CN108981276B - Design method of noise reduction device of refrigerating device - Google Patents
Design method of noise reduction device of refrigerating device Download PDFInfo
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- CN108981276B CN108981276B CN201710397714.4A CN201710397714A CN108981276B CN 108981276 B CN108981276 B CN 108981276B CN 201710397714 A CN201710397714 A CN 201710397714A CN 108981276 B CN108981276 B CN 108981276B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D23/00—General constructional features
- F25D23/10—Arrangements for mounting in particular locations, e.g. for built-in type, for corner type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D2201/00—Insulation
- F25D2201/30—Insulation with respect to sound
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Abstract
The invention provides a design method of a noise reduction device of a refrigerating device, wherein the refrigerating device comprises a compressor and comprises the following steps: placing the refrigerating device in the anechoic chamber or the semi-anechoic chamber, and enabling the refrigerating device to work normally; determining a position of a compressor; testing to obtain the frequency characteristic of the noise of the compressor, and determining the frequency with the highest noise volume peak value and/or the second highest noise volume peak value as the required sound insulation frequency; extracting one or more sound insulation units, recording the frequency of noise when the sound insulation quantity is maximum, and recording as the actual sound insulation frequency; calculating the difference between the actual sound insulation frequency and the required sound insulation frequency, if the difference is less than ɛ, judging that the sound insulation unit meets the design requirement of the refrigeration device, and if the difference is more than or equal to ɛ, changing one or more parameters of the sound insulation unit, and recalculating the actual sound insulation frequency of the sound insulation unit; a plurality of sound insulation units meeting design requirements are adopted to manufacture the noise reduction device.
Description
Technical Field
The present application relates to a method of designing a noise reduction device for a refrigeration device.
Background
In real life, noise of refrigerating devices such as refrigerators and freezers is high, particularly noise generated by compressors of the refrigerators and freezers is high, and how to reduce noise of the compressors is a problem which is difficult to solve in household life. In addition, since the structure of each refrigerator or freezer is different and the compressor power is different, the noise generated by the compressor is different in practical application, and therefore, a design for matching the noise reduction material with the compressor to a certain degree is required. The best sound insulation and noise reduction effects can be achieved only when the sound insulation frequency of the noise reduction material is matched with the acoustic characteristics of compressors of refrigerators and freezers.
Disclosure of Invention
In order to solve one of the above problems, the present application proposes a design method that can produce a noise reduction device according to the actual noise of the compressor of the refrigeration device.
In order to achieve the above object, an embodiment of the present application provides the following technical solutions:
a method of designing a noise reducer for a refrigeration unit, the refrigeration unit including a compressor, comprising: placing the refrigerating device in the anechoic chamber or the semi-anechoic chamber, and enabling the refrigerating device to work normally; determining the position of a compressor, and placing a noise collecting device at a position which is separated from the compressor by a distance D; testing to obtain the frequency characteristic of the noise of the compressor, analyzing the frequency spectrum distribution condition of the noise, and determining the frequency with the highest noise volume peak value and/or the second highest noise volume peak value as the required sound insulation frequency; extracting one or more sound insulation units, respectively testing the sound insulation amount of noise of the sound insulation units, and recording the frequency of the noise when the sound insulation amount is maximum as an actual sound insulation frequency; calculating the difference between the actual sound insulation frequency and the required sound insulation frequency, if the difference is smaller than ɛ, judging that the sound insulation unit meets the design requirement of the refrigeration device, if the difference is larger than or equal to ɛ, changing one or more parameters of the sound insulation unit, carrying out sound insulation test again, and recalculating the actual sound insulation frequency of the sound insulation unit until the sound insulation unit meets the design requirement of the refrigeration device; and manufacturing the noise reduction device by adopting a plurality of sound insulation units meeting the design requirements, and installing the noise reduction device at a position close to the compressor in the refrigerating device.
As a further improvement of the invention, the sound insulation unit comprises an outer frame which is annularly arranged and provided with two symmetrical openings, a film which covers one opening of the outer frame, and a mass block which is accommodated in the outer frame, wherein the mass block is attached to the film; the thicker the thickness of the film is, the higher the actual sound insulation frequency of the sound insulation unit is; the larger the size of the frame is, the larger the size of the film is, and the lower the actual sound insulation frequency of the sound insulation unit is; the larger the elastic modulus of the film is, the higher the actual sound insulation frequency of the sound insulation unit is; the larger the pretightening force between the film and the frame is, the higher the actual sound insulation frequency of the sound insulation unit is; the larger the weight of the mass block is, the smaller the actual sound insulation frequency of the sound insulation unit is.
As a further improvement of the present invention, the mass block is fixed to the membrane, and the larger the area of the mass block in contact with the membrane is, the higher the actual sound insulation frequency of the sound insulation unit is.
As a further improvement of the present invention, the sound insulation unit further includes a constraint portion for fixing the mass block on an outer frame, the constraint portion extends outward from two opposite ends of the mass block to be connected and fixed with the outer frame, and the larger the area of the mass block in contact with the thin film is, the higher the actual sound insulation frequency of the sound insulation unit is.
As a further improvement of the invention, a through hole for heat dissipation is formed in the mass block in a penetrating manner, and the larger the size of the through hole is, the higher the actual sound insulation frequency of the sound insulation unit is.
As a further improvement of the present invention, "testing the frequency characteristics of the noise of the compressor to obtain the spectral distribution of the noise source" specifically includes: an 1/3 octave distribution of compressor noise volume was observed over a range of 100 to 2000Hz and the frequencies of the first three volume peaks were determined.
As a further improvement of the present invention, "determining the frequency at which the peak value of the noise volume is the highest and/or the next highest to the peak value as the sound insulation frequency is required" specifically includes: when the volume difference between the highest peak value of the noise volume and the next highest peak value is larger than 10dB, determining the highest frequency of the peak value as the required sound insulation frequency; and when the volume difference between the three volume peaks is within 10dB, determining that the peak highest frequency and the peak second highest frequency are two required sound insulation frequencies.
As a further improvement of the invention, the number of the types of the sound insulation units meeting the design requirements of the refrigeration device is the same as the number of the required sound insulation frequencies.
As a further development of the invention, D ranges between 50mm and 200 mm.
As a further improvement of the invention, ɛ is 5 Hz.
The invention has the beneficial effects that: according to the invention, through specific test on the noise of the compressor, the special noise reduction device for noise reduction and sound insulation of the compressor of the refrigeration device is designed, so that the cost is saved, and meanwhile, a better noise reduction effect can be achieved.
Drawings
The accompanying drawings, which are included to provide a further understanding of the application and are incorporated in and constitute a part of this application, illustrate embodiment(s) of the application and together with the description serve to explain the application and not to limit the application. In the drawings:
FIG. 1 is a schematic flow chart of a design method of the present invention;
fig. 2 is a schematic structural view of a first embodiment of the sound-insulating unit according to the present invention;
fig. 3 is a schematic structural view of a sound-proof unit according to a second embodiment of the present invention.
Detailed Description
In order to make the objects, technical solutions and advantages of the present application more apparent, the technical solutions of the present application will be described in detail and completely with reference to the following specific embodiments of the present application and the accompanying drawings. It should be apparent that the described embodiments are only some of the embodiments of the present application, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present application.
Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the accompanying drawings are illustrative only for the purpose of explaining the present invention, and are not to be construed as limiting the present invention.
In the description of the present invention, it is to be understood that the terms "longitudinal", "lateral", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", and the like, indicate orientations or positional relationships based on those shown in the drawings, and are used merely for convenience of description and for simplicity of description, and do not indicate or imply that the referenced devices or elements must have a particular orientation, be constructed in a particular orientation, and be operated, and thus, are not to be construed as limiting the present invention.
In the description of the present invention, unless otherwise specified and limited, it is to be noted that the terms "mounted," "connected," and "connected" are to be interpreted broadly, and may be, for example, a mechanical connection or an electrical connection, a communication between two elements, a direct connection, or an indirect connection via an intermediate medium, and specific meanings of the terms may be understood by those skilled in the art according to specific situations.
As shown in fig. 1, the present invention provides a method for designing a noise reduction device of a refrigeration device, in particular, a refrigerator or an ice chest. In addition, in a refrigerator or an ice chest, noise of a compressor is the largest, and therefore, how to reduce the noise of the compressor becomes a difficult problem. Further, since the structure of different refrigerators or freezers is different and the power of the compressor is different, if the same noise reducer is used, there is a possibility that the noise reduction is not complete or material resources are wasted.
Therefore, the present invention designs different noise reduction devices for different refrigeration devices by analyzing the noise of the compressor of the refrigeration device, and in the present embodiment, the noise reduction devices are made of the acoustic metamaterial. Specifically, the following is:
the design method of the noise reduction device of the refrigerating device comprises the following steps:
s1, placing the refrigerating device in the anechoic chamber or the semi-anechoic chamber, and enabling the refrigerating device to work normally;
s2, determining the position of the compressor, and placing the noise collecting device at a position with a distance D from the compressor to collect the noise emitted by the noise source;
s3, testing to obtain the frequency characteristic of the noise of the compressor, analyzing the frequency spectrum distribution condition of the noise, and determining the frequency with the highest noise volume peak value and/or the second highest noise volume peak value as the required sound insulation frequency f0 and/or f 0';
s4, extracting one or more sound insulation units, respectively testing the sound insulation amount of noise of the sound insulation units, and recording the frequency of the noise with the maximum sound insulation amount as the actual sound insulation frequency f 1;
s5, respectively calculating the difference between the actual sound insulation frequency f1 and the required sound insulation frequency f0, if the difference is smaller than ɛ, judging that the sound insulation unit of the parameter meets the design requirement of the refrigeration device, if the difference is larger than or equal to ɛ, changing one or more parameters of the sound insulation unit, carrying out sound insulation test again, and recalculating the actual sound insulation frequency f1 of the sound insulation unit until the difference between the actual sound insulation frequency f1 and the required sound insulation frequency f0 of the sound insulation unit is smaller than ɛ;
and S6, manufacturing the noise reduction device by adopting a plurality of sound insulation units meeting the design requirements, and installing the noise reduction device at a position close to the compressor in the refrigerating device.
Therefore, by the method, the noise reduction device can be customized for the refrigerating device, so that the noise reduction device can meet the requirements of the refrigerating device, and the best noise reduction effect is achieved under the conditions of meeting the cost and heat dissipation.
Specifically, in step S1, in the present embodiment, the refrigeration apparatus is placed in the half-muffling chamber. The semi-anechoic chamber is an extremely important experimental site in acoustic experiments and noise tests, and the main function of the semi-anechoic chamber is to provide a low-noise test environment in a semi-free-field space. A semi-anechoic chamber is one in which no reflector (surface) is present elsewhere in the chamber, except on the ground. Since the refrigerating device is placed on the ground in the embodiment, the ground is obviously a reflecting surface in the process of transmitting the noise of the compressor, and the refrigerating device is placed in the semi-silencing chamber, so that the simulation condition is closer to the actual condition, and the test accuracy is improved. The background noise of the semi-anechoic chamber must be low to meet the requirements of the test environment, and the sound absorption coefficient of the semi-anechoic chamber must be high on the wall surface except the ground, and generally, the sound absorption coefficient must be more than 99%. Therefore, the test is carried out in the semi-silencing chamber, the test accuracy can be further improved, and the best test effect is achieved.
In the step S2, D ranges from 50mm to 200mm, i.e., the distance between the noise collecting device and the compressor is maintained between 50mm to 200 mm. The distance between the noise collecting device and the compressor cannot be too small or too large, and too small a distance may cause the noise collected by the noise collecting device to be too concentrated or too large, and too large a distance may cause the noise collected by the noise collecting device to be unclear. And, it is ensured that there is no sound transmission obstacle between the noise collecting device and the compressor. Of course, in the present embodiment, the noise collection device is a microphone.
In step S3, specifically, the frequency characteristic of the noise of the compressor is measured by acoustic test software, and of course, the acoustic test software is connected to the noise collecting device. After the frequency characteristic of the compressor noise is obtained, the frequency spectrum distribution condition of the noise is specifically analyzed.
Specifically, an 1/3 octave of compressor noise was observed in the range of 100 to 2000 Hz. The observation is made mainly in the range of 100 to 2000Hz, since the noise emitted by the compressor is mainly low and medium frequency noise. Low or medium frequency noise is different from high frequency noise, and high frequency noise can be quickly attenuated through long distance transmission or meeting obstacles. The decibel of the low-frequency or medium-frequency noise is gradually decreased, and the noise can easily pass through the barrier, so that the harm to the health of people is the greatest. Therefore, observing the spectral characteristics of noise in the range of 100 to 2000Hz, and controlling and attenuating noise in this range, is particularly important in daily life. And the noise spectrum is observed in 1/3 octaves to make the observation clearer.
In this embodiment, the frequencies of the first three noise volume peaks are determined by observing the compressor noise within the 1/3 octave distribution. Of course, the first four or more peaks can be determined by observing the frequency spectrum of the noise of the compressor, and the purpose of the invention can be achieved, but the frequency of the first three noise volume peaks is most accurate to observe, and the efficiency is fastest. After the frequencies of the first three peaks are obtained, the volume levels and the frequencies at which the three volume peaks are located are observed. When the difference of the noise volume between the highest volume peak value and the next highest peak value is larger than 10dB, the energy of the noise with the frequency with the highest volume peak value is extremely large, and the frequency with the highest peak value is determined as the required sound insulation frequency f 0; when the volume difference between the three peak values is within 10dB, namely less than or equal to 10dB, the noise energy of the frequency of the three peak values is very large, and at the moment, the frequency with the highest peak value and the frequency with the next highest peak value are determined as two required sound insulation frequencies f0 and/or f 0'.
Specifically, the number of the types of the sound insulation units meeting the design requirements of the refrigeration device is the same as the number of the required sound insulation frequencies, that is, if the number of the required sound insulation frequencies f0 is one, the types of the sound insulation units are only one, and the sound insulation units are only used for mainly isolating the noise volume peak value of the required sound insulation frequency f 0; if the number of the required sound insulation frequencies f0 is two, the number of the sound insulation units is also two, and the two sound insulation units are respectively used for isolating the noise volume peak values of the two required sound insulation frequencies f0 and f 0'. However, if the number of the sound insulation units is too large, the design and arrangement of the sound insulation units in the whole noise reduction device are not facilitated, and therefore, it is preferable that the number of the sound insulation units in the present embodiment is two at most.
In addition, the type of the sound insulation unit in the present embodiment means that the actual sound insulation frequency of the sound insulation unit is affected by changes in various parameters of the sound insulation unit, the structures of the sound insulation units having the same actual sound insulation frequency are completely the same, and the types of the sound insulation units having the same structure are the same. Of course, the number of the sound insulation units of the same kind of the sound insulation device can be one or more than one.
Then, by the above method, the specific magnitude distribution of the noise of the compressor of the refrigeration apparatus is determined, and the required sound insulation frequency f0 and/or f0 'is identified, and the required sound insulation frequency f0 and/or f 0' having the highest peak value and/or the next highest peak value is the main sound insulation frequency required to be used as sound insulation and noise reduction treatment.
In step S4, specifically, one or more sound insulation units are extracted and subjected to a sound insulation test of noise. In the present embodiment, different types of sound insulation units are placed in the sound tube respectively for testing. The specific test method is that the sound insulation unit is placed in a sound tube, and the sound insulation amount of the sound insulation unit is tested within the frequency range of 100-1200 Hz. And determining the frequency at which the sound insulation amount of the sound insulation unit is the largest, and recording the frequency as the actual sound insulation frequency f 1.
In the present embodiment, the noise in the sound pipe starts from 100Hz, and the decibel of the noise gradually increases until the maximum sound insulation amount of the sound insulation unit at the frequency is reached, and then the next frequency test is started, in the present embodiment, the sound insulation amount of the sound insulation unit in the range of 100 to 1200Hz is separately tested at intervals of 10Hz, so that the sound insulation amount variation of the sound insulation unit in the range of 100 to 1200Hz can be obtained, and the actual sound insulation frequency f1 at which the maximum sound insulation amount is in the range of 100 to 1200Hz can be easily compared.
Of course, if the number of the frequencies to be insulated is two, namely f0 and f0 ', two kinds of sound insulation units are required to be designed to separate the two frequencies to be insulated, and the actual sound insulation frequencies of the two sound insulation units are f1 and f 1'.
Then, in step S5, the difference between the actual sound insulation frequency and the desired sound insulation frequency is calculated. And when the number of the actual sound insulation frequency and the required sound insulation frequency is more than one, calculating the difference value between the corresponding actual sound insulation frequency and the required sound insulation frequency. And when the difference is smaller than ɛ, judging that the sound insulation unit under the parameter meets the design requirement of the refrigeration device, if the difference is larger than or equal to ɛ, changing one or more parameters of the sound insulation unit, carrying out sound insulation quantity test again, and recalculating the actual sound insulation frequency of the sound insulation unit until the difference between the actual sound insulation frequency and the required sound insulation frequency of the sound insulation unit is smaller than ɛ.
In this embodiment, ɛ has a value of 5 Hz. Therefore, if the difference between the actual sound insulation frequency of the sound insulation unit and the required sound insulation frequency of the noise of the compressor is less than 5Hz, it can be determined that the sound insulation unit can be used to isolate the peak volume of the noise. If the difference between the actual sound insulation frequency of the sound insulation unit and the required sound insulation frequency of the noise of the compressor is larger than 5Hz, the difference between the actual sound insulation frequency of the sound insulation unit and the required sound insulation frequency of the compressor is too large, the sound insulation unit cannot effectively insulate and reduce the noise of the compressor, and the sound insulation unit cannot be used for isolating the volume peak value of the noise.
As shown in fig. 2 and fig. 3, specifically, the sound insulation unit includes an outer frame 1 disposed in a ring shape and having two symmetrical openings, a membrane covering an opening of the outer frame 1, and a mass block 2 accommodated in the outer frame 1, where the mass block 2 is attached to the membrane. In a first embodiment, the mass 2 is fixed to the membrane, and the mass 2 can be connected to the membrane by means of a snap, an adhesive, or the like. In the second embodiment, the sound insulation unit further includes a constraint portion 21, and the constraint portion 21 extends outwards from two opposite ends of the mass block 2 to be connected and fixed with the outer frame 1. In addition, a through hole 22 for dissipating heat may be formed through the mass block 2, and a penetrating direction of the through hole 22 faces the opening.
Specifically, the thicker the thickness of the film is, the higher the actual sound insulation frequency of the sound insulation unit is; the larger the size of the outer frame is, the larger the size of the film is, and the lower the actual sound insulation frequency of the sound insulation unit is; the larger the elastic modulus of the film is, the higher the actual sound insulation frequency of the sound insulation unit is; the larger the pretightening force between the film and the outer frame is, the higher the actual sound insulation frequency of the sound insulation unit is; the greater the weight of the mass 2, the lower the actual sound insulation frequency of the sound insulation unit. And the larger the area of the mass block 2 attached to the membrane is, the higher the actual sound insulation frequency of the sound insulation unit is. The larger the size of the through hole 22 penetrating in the mass block 2 is, the higher the actual sound insulation frequency of the sound insulation unit is.
Therefore, if the actual sound insulation frequency of the sound insulation unit is too large, far exceeding the required sound insulation frequency of the compressor noise, the actual sound insulation frequency can be reduced by changing the following parameters: the thickness of the film is reduced, the size of the frame is increased, namely the size of the film is increased, the elastic modulus of the film is reduced, the pretightening force between the film and the outer frame is reduced, the weight of the mass block 2 is increased, the contact area between the mass block 2 and the film is reduced, and the size of the through hole 22 in the mass block 2 is reduced. Of course, if the actual sound insulation frequency of the sound insulation unit is too low, the corresponding method for changing the parameters is opposite, and the details are not described here.
Finally, the sound insulation unit for reducing noise of the compressor of the refrigeration apparatus can be obtained by the above-described step S5. Then in step S6, a noise reducing device is fabricated using a plurality of the above-described sound insulation units, and the noise reducing device is installed in the refrigeration apparatus at a position near the compressor. In the present embodiment, the noise reducer may be in a plate shape to block the path of the outward noise generated from the compressor, or may be in a box shape to completely house the compressor, thereby achieving the best noise reduction effect.
In summary, by the above design method for the noise reduction device of the refrigeration device, the noise reduction device of the refrigeration device can be customized, and the sound insulation unit can be selected and manufactured according to the noise emitted by the compressor of the refrigeration device. Therefore, the noise reduction device can achieve the best sound insulation effect.
It should be understood that although the present description refers to embodiments, not every embodiment may contain only a single embodiment, and such description is for clarity only, and those skilled in the art will be able to make the description as a whole, and the embodiments may be appropriately combined to form other embodiments as will be appreciated by those skilled in the art.
The above detailed description is merely illustrative of possible embodiments of the present invention and is not intended to limit the scope of the invention, which is intended to include all equivalent embodiments or modifications within the scope of the present invention without departing from the technical spirit of the present invention.
Claims (9)
1. A method for designing a noise reduction device of a refrigeration device including a compressor, characterized in that: the method comprises the following steps:
placing the refrigerating device in the anechoic chamber or the semi-anechoic chamber, and enabling the refrigerating device to work normally;
determining the position of a compressor, and placing a noise collecting device at a position which is separated from the compressor by a distance D;
testing the frequency characteristic of the noise of the compressor, analyzing the frequency spectrum distribution condition of the noise, at least determining the frequency of the first three noise volume peaks, and determining the peak value highest frequency as the required sound insulation frequency when the volume difference between the highest noise volume peak value and the next highest noise volume peak value is more than 10 dB; when the volume difference between the three volume peak values is within 10dB, determining the peak value highest frequency and the peak value second highest frequency as two required sound insulation frequencies;
extracting one or more sound insulation units, respectively testing the sound insulation amount of noise of the sound insulation units, and recording the frequency of the noise when the sound insulation amount is maximum as an actual sound insulation frequency;
calculating the difference between the actual sound insulation frequency and the required sound insulation frequency, if the difference is smaller than ɛ, judging that the sound insulation unit meets the design requirement of the refrigeration device, if the difference is larger than or equal to ɛ, changing one or more parameters of the sound insulation unit, carrying out sound insulation test again, and recalculating the actual sound insulation frequency of the sound insulation unit until the sound insulation unit meets the design requirement of the refrigeration device;
and manufacturing the noise reduction device by adopting a plurality of sound insulation units meeting the design requirements, and installing the noise reduction device at a position close to the compressor in the refrigerating device.
2. A method of designing a noise reducing device of a refrigerating apparatus according to claim 1, wherein: the sound insulation unit comprises an outer frame which is annularly arranged and provided with two symmetrical openings, a film which covers one opening of the outer frame and a mass block which is accommodated in the outer frame, wherein the mass block is attached to the film; the thicker the thickness of the film is, the higher the actual sound insulation frequency of the sound insulation unit is; the larger the size of the frame is, the larger the size of the film is, and the lower the actual sound insulation frequency of the sound insulation unit is; the larger the elastic modulus of the film is, the higher the actual sound insulation frequency of the sound insulation unit is; the larger the pretightening force between the film and the frame is, the higher the actual sound insulation frequency of the sound insulation unit is; the larger the weight of the mass block is, the smaller the actual sound insulation frequency of the sound insulation unit is.
3. A method of designing a noise reducing device of a refrigerating apparatus according to claim 2, wherein: the mass block is fixed on the film, and the larger the area of the mass block, which is attached to the film, is, the higher the actual sound insulation frequency of the sound insulation unit is.
4. A method of designing a noise reducing device of a refrigerating apparatus according to claim 2, wherein: the sound insulation unit further comprises a constraint part for fixing the mass block on the outer frame, the constraint part extends outwards from two opposite ends of the mass block to be connected and fixed with the outer frame, the larger the area of the mass block, which is attached to the film, is, the higher the actual sound insulation frequency of the sound insulation unit is.
5. The method of designing a noise reducer for a refrigeration apparatus according to claim 4, wherein: and a through hole for heat dissipation is formed in the mass block in a penetrating manner, and the larger the size of the through hole is, the higher the actual sound insulation frequency of the sound insulation unit is.
6. A method of designing a noise reducing device of a refrigerating apparatus according to claim 1, wherein: the step of testing the frequency characteristics of the noise of the compressor and analyzing the frequency spectrum distribution of the noise specifically comprises the following steps:
an 1/3 octave distribution of compressor noise volume was observed over a range of 100 to 2000Hz and the frequencies of the first three volume peaks were determined.
7. A method of designing a noise reducing device of a refrigerating device according to claim 6, wherein: the number of the types of the sound insulation units meeting the design requirements of the refrigeration device is the same as the number of the required sound insulation frequencies.
8. A method of designing a noise reducing device of a refrigerating apparatus according to claim 1, wherein: d ranges between 50mm and 200 mm.
9. A method of designing a noise reducing device of a refrigerating apparatus according to claim 1, wherein: ɛ is 5 Hz.
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