CN106558302B - Noise reduction method for sound source equipment - Google Patents
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Abstract
The invention relates to a noise reduction method for sound source equipment, which comprises the following steps: acquiring a near-field noise signal of sound source equipment and a body vibration signal of the sound source equipment, and determining a characteristic frequency band and a bandwidth of the noise signal and a characteristic frequency band and a bandwidth of the vibration signal; establishing an indoor sound field simulation model according to the noise characteristic frequency band and the bandwidth, and calculating the distribution characteristics of the indoor sound field; and designing a sound absorption module, a sound insulation module, a noise elimination module and a vibration isolation module according to the characteristic frequency band and the bandwidth of the noise signal, the characteristic frequency band and the bandwidth of the vibration signal and the distribution characteristics of the indoor sound field. The technical scheme of the invention has good noise reduction effect, the station boundary acoustic environment of the factory enterprise can well meet the requirement of GB12348 after noise reduction treatment, and the method is particularly suitable for noise treatment of indoor equipment such as transformers, reactors, steam turbines and the like.
Description
Technical Field
The invention relates to the technical field of noise control, in particular to a noise reduction method for sound source equipment.
Background
With the advance of urbanization and the development of industrialization, the land resources are increasingly tense, so that a plurality of residential areas are deeply disturbed by the noise of large-scale enterprises and factories adjacent to the residential areas. The national laws and regulations have stricter standard requirements on station noise, and noise complaints become a headache problem for enterprise managers due to the enhancement of public rights awareness. Therefore, the exceeding of the noise not only relates to the life happiness index of urban residents, but also becomes an important problem for limiting the development of industrial enterprises.
Most of sound source equipment in enterprise plants are placed in relatively closed plants, the internal space is limited, and for example, a main transformer chamber and a reactor chamber are generally arranged for a transformer and a reactor in a transformer substation. In order to facilitate equipment inspection and ensure that the working temperature is appropriate, doors, windows and ventilation systems are generally arranged indoors. Noise generated during the operation of the equipment is easy to spread from the channels communicated with the outside to the periphery. In addition, because the walls of the plants such as the main transformer room and the like are not subjected to any sound absorption treatment, equipment noise is superposed with direct noise after being reflected by the walls to form a standing wave effect and a reverberation effect, and the sound level of indoor noise is improved. Therefore, the noise control of the indoor sound source equipment is the key point of various noise reduction projects.
Aiming at the characteristic that most of the existing enterprise factory equipment is directly installed on the ground or a floor cement foundation, the mode of installing a sound absorption plate, a sound insulation plate and the like for the equipment can only obstruct the transmission of sound in the air, and cannot obstruct the way of sound diffusing outwards along the foundation. When vibrations generated by the equipment are transmitted to the foundation, floor, wall or other structure, they are induced to travel in the form of elastic waves along the building structure to all parts of the building and vibrate adjacent air, generating structural noise. Based on the above situation, in order to ensure the effectiveness of the noise reduction project, the noise control work needs to be systematically carried out from four aspects of sound absorption, sound insulation, noise elimination and vibration isolation.
Disclosure of Invention
The invention aims to provide a noise reduction method for sound source equipment, which realizes fast and efficient noise control.
In order to achieve the purpose, the invention adopts the following technical scheme: a sound source device noise reduction method comprising:
acquiring a near-field noise signal of sound source equipment and a body vibration signal of the sound source equipment, and determining a characteristic frequency band and a bandwidth of the noise signal and a characteristic frequency band and a bandwidth of the vibration signal;
establishing an indoor sound field simulation model according to the noise characteristic frequency band and the bandwidth, and calculating the distribution characteristics of the indoor sound field;
and designing a sound absorption module, a sound insulation module, a noise elimination module and a vibration isolation module according to the characteristic frequency band and the bandwidth of the noise signal, the characteristic frequency band and the bandwidth of the vibration signal and the distribution characteristics of the indoor sound field.
Collecting the near-field noise signals of the sound source equipment by using a sound level meter within 1.5 m; and enabling the sound source equipment to collect and design the body vibration signal by using a vibration level meter within 1.5 m.
And respectively carrying out frequency spectrum analysis on the noise information and the vibration signal to obtain a characteristic frequency band and a bandwidth of the noise signal and a characteristic frequency band and a bandwidth of the vibration signal.
And obtaining the key position information with the largest influence on the indoor noise by calculating the distribution characteristics of the indoor sound field.
The sound absorption module is a microporous fiber composite sound absorption plate and comprises a composite aluminum fiber sound absorption plate and a microporous plate; a plurality of slit holes formed by aluminum fibers and aluminum foils are formed in the aluminum fiber sound absorption plate; the sound absorption capacity of the aluminum fiber sound absorption board is determined according to the porosity, the board thickness, the fiber diameter and the fiber surface density of the aluminum fiber sound absorption board; the microperforated panel will have its sound absorption capacity determined by its perforation rate and resonant back cavity thickness.
Arranging the sound absorption modules in the room according to various different proportions of the sound absorption modules in the total indoor surface area, and carrying out sound field simulation analysis on the arrangement; selecting the proportion with the best sound absorption effect in the different proportions for setting through the sound field simulation analysis; and selecting the position of the sound absorption module installed in the room through sound field simulation analysis to ensure that the sound absorption effect is best.
The sound insulation module comprises a steel plate, sound absorption glass wool and a galvanized steel plate; and determining the sound insulation capability of the sound absorption glass wool through the thickness of the damping material filled in the sound absorption glass wool and the thickness of the rigid material structure of the galvanized steel plate.
Arranging the sound absorption module indoors according to various different proportions of the sound insulation module in the area of the indoor wall body, and performing sound field simulation analysis on the arrangement in different proportions; and selecting the proportion with the best sound insulation effect in different proportions for setting through the sound field simulation analysis. (ii) a
The silencing module is a silencer; the sound attenuation capacity of the sound attenuator is determined by the sound channel structure form, the material thickness of the sound attenuation sheet, the material volume weight and the sound attenuation length of the sound attenuator.
The vibration isolation module comprises an elastic element and a damping element which are arranged between a vibration source and a vibration body; the vibration isolation capability of the vibration isolation module is determined by the damping performance, the natural frequency, the structural rigidity and the structural form of the vibration isolation module.
Compared with the closest prior art, the technical scheme provided by the invention has the following excellent effects
1. According to the technical scheme, an indoor sound field simulation model is established, and the influence of relevant positions on indoor noise is more important because the multiple reflection and interference phenomena of sound waves are more obvious at positions such as indoor wall positions through calculation and analysis, so that a sound absorption module can be installed at the relevant positions in a targeted manner to optimize the sound absorption effect;
2. according to the technical scheme, in the design of the sound absorption module and the noise elimination module, the adjustment of various functional parameters is guided through simulation analysis, so that the test cost is saved;
3. the technical scheme of the invention adopts a modular design concept, and can adopt modular design aiming at similar service environments, arrangement structures and equipment forms, thereby greatly reducing the workload and improving the design efficiency; (ii) a
4. According to the technical scheme, in the production design of the noise reduction material, the general modular plate structure and material specification can greatly improve the production efficiency, improve the product stability and reduce the cost;
5. according to the technical scheme, the novel noise reduction material-microporous fiber composite sound absorption plate is adopted to process various noise reduction modules, the material can change the acoustic performance of the material through adjusting the thickness of the double-layer resonance cavity, once the characteristic frequency of target noise is mastered, the functional parameters of the noise reduction modules can be adjusted in a targeted manner, and efficient sound absorption and noise reduction are guaranteed; the material is non-combustible and non-corrosive, green and environment-friendly, light in weight, easy to process and treat, and has great application potential in noise reduction engineering;
6. the technical scheme of the invention develops noise reduction design from four aspects of sound absorption, sound insulation, noise elimination and sound insulation, cuts off the way of transmitting noise from indoor to outdoor, greatly reduces the factory noise level of enterprise factories, can meet the requirement of GB12348, and is particularly suitable for noise treatment of indoor sound source equipment such as transformers, reactors, steam turbines and the like.
Drawings
FIG. 1 is a graph of noise measurement points according to an embodiment of the present invention;
FIG. 2 is a diagram of vibration measurement points according to an embodiment of the present invention;
FIG. 3 is a diagram of a transformer near-field noise spectrum according to an embodiment of the present invention;
FIG. 4 is a diagram of a vibration spectrum of a transformer body according to an embodiment of the present invention;
FIG. 5 is a schematic structural view of a microporous fiber composite sound-absorbing panel according to an embodiment of the present invention;
FIG. 6 is a schematic view of a dynamic model of a vibration isolation system according to an embodiment of the present invention;
FIG. 7 is a graph illustrating a transmittance curve according to an embodiment of the present invention;
1-micro-perforated plate, 2-aluminum fiber board, 3-keel frame.
Detailed Description
The present invention will be described in further detail with reference to examples.
Example 1:
the invention provides a noise reduction method for sound source equipment, which realizes fast and efficient noise control through the structure optimization and application design of a noise reduction module, and various noise reduction facilities can be produced in a modularized and batch mode on the premise of universal design, thereby not only ensuring the stability of noise reduction design, but also reducing the input cost. The method is completed by the following steps:
the method comprises the steps of noise vibration signal acquisition, indoor sound field simulation analysis, sound absorption, sound insulation, noise elimination, vibration isolation module structure theoretical calculation and functional parameter optimization design. The method specifically comprises the following steps:
(1) collecting its near-field noise signal using a sound level meter at the sound source device 1m, as shown in fig. 1; and (3) acquiring the vibration signal of the equipment body by using a vibration level meter, and grasping the characteristic frequency band and the bandwidth of the noise vibration signal as shown in fig. 2.
(2) And calculating the distribution characteristics of the indoor sound field by using finite element analysis software to obtain the key position information with the largest influence on the indoor noise.
(3) The sound absorption module is manufactured by adopting the microporous fiber composite sound absorption plate, the acoustic performance of the composite sound absorption plate is determined according to the noise spectrum characteristics, and the sound absorption coefficient curve can be ensured to comprehensively cover the characteristic frequency band of the target noise by adjusting the thickness of the double back cavities. The microporous fiber composite sound-absorbing board has a structure such as
(4) And the total area proportion, the installation position and the sound absorption coefficient curve of the sound absorption module are used as condition parameters to be input into the simulation model, and each functional parameter of the sound absorption module is adjusted through the feedback of a calculation result, so that the sound absorption effect is optimized.
(5) The sound insulation module is manufactured by adopting a steel plate with the thickness of 1mm, sound absorption glass wool with the thickness of 100mm and a steel plate with the thickness of 1mm, the total area proportion, the damping characteristic of the filling material and the structural rigidity of the sound insulation module are used as condition parameters to be input into the simulation model, and each functional parameter is fed back and adjusted through a calculation result, so that the sound insulation effect is optimized.
(6) The method comprises the steps of manufacturing a silencer by adopting a microporous fiber composite sound absorption plate, establishing a silencer acoustic simulation model, inputting a structural form of a silencing channel, the thickness of a silencing material, the volume weight and the air flow rate into the simulation model as condition parameters, and feeding back and adjusting various functional parameters through a calculation result to optimize the silencing effect.
(7) The vibration isolation module is made of the nitrile rubber, and the damping performance, the natural frequency and the structural rigidity of the module are determined according to the frequency spectrum characteristics of the vibration signals, so that the vibration transmission efficiency can be reduced to the maximum extent.
(8) The sound absorption module is installed on the indoor wall surface, the sound insulation module is installed at an indoor gate, the noise elimination module is installed at a ventilation system, and the vibration isolation module is installed on a base of sound source equipment, so that systematic noise control of the sound source equipment is realized in the aspects of sound absorption, sound insulation, noise elimination and vibration isolation.
A certain substation is a typical urban indoor substation, and the two main transformers are respectively positioned in independent main substations. The urban central region is in a complex surrounding environment, commercial and civil buildings are erected in forest, the most sensitive position of the station boundary is provided with a residential building, and the building is 22 meters away from a main transformer room. The field test result shows that under the daily operation working condition, the factory noise of the substation is basically stabilized at 52-53 dB (A), the noise at 1 meter outside the 1-floor residential building is at the level of 51-52 dB (A), and the environmental influence is serious. On the basis, the factory noise in the peak period of the estimated power consumption can reach more than 60dB (A), and the noise at 1m outside the residential building is at the level of 57-61 dB (A), so that the normal life and rest of the surrounding residents are seriously influenced in part of the operation period.
Aiming at the information, the following scheme is mainly adopted:
1. and measuring and researching the noise vibration of the transformer substation. After mastering the size information of a main transformer chamber of a substation, the structural model of the transformer, the main working condition and other information, carrying out related measurement: a sound level meter is used for collecting noise signals at the position 1m of the main transformer, a vibration level meter is used for collecting vibration signals of the transformer body, spectral characteristic analysis is carried out, and the characteristic frequency band and the bandwidth are mastered. The near-field noise spectrogram of the equipment is shown in fig. 3, and therefore, the noise energy of the transformer is mainly concentrated in the low-frequency range of 12.5-500 Hz. The spectrogram of the vibration signal of the device body is shown in fig. 4, and the noise has large wave length, slow attenuation and strong penetrating power and needs to be treated intensively.
2. And (5) simulating and analyzing the indoor sound field of the main transformer. And modeling and analyzing an indoor sound field by adopting finite element simulation software. According to the acoustic theory, when the main transformer equipment generates noise in the rectangular structure, sound waves can be transmitted forwards in a direct sound mode until the sound waves are close to the wall surface boundary of a wall body, and standing waves are formed by the sound waves, reflected waves of the sound waves and multiple re-reflected waves. The sound wave radiated by the device sound source in the main transformer chamber is not different from the radiation in free space before meeting the wall surface, and is only slightly influenced by the surrounding environment. Then, the sound waves contact the wall surface in sequence, and the sound waves in different directions are reflected and mutually interfered, so that the original spherical wave characteristic is lost. Through multiple continuous reflection, the sound wave finally reaches a stable state, and only the allowable wave mode in the room, namely the normal wave, is left. Simulation results show that the sound field distribution in the main transformer chamber of the transformer substation changes along with different frequency bands. The main transformer noise frequency is mainly low frequency, for a low frequency sound field, the distance node of a normal wave is larger due to the larger wavelength of a low frequency sound wave, high noise standing wave areas with larger range are formed on the wall and the inner space of a main transformer chamber, and in the areas, the sound wave interaction is strong, so that the integral noise in the space is directly and obviously increased. Noise of other frequency bands also has certain influence on the whole sound field, and the key area of the effect is the wall of the main transformer chamber. Therefore, the sound absorption module is mounted on the wall for low-frequency noise.
3. And (4) structural theoretical calculation and functional design of the sound absorption module. The sound absorption module uses a microporous fiber composite sound absorption plate as a manufacturing material, and the material is formed by compounding an aluminum fiber sound absorption plate and a micro-perforated plate, as shown in fig. 5. The aluminum fiber sound absorption board is a porous resonance sound absorption material and is provided with a plurality of slit holes formed by aluminum fibers and aluminum foil. When sound waves enter the interior of the material along the pores, air in the pores is caused to vibrate, friction with the walls of the pores is generated, and part of sound energy is converted into heat energy to be dissipated. The fiber slits may also be equivalent to a plurality of resonant structures of unequal diameter that will dissipate the target frequency acoustic energy through resonance action. The acoustic impedance ratio of the slit plate can be approximately expressed as
Wherein the content of the first and second substances,
is the integral of the full ellipse and is,
the ellipticity is given.
Where η is an air viscosity coefficient, d 2a is a gap width of the fiber material, 2l is a gap length, b is a gap center distance of the fiber material gap, σ d/b is a porosity, t is a sheet thickness, ρ0c0Is an impedance characteristic in air.
In material design and processing, the sound absorption performance of the material can be adjusted through technological parameters such as porosity, plate thickness, fiber diameter, fiber areal density and the like.
The micropunch plate absorbs sound through resonance to achieve the effect of consuming sound energy, and the resonance frequency of the micropunch plate is as follows:
wherein c is the speed of sound, lkThe thickness of the plate, P the perforation rate and D the depth of the cavity.
In material design and processing, the matching of target noise frequency can be carried out by adjusting the perforation rate P and the thickness D of the resonant back cavity. The acoustic impedance after the two are compounded is
In the design and matching of the device, the acoustic resistance R (R1 is the acoustic resistance of the micro-perforated plate, R2 is the acoustic resistance of the aluminum fiber plate), the acoustic mass M (M1 is the acoustic mass of the micro-perforated plate, M2 is the acoustic mass of the aluminum fiber plate) and the cavity depths D1 and D2 are assembled by adjusting the thickness of the resonant cavity, the parameters of the aluminum fiber plate and the parameters of the micro-perforated plate, and finally the resonant frequency of the device shifts to the characteristic frequency band of the target noise and is coupled to obtain the high sound absorption coefficient of the target frequency band. The sound absorption coefficient obtained by final design is
Sound absorption coefficient of sound absorption material structure
| Frequency band of sound absorption | 250Hz | 500Hz | 1000Hz | 2000Hz | Noise reduction coefficient |
| Coefficient of sound absorption | 0.8 | 0.9 | 0.7 | 0.8 | 0.8 |
In addition to the acoustic function of the sound absorption module, the overall area ratio is also an important factor affecting noise abatement. Four area ratios of 10%, 20%, 30% and 40% of the total surface area of the main transformer chamber are selected to arrange the sound absorption module. According to sound field simulation analysis, when the total area of the sound absorption module accounts for 10%, the sound wave interference effect of different frequency bands of the wall accessory of the main transformer chamber is weakened, the distribution of the internal sound field is optimized, the overall noise level of the main transformer chamber is reduced, and the noise in the frequency bands of 100Hz, 200Hz, 315Hz and 630Hz with higher noise level is weakened to a certain degree. At a sound absorbing material arrangement ratio of 10%, the noise near the indoor wall was reduced by about 3.8dB without adding the sound absorbing material. The calculated average reverberation time within the range of 100Hz to 1000Hz is 1.1s, which shows that the indoor reverberation effect is reduced, and the arrangement of the sound absorption material plays a corresponding role. When the area proportion of the sound absorption module is 20%, the noise is reduced by 5.7dB, and the average reverberation time is 0.7 s; when the area ratio is 30%, the noise is reduced by 7.19dB, and the average reverberation time is 0.58 s; the area ratio is 40%, the noise is reduced by 8.03dB, and the average reverberation time is 0.46 s. Therefore, when the area of the sound absorption material/structure arranged in the main transformer chamber is increased continuously, the noise reduction amount in the main transformer chamber tends to increase continuously, but the noise reduction amount is not in a linear growth relation, but tends to decrease incrementally along with the increase of the arrangement area, which shows that the indoor arrangement area of the sound absorption material/structure is not larger as well as better, but has an optimal value. Meanwhile, the 20% area proportion is finally determined by analyzing the overall economy of the noise reduction project.
The position of the sound absorption module on the wall can also have certain influence on the noise reduction effect. The sound absorption modules are respectively arranged at the corner, the middle part and the top of a room and are brought into a finite element model for simulation analysis, so that when the sound absorption modules are arranged at the corner, the noise is reduced by 3.7dB, and the reverberation time is 0.78 s; when the device is installed in the air, the noise is reduced by 5.21dB, and the reverberation time is 0.76 s; when mounted on top, the noise is reduced by 4.6dB and the reverberation time is 0.73 s. Therefore, the sound absorption module is arranged in the middle of the wall, and the noise reduction function can be effectively played.
4. And (4) designing functions and applications of the sound insulation module. The sound insulation module adopts a sound insulation structure of 1mm steel plate, 100mm sound absorption glass wool and 1mm galvanized steel plate, and is mainly used for preventing noise of the soundproof door from spreading outwards from the door. Factors mainly influencing the acoustic performance of the sound insulation module are the proportion of the sound insulation module occupying the area of the wall body, the thickness of the damping material filled in the sound insulation module and the thickness of the rigid material structure. According to the statistical result of the sizes of the door bodies of the transformer substations, three area proportions of 70%, 40% and 10% of the area of the door body of the main transformer chamber in the wall body are respectively selected to analyze the noise reduction effect of the sizes of the door bodies.
According to the low-frequency sound wave, after the door body is installed, the low-frequency sound wave still has certain sound transmission capacity, and part of the sound wave can transmit sound energy to the outside of the door through the particle vibration effect of the door body, so that low-frequency noise is still transmitted to the outside of the door with certain intensity; for medium-high frequency sound waves, the medium-high frequency noise of the transformer substation main transformer is small, so that the noise energy is relatively weak, and the intensity and energy transmitted to the outdoor are relatively small. When the proportion of the sound insulation modules is 70%, the noise level calculated outside the sound insulation door is 39 dB; when the proportion is 40%, the sound level of the outdoor noise is 41 dB; at a percentage of 10%, the outdoor noise level is 41.5 dB. Therefore, the influence of the proportion of the sound insulation door on the sound insulation effect is small, and the proportion of 10% is selected in consideration of the economical efficiency of the comprehensive engineering.
In order to ensure the optimized sound insulation performance of the sound insulation module, damping filling materials with the thicknesses of 50mm, 100mm and 150mm are respectively selected and matched with galvanized steel plates with the thicknesses of 0.5mm, 1.0mm and 1.5 mm. According to the test results, the sound insulation performance of the sound insulation module is increased along with the increase of the thicknesses of the damping filling material and the galvanized steel sheet. The economical efficiency and the sound insulation performance are comprehensively considered, and a damping filling material with the thickness of 50mm and a galvanized steel plate material with the thickness of 100mm are selected.
5. The function and application design of the noise elimination module. A ventilation system in a transformer substation is one of important ways for outward transmission of main transformer noise, and in order to reduce station boundary noise, a silencer is mounted for noise elimination and noise reduction. The structural form of the silencing channel of the silencing module, the material thickness of the silencing sheet, the material volume weight and the silencing length are key factors influencing the silencing performance.
And (3) carrying out simulation analysis on the straight plate type silencer, the folded plate type silencer and the labyrinth silencer, wherein from the aspect of the frequency spectrum analysis of the noise elimination amount, according to the sequence of the straight plate type silencer, the folded plate type silencer and the labyrinth silencer, the peak value of the noise elimination performance curve gradually moves from a high-frequency band to a low-frequency band, the noise elimination amount gradually rises in the low-frequency band of 63-500 Hz, and the characteristic of the trend that the noise elimination amount of the silencer gradually increases in the low-frequency band is displayed. The integral silencing performance is straight plate type < folding plate type < labyrinth type. Because the noise frequency of the substation is mainly low frequency, a labyrinth silencer is selected.
Simulation analysis is carried out on the silencing pieces with different thicknesses, so that the silencing performance of the silencing module is in an overall rising trend along with the increase of the thickness, but the low-frequency silencing performance is not remarkably improved; as the volume weight increases, the acoustic performance also increases; as the muffling passage increases, the muffling performance increases significantly, but the magnitude of the increase decreases significantly after a threshold is reached. In consideration of comprehensive economy and manufacturability, the parameters of the silencer are designed as follows: the thickness of the silencing sheet is 50mm, the volume weight is 45kg/m3, and the length of the silencing channel is 1300 mm.
6. The function and application design of the vibration isolation module. Vibration isolation is to arrange an elastic element and a damping element between a vibration source and a vibration body to reduce or isolate the transmission of vibration. The passive vibration isolation is mainly discussed according to the ship-borne situation, and the vibration isolation mechanical model is shown in fig. 6 and is generally simplified into a single-degree-of-freedom damping spring mass system.
When the system is subjected to ze＝z0ejwtWhen the simple harmonic support is excited, the motion equation can be expressed as follows:
with u-zeBrought in to
Where f (w) is the excitation force amplitude as a function of the square of the excitation. Solving the relative displacement amplitude of the available system:
the system vibration transmissibility can be obtained by the same method:
in the formula, omega is the frequency of external exciting force;
Wherein m is the mass of the vibrating mass, k is the stiffness, c is the system damping coefficient, zeFor vibrational displacement, z0Is the amplitude, and z is the initial displacement.
The transmission rate versus frequency ratio curves can be obtained from different damping ratios, as shown in fig. 7.
From the above figureIt can be seen that only when
When the vibration isolation transmission rate eta of the system is less than or equal to 1, the system enters a vibration isolation area. In transformer isolation design, a frequency ratio of 2.5-5 is generally required for safety. When the frequency ratio is 1, the system is in a resonance state. In the vibration isolation area, along with the reduction of the damping ratio, the vibration isolation effect of the system is better and better; however, the smaller the damping ratio, the larger the resonance amplification at the time of system resonance, and the larger the influence on the apparatus. Therefore, the ideal vibration isolator should make the natural frequency of the system low, have variable damping characteristic, namely there is greater damping in the resonance area of the system, make the system have apparent resonance amplification, have minor damping in the vibration isolation area, make the system have good vibration isolation efficiency, and shock resistance and stability are good, while choosing the damping ratio of the system, should consider vibration isolation efficiency and resonance amplification rate of the system synthetically, choose a suitable damping ratio. The design of the vibration isolation device of the power transmission and transformation equipment is to determine the damping and the rigidity of the vibration isolation device system properly.
According to the collected vibration spectrum characteristics of the transformer, the vibration energy of the transformer is mainly concentrated in the areas near the frequency bands of 25Hz, 50Hz and the like, and the vibration direction of the transformer is mainly vertical. In the structural design of the vibration isolation module, the compression type damping structure has vertical deformability and rigidity, and meets the vibration isolation requirement. Among the choices of vibration-isolating materials, natural rubber, nitrile rubber and butyl rubber are commonly used, and their vibration-isolating properties are shown in the following table.
TABLE 1 comparison of different rubber vibration isolation Properties
As can be seen from the table above, the nitrile rubber has high vertical rigidity and damping, and the adhesive strength and the aging resistance are superior to those of other two rubbers, so that the functional main body of the vibration isolation module is the nitrile rubber with a compression damping structure.
7. After the sound absorption module, the sound insulation module, the noise elimination module and the vibration isolation module are installed in the transformer substation, the noise level meter is used for measuring the noise conditions of a main transformer room and a transformer substation boundary in the daytime and at night. The results obtained are shown in the table below.
TABLE 2 comparison of noise levels before and after transformer substation administration
| Station boundary in daytime dB (A) | Front dB (A) of daytime building | Night station boundary dB (A) | Night front dB (A) | |
| Before treatment | 52～53 | 55 | 52～53 | 49 |
| After treatment | 43.3 | 50 | 41.15 | 42～43 |
The above table shows that the noise reduction design achieves good effect, and the station boundary noise emission of daytime and page reaches the requirement of GB 12348.
Finally, it should be noted that: the above embodiments are only for illustrating the technical solutions of the present invention and not for limiting the same, and those skilled in the art should understand that although the above embodiments are referred to: modifications and equivalents may be made to the embodiments of the invention without departing from the spirit and scope of the invention, which is set forth in the claims below.
Claims (4)
1. A noise reduction method for sound source equipment is characterized by comprising the following steps: the method comprises the following steps:
acquiring a near-field noise signal of sound source equipment and a body vibration signal of the sound source equipment, and determining a characteristic frequency band and a bandwidth of the noise signal and a characteristic frequency band and a bandwidth of the vibration signal;
establishing an indoor sound field simulation model according to the noise characteristic frequency band and the bandwidth, and calculating the distribution characteristics of the indoor sound field;
designing a sound absorption module, a sound insulation module, a noise elimination module and a vibration isolation module according to the characteristic frequency band and the bandwidth of the noise signal, the characteristic frequency band and the bandwidth of the vibration signal and the distribution characteristics of the indoor sound field;
the sound absorption module is a microporous fiber composite sound absorption plate and comprises a composite aluminum fiber sound absorption plate and a microporous plate; a plurality of slit holes formed by aluminum fibers and aluminum foils are formed in the aluminum fiber sound absorption plate; the sound absorption capacity of the aluminum fiber sound absorption board is determined according to the porosity, the board thickness, the fiber diameter and the fiber surface density of the aluminum fiber sound absorption board; the micro-perforated plate determines the sound absorption capacity according to the perforation rate and the thickness of the resonant back cavity;
arranging the sound absorption module in the room according to the proportion of the sound absorption module in the total indoor surface area, and carrying out sound field simulation analysis on the arrangement; setting according to the integral economy of the comprehensive noise reduction project through the sound field simulation analysis; selecting the wall corner, the middle part or the top of the room of the sound absorption module through the sound field simulation analysis; the sound insulation module comprises a steel plate, sound absorption glass wool and a galvanized steel plate; the sound insulation capacity of the sound absorption glass wool is determined by the thickness of a damping material filled in the sound absorption glass wool and the thickness of a rigid material structure of a galvanized steel plate;
arranging the sound absorption module indoors according to the proportion of the sound insulation module in the area of the indoor wall body and carrying out sound field simulation analysis; selecting the proportion with the best sound insulation effect for setting through the sound field simulation analysis;
the silencing module is a silencer; determining the silencing capacity of the silencer through the sound channel structure form, the material thickness of the silencing sheet, the material volume weight and the silencing length of the silencer;
the vibration isolation module comprises an elastic element and a damping element which are arranged between a vibration source and a vibration body; the vibration isolation capability of the vibration isolation module is determined by the damping performance, the natural frequency, the structural rigidity and the structural form of the vibration isolation module.
2. The noise reduction method of an acoustic source device according to claim 1, wherein: collecting the near-field noise signals of the sound source equipment by using a sound level meter within 1.5 m; and enabling the sound source equipment to collect and design the body vibration signal by using a vibration level meter within 1.5 m.
3. The noise reduction method of an acoustic source device according to claim 1, wherein: and respectively carrying out frequency spectrum analysis on the noise signal and the vibration signal to obtain the characteristic frequency band and the bandwidth of the noise signal and the characteristic frequency band and the bandwidth of the vibration signal.
4. The noise reduction method of an acoustic source device according to claim 1, wherein: and obtaining the key position information with the largest influence on the indoor noise by calculating the distribution characteristics of the indoor sound field.
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| CN108986780B (en) * | 2017-05-31 | 2021-11-02 | 青岛海尔智能技术研发有限公司 | Design method of noise reduction device of household appliance |
| CN109506904A (en) * | 2018-10-22 | 2019-03-22 | 北京工商大学 | A kind of thin plate harmonic radiation Noise Suppression Device design method |
| CN109272981A (en) * | 2018-10-23 | 2019-01-25 | 云南电网有限责任公司 | A kind of substation's denoising device |
| CN112447163B (en) * | 2019-08-29 | 2024-05-07 | 比亚迪股份有限公司 | Noise reduction method and acoustic noise elimination structure in vehicle cab |
| CN111696768B (en) * | 2020-05-13 | 2023-04-11 | 云南电网有限责任公司 | Outdoor transformer noise reduction method |
| CN112116901B (en) * | 2020-09-18 | 2024-03-05 | 北京市燃气集团有限责任公司 | Method for improving acoustic subjective evaluation index of medium-low pressure gas pressure regulating tank |
| CN112434416B (en) * | 2020-11-19 | 2023-09-05 | 西安西电变压器有限责任公司 | Method and device for determining vibration isolation system of body and vibration isolation system of body |
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