tool for the optimization of multi-variable design parameters of a full-frequency and tuned hybrid sound absorbing system by a one-dimensional plane wave (low-order wave) four-turn transmission matrix method combined with a particle swarm method. The system and the overall flexible design method, with the optimized parameters to design the full-frequency and tuning mixed sound absorption system required in the limited space (such as the closed factory building), avoiding the traditional method of trial and error, one by one. The material and manpower caused by the sound absorbing panel And wasted time cost.

2. The invention searches for parameters of the full-frequency and tuning hybrid sound absorbing system by particle swarm optimization, so that users lacking expert experience can adjust and construct high sound absorption rate or low sound according to the optimization situation. Power level full-range and tuning hybrid sound absorption system.

3. The invention adopts the particle swarm algorithm to complete only three parameters and has a fast convergence capability. For a precision process factory that pursues exquisite and high quality, an effective sound absorption can be developed in a limited space. The system is to eliminate the full-frequency (low frequency, intermediate frequency, high frequency, pure tone) reflected sound in the closed building.

In summary, the method for optimizing the structure of the sound absorbing panel by the particle group method can achieve the intended use efficiency by the above disclosed embodiments, and the present invention has not been disclosed before the application. Full compliance with the requirements and requirements of the Patent Law.爰Issuing an application for a patent for invention in accordance with the law, and asking for a review, and granting a patent, is truly sensible.

The illustrations and descriptions of the present invention are merely preferred embodiments of the present invention, and are not intended to limit the scope of the present invention; those skilled in the art, which are characterized by the scope of the present invention, Equivalent variations or modifications are considered to be within the scope of the design of the invention.

(1)‧‧‧ board

(2) ‧‧‧punching plate

(21)‧‧‧ holes

(22)‧‧‧ Tuning tube

(3) ‧‧‧ Tuning resonance chamber

(31)‧‧‧ neck

(4) ‧‧‧Acoustic body

(5) ‧‧‧Acoustic cotton

(S1)‧‧‧Step one

(S2)‧‧‧Step 2

(S3) ‧ ‧ Step 3

(S4)‧‧‧Step four

(S5) ‧ ‧ step five

(S6) ‧‧‧Step six

(S7) ‧‧‧Step seven

First Figure: Flow chart of the method of the present invention

Second: Schematic diagram of a full frequency and tuning hybrid sound absorbing system according to a preferred embodiment of the present invention (mixed type A sound absorbing panel)

Third: Schematic diagram of a full-frequency and tuning hybrid sound absorbing system of a second preferred embodiment (hybrid B-type sound absorbing panel) of the present invention

Fourth: Schematic diagram of a full-frequency and tuning hybrid sound absorbing system of the three preferred embodiments (mixed C-type sound absorbing panels) of the present invention

Fifth: Schematic diagram of a full-frequency and tuning hybrid sound absorbing system of four preferred embodiments (hybrid D-type sound absorbing panels) of the present invention

Figure 6 is a schematic diagram of a full frequency and tuning hybrid sound absorbing system of a fifth preferred embodiment (single layer sound absorbing panel) of the present invention

Figure 7 is a schematic diagram of a full-frequency and tuned hybrid sound absorbing system of a sixth preferred embodiment (double-layer sound absorbing panel) of the present invention

Figure 8 is a schematic diagram of a full-frequency and tuning hybrid sound absorbing system of a seventh preferred embodiment (three-layer sound absorbing panel) of the present invention

Ninth aspect: a schematic diagram of a full-frequency and tuning hybrid sound absorbing system with a tuning tube according to an eighth preferred embodiment of the present invention

FIG. 10 is a schematic diagram of a full-frequency and tuning hybrid sound absorbing system with two tuning tubes according to a preferred embodiment of the present invention;

Eleventh drawing: a schematic diagram of a full-frequency and tuned hybrid sound absorbing system with two tuning tubes according to a tenth preferred embodiment of the present invention

Twelfth Embodiment: Schematic diagram of a full-frequency and tuned hybrid sound absorbing system with two tuning tubes according to an eleventh preferred embodiment of the present invention

Thirteenth Diagram: Schematic diagram of a full-frequency and tuning hybrid sound absorbing system with three tuning tubes according to a twelve preferred embodiment of the present invention

Figure 14 is a schematic diagram of a full-frequency and tuned hybrid sound absorbing system with three tuning tubes in accordance with a thirteenth preferred embodiment of the present invention

Fifteenth Figure: Schematic diagram of a full-frequency and tuned hybrid sound absorbing system with three tuning tubes according to a fourteenth preferred embodiment of the present invention

(S1)‧‧‧Step one

(S2)‧‧‧Step 2

(S3) ‧ ‧ Step 3

(S4)‧‧‧Step four

(S5) ‧ ‧ step five

(S6) ‧‧‧Step six

(S7) ‧‧‧Step seven

Claims (11)

A method for optimizing a structure of a sound absorbing panel by a particle group method, comprising the following steps: Step 1: constructing a full frequency and tuning mixed sound absorbing system, and optimizing the full frequency cum tuning sound absorbing system by particle swarm optimization In the calculation, the required parameters are the shape, configuration and material properties of the components of the full-frequency and tuning hybrid sound absorbing system; Step 2: Define the target to be achieved after the optimization of the full-frequency and tuning hybrid sound absorbing system; Third: provide the objective function of the best design strategy for the target; Step 4: Provide the resource limit of the parameter; Step 5: Initialize the parameter and encode the parameter to generate the initial position and initial velocity of the particle; Step 6: The particle is substituted into the objective function to obtain the objective function fitness value of the particle, and the fitness value of the objective function is compared with the optimal objective function value searched by the particle; and step 7: if the group optimal value error When less than or equal to a preset minimum value or the number of iterations reaches a preset number of times, the operation ends; otherwise, step 6 is repeated. The method for optimizing the structure of the sound absorbing panel by the particle group method according to the first aspect of the patent application, wherein the optimal objective function adaptation value is a personal best value (pbest) possessed by the individual particle. Best value with group (global best v Alue, gbest). The method for optimizing the structure of the sound absorbing panel by the particle group method according to the first aspect of the patent application, wherein the full frequency and tuning mixed sound absorbing system is based on a one-dimensional plane wave theory and a Helmholtz resonance chamber. The acoustic impedance is based on the construction. A method for optimizing a sound absorbing panel structure by a particle swarm method as described in claim 1, wherein the objective function includes maximizing a sound absorption coefficient or minimizing a sound power level. SWL) one of them. The method for optimizing the structure of the sound absorbing panel by the particle group method according to the first aspect of the patent application, wherein the full frequency cum tuning sound absorbing system is a plurality of gussets and a plurality of punching holes connected to the slab The plates are constructed, wherein the plates define at least one tuning resonance chamber having an opening, and the punching plate forms at least one sound absorbing body with the receiving plates. The method for optimizing the structure of the sound absorbing panel by the particle group method according to the fifth aspect of the patent application, wherein the hole of the punching plate is further provided with at least one tuning tube. A method for optimizing a sound absorbing panel structure by a particle group method according to claim 5, wherein the tuning resonance chamber is provided with at least one layer of sound absorbing cotton. A method for optimizing a sound absorbing panel structure by a particle group method according to claim 5, wherein the sound absorbing body is provided with at least one layer of sound absorbing cotton. The best particle group method as described in any one of claims 5 to 8. The method for absorbing the structure of the sound absorbing panel, wherein the component shape parameter of the full frequency cum tuning mixing type sound absorbing system is selected from the group consisting of a punching inner diameter, a punching plate thickness, a punching plate opening ratio, and a sound absorbing cotton thickness. The method for optimizing the structure of the sound absorbing panel by the particle group method according to any one of claims 5 to 8, wherein the component configuration parameter of the full frequency cum tuning mixing type sound absorbing system is selected from the group consisting of air layer thickness and tuning. The group consisting of the diameter of the resonance chamber neck, the length of the tuning resonance chamber neck, and the volume of the resonance chamber. The method for optimizing a sound absorbing panel structure by a particle group method according to any one of claims 5 to 8, wherein the component material property parameter of the full frequency and tuning hybrid sound absorbing system comprises a sound absorbing cotton flow impedance. .