CN111486514B - Noise elimination device, air conditioner, noise elimination control method, and computer-readable storage medium - Google Patents
Noise elimination device, air conditioner, noise elimination control method, and computer-readable storage medium Download PDFInfo
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- CN111486514B CN111486514B CN202010337081.XA CN202010337081A CN111486514B CN 111486514 B CN111486514 B CN 111486514B CN 202010337081 A CN202010337081 A CN 202010337081A CN 111486514 B CN111486514 B CN 111486514B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
- F24F1/08—Compressors specially adapted for separate outdoor units
- F24F1/12—Vibration or noise prevention thereof
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
- F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
- F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
- F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
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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
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/40—Fluid line arrangements
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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
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/12—Sound
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- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
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- Thermal Sciences (AREA)
- Air Conditioning Control Device (AREA)
Abstract
The invention provides a silencing device, an air conditioner, a silencing control method and a computer readable storage medium. Wherein, noise eliminator is applicable to the air conditioner, and the air conditioner includes refrigerant pipeline and compressor, and noise eliminator includes: and the length of the silencing pipeline is odd times of the half wavelength of the noise sound wave of the compressor. The noise of the compressor flows in the refrigerant pipeline along with a part of refrigerant flowing out of the compressor, a part of the noise enters the silencing pipeline from one end of the silencing pipeline and flows, the part of the noise of the compressor flowing through the refrigerant pipeline can branch into the silencing pipeline through the other end of the silencing pipeline, and the two sound waves meet in the silencing pipeline. Because the length of the silencing pipeline is odd times of the half wavelength of the noise sound wave of the compressor, the phases of the two sound waves are opposite, so that the sound energy in the silencing pipeline is greatly reduced, the pulsation noise of the compressor transmitted to the indoor unit is reduced, and the use comfort of the indoor unit is prevented from being influenced.
Description
Technical Field
The invention relates to the technical field of air conditioners, in particular to a silencing device, an air conditioner, a silencing control method and a computer readable storage medium.
Background
Conventionally, in order to eliminate transmission of compressor transmission sound caused by pressure pulsation of a compressor of an outdoor unit of an air conditioner to an indoor unit of the air conditioner, a muffler is generally connected to a four-way valve member. However, the method is easy to have the problems of limited assembly space position of the silencer, insufficient silencing quantity of the silencer, pipeline deformation and pipe breakage caused by the self weight of the silencer, and the like.
Disclosure of Invention
The present invention is directed to solving at least one of the problems of the prior art or the related art.
To this end, one aspect of the invention is to propose a silencing device.
Another aspect of the present invention is to provide an air conditioner.
Yet another aspect of the present invention is to provide a sound damping control method.
Yet another aspect of the present invention is to provide a computer-readable storage medium.
In view of the above, according to an aspect of the present invention, there is provided a muffler device for an air conditioner, the air conditioner including a refrigerant pipeline and a compressor, the muffler device comprising: and the length of the silencing pipeline is odd times of the half wavelength of the noise sound wave of the compressor.
In the technical scheme, a silencing pipeline is arranged on a pipeline through which a refrigerant flows into an indoor unit from an outdoor unit, so that part of noise of a compressor flows in the refrigerant pipeline along with the refrigerant flowing out of the compressor, part of the noise enters the silencing pipeline from one end of the silencing pipeline and flows, part of the noise of the compressor flowing through the refrigerant pipeline can branch into the silencing pipeline through the other end of the silencing pipeline, and two sound waves meet in the silencing pipeline. Because the length of the silencing pipeline is odd times of the half wavelength of the noise sound wave of the compressor, the phases of the two sound waves are opposite, so that the sound energy in the silencing pipeline is greatly reduced, the pulsation noise of the compressor transmitted to the indoor unit is reduced, and the use comfort of the indoor unit is prevented from being influenced. In addition, the problems of insufficient silencing quantity of the silencer, pipeline deformation and pipe breakage caused by the self weight of the silencer and the like caused by additionally connecting the silencer in the four-way valve component can be avoided.
According to the present invention, the muffler device may further include the following features:
in the above technical solution, the method further comprises: the first flow control valve is arranged on the silencing pipeline and is close to the first end of the silencing pipeline, and the first end is one end, close to the compressor, of the two ends of the silencing pipeline; and the second flow control valve is arranged on the silencing pipeline and is close to the second end of the silencing pipeline, the second end is the other end of the two ends of the silencing pipeline except the first end, the first flow control valve controls the flow of the refrigerant flowing into the first end of the silencing pipeline from the refrigerant pipeline, and the second flow control valve controls the flow of the refrigerant flowing into the second end of the silencing pipeline from the refrigerant pipeline.
In the technical scheme, two flow control valves are arranged on the silencing pipeline and are respectively arranged at two ends of the silencing pipeline, and the flow of the refrigerant flowing into the two ends of the silencing pipeline is respectively controlled by controlling the opening degrees of the two flow control valves, namely the size of the cross section area of the silencing pipeline is controlled, so that the silencing quantity and the silencing frequency are adjusted, and the silencing requirements on high-frequency noise and low-frequency noise are met.
In any of the above technical solutions, the first flow control valve is provided with a first pressure sensor; the second flow control valve is provided with a second pressure sensor, wherein the first pressure sensor detects pressure pulsation of the refrigerant flowing into the first end from the refrigerant pipeline, and the second pressure sensor detects pressure pulsation of the refrigerant flowing into the second end from the refrigerant pipeline.
In the technical scheme, the flow control valve is provided with a pressure sensor, and the pressure sensor is used for detecting the pressure pulsation of the refrigerant flowing into two ends of the silencing pipeline, so that the frequency of the noise of the compressor is determined according to the pressure pulsation of the refrigerant, the opening degree of the flow control valve is controlled according to the frequency of the noise of the compressor, and the silencing of sound waves with different frequencies is realized.
In any of the above technical solutions, the method further includes: the first connecting pipe is connected with the first ends of the refrigerant pipeline and the silencing pipeline; and the second connecting pipe is connected with the second ends of the refrigerant pipeline and the silencing pipeline.
In the technical scheme, the first connecting pipe and the second connecting pipe are three-way pipes, two interfaces of the three-way pipes are connected with the refrigerant pipeline, and the other interface of the three-way pipes is connected with the silencing pipeline, so that the silencing pipeline is firmly connected with the refrigerant pipeline.
In any of the above technical solutions, the refrigerant pipeline includes one or a combination of the following: the air conditioner comprises an exhaust pipe, a low-pressure valve pipe and an air return pipe, wherein the exhaust pipe is arranged between a reversing valve and a compressor of the air conditioner, the low-pressure valve pipe is arranged between the low-pressure valve and the reversing valve of the air conditioner, and the air return pipe is arranged between a liquid storage device and the reversing valve of the compressor of the air conditioner.
In the technical scheme, according to the noise elimination requirement of sound transmission of the indoor side compressor under the refrigeration or heating working condition of the air conditioner, the noise elimination pipeline can be positioned between the outdoor unit and the indoor unit. The silencing pipeline can be connected to the exhaust pipe, the low-pressure valve pipe or the muffler, for example, the silencing pipeline can be located on the exhaust pipe or the low-pressure valve pipe under the heating working condition of the air conditioner, and the silencing pipeline can be located on the muffler aiming at the refrigerating working condition of the air conditioner so as to meet silencing requirements under different working conditions and improve silencing effect. In addition, the two flow control valves are not limited to be located on the same pipeline, and two ends of the muffling pipeline are not limited to be connected to the same pipeline, for example, one end of the muffling pipeline is connected to the exhaust pipe, and the other end of the muffling pipeline is connected to the low-pressure valve pipe, or one end of the muffling pipeline is connected to the exhaust pipe, and the other end of the muffling pipeline is connected to the return pipe.
In any of the above solutions, the sectional diameter of the muffling line ranges from 6.45 mm to 12 mm.
In the technical scheme, the numerical range of the diameter of the section of the silencing pipeline is 6.45 mm to 12 mm, namely the cross section area of the silencing pipeline can be changed, so that the silencing requirements for high-frequency and low-frequency noises are met.
According to another aspect of the present invention, there is provided an air conditioner including: a compressor; a refrigerant pipeline; and a muffler device according to any one of the above-described embodiments.
In the technical scheme, the air conditioner comprises a compressor, a refrigerant pipeline and a noise eliminator, wherein two ends of the noise eliminator pipeline are connected with the refrigerant pipeline, the noise eliminator is used for reducing the pulsation noise of the compressor transmitted to the indoor unit, and the comfort of the indoor unit is prevented from being influenced.
According to still another aspect of the present invention, there is provided a sound-deadening control method applied to a sound-deadening device according to any one of the above aspects, the sound-deadening control method including: and controlling the noise elimination pipeline of the noise elimination device to be communicated, so that the refrigerant in the refrigerant pipeline flows into the noise elimination pipeline from two ends of the noise elimination pipeline respectively, and eliminating the noise of the compressor driven along with the refrigerant.
In the technical scheme, the noise elimination pipeline is controlled to be communicated, so that part of noise of the compressor flows in the refrigerant pipeline along with a refrigerant flowing out of the compressor, part of noise enters the noise elimination pipeline from one end of the noise elimination pipeline and flows, part of noise of the compressor flowing through the refrigerant pipeline can branch into the noise elimination pipeline through the other end of the noise elimination pipeline, and two sound waves meet in the noise elimination pipeline. Because the length of the silencing pipeline is odd times of the half wavelength of the noise sound wave of the compressor, the phases of the two sound waves are opposite, so that the sound energy in the silencing pipeline is greatly reduced, the pulsation noise of the compressor transmitted to the indoor unit is reduced, and the use comfort of the indoor unit is prevented from being influenced.
According to the above noise cancellation control method of the present invention, the following technical features may be further provided:
in the above technical solution, the step of controlling the conduction of the muffling pipeline of the muffling apparatus specifically includes: a first flow rate control valve of the muffler device is controlled to open and a second flow rate control valve of the muffler device is controlled to open.
In the technical scheme, two flow control valves are arranged on the silencing pipeline and are respectively arranged at two ends of the silencing pipeline, and the silencing pipeline is conducted by controlling the two flow control valves to be opened.
In any of the above technical solutions, the method further includes: and in the process of conducting the silencing pipeline, acquiring the frequency of the noise of the compressor, and controlling the opening of the first flow control valve of the silencing device and the opening of the second flow control valve of the silencing device according to the frequency of the noise of the compressor.
In the technical scheme, the pressure pulsation of the refrigerant flowing into the silencing pipeline is obtained, so that the frequency of the noise of the compressor is determined according to the pressure pulsation of the refrigerant, the size of the cross section area of the silencing pipeline is controlled by controlling the opening degrees of the two flow control valves, the silencing quantity and the silencing frequency are adjusted, and the silencing requirements for high-frequency and low-frequency noise are met.
In any of the above technical solutions, the step of obtaining the frequency of the noise of the compressor and controlling the opening degree of the first flow rate control valve of the muffler device and the opening degree of the second flow rate control valve of the muffler device according to the frequency of the noise of the compressor specifically includes: setting a first flow control valve as a front end control valve and a second flow control valve as a rear end control valve when the air conditioner is in a heating mode, or setting the second flow control valve as the front end control valve and the first flow control valve as the rear end control valve when the air conditioner is in a cooling mode; and calculating the frequency of the noise of the front-end compressor according to the refrigerant pressure pulsation detected by the pressure sensor of the front-end control valve, and controlling the opening of the front-end control valve and the opening of the rear-end control valve according to the frequency of the noise of the front-end compressor.
In the technical scheme, when the air conditioner is in a heating mode, a refrigerant flowing out of a compressor firstly enters an indoor heat exchanger and then enters an outdoor heat exchanger, the refrigerant firstly flows into a noise elimination pipeline through a first flow control valve close to the compressor, so that the first flow control valve close to the compressor is set as a front end control valve, and a second flow control valve far away from the compressor is set as a rear end control valve, or when the air conditioner is in a cooling mode, the refrigerant flowing out of the compressor firstly enters the outdoor heat exchanger and then enters the indoor heat exchanger, the refrigerant firstly flows into the noise elimination pipeline through a second flow control valve far away from the compressor, so that the second flow control valve far away from the compressor is set as a front end control valve, and the first flow control valve close to the compressor is set as a rear end control valve. The noise control method comprises the steps of calculating the frequency of noise of a front-end compressor according to refrigerant pressure pulsation detected by a pressure sensor of a front-end control valve, wherein the noise of the front-end compressor is the noise at the position of a first flow control valve in a heating mode, the noise of the front-end compressor is the noise at the position of a second flow control valve in a cooling mode, and further controlling the opening degree of the front-end control valve and the opening degree of a rear-end control valve according to the frequency of the noise of the front-end compressor, so that the size of the cross section area of a silencing pipeline is controlled through the opening degrees of the two flow control valves, and the noise frequency is detected and the corresponding opening degree of the flow control valve is fed back to meet silencing requirements and silencing frequencies of.
In any of the above technical solutions, the step of controlling the opening degree of the front end control valve and the opening degree of the rear end control valve according to the frequency of the noise of the front end compressor specifically includes: judging whether the frequency of the noise of the front-end compressor is smaller than a frequency threshold value; when the frequency of the noise of the front-end compressor is judged to be smaller than the frequency threshold value, controlling the opening degree of the front-end control valve and the opening degree of the rear-end control valve to be first preset opening degrees; and when the frequency of the noise of the front-end compressor is judged to be larger than or equal to the frequency threshold value, controlling the opening of the front-end control valve and the opening of the rear-end control valve to be second preset openings, calculating the noise of the rear-end compressor according to the refrigerant pressure pulsation detected by the pressure sensor of the rear-end control valve, and controlling the opening of the front-end control valve and the opening of the rear-end control valve according to the frequency of the noise of the rear-end compressor, wherein the second preset opening is smaller than the first preset opening.
In the technical scheme, the frequency (which may be a peak frequency) of the noise of the front-end compressor is determined to be high frequency or low frequency, and if the frequency of the noise of the front-end compressor is smaller than a frequency threshold, the frequency threshold is determined to be low frequency, wherein the frequency threshold can be self-defined, for example, set to 500Hz, the front-end control valve and the rear-end control valve are opened, and the opening degrees of valve cores of the front-end control valve and the rear-end control valve are maintained to be a first preset opening degree, which is a total opening degree, so that sound waves flowing through the muffling pipeline and the refrigerant pipeline interfere with each other at a rear-end collection part, and the transmission of low-. If the frequency of the noise of the front-end compressor is larger than or equal to the frequency threshold value, the front-end control valve and the rear-end control valve are opened, the valve core opening degrees of the front-end control valve and the rear-end control valve are kept to be second preset opening degrees, the second preset opening degree is 1/2 of the total opening degree, the opening degrees of the front-end control valve and the rear-end control valve are controlled according to the frequency of the noise of the rear-end compressor, the noise of the rear-end compressor is the noise of the position of the second flow control valve in the heating mode, and the noise of the rear-end compressor is the noise of the position of the first flow control valve in the cooling mode.
In any of the above technical solutions, the step of controlling the opening degree of the front end control valve and the opening degree of the rear end control valve according to the frequency of the noise of the rear end compressor specifically includes: judging whether the frequency of the noise of the rear-end compressor is smaller than a frequency threshold value; when the frequency of the noise of the rear-end compressor is judged to be smaller than the frequency threshold value, controlling the opening degree of the front-end control valve to be kept at a second preset opening degree, and controlling the opening degree of the rear-end control valve to be a third preset opening degree, wherein the third preset opening degree is smaller than the second preset opening degree; and when the frequency of the noise of the rear-end compressor is judged to be greater than or equal to the frequency threshold value, controlling the opening degree of the front-end control valve and the opening degree of the rear-end control valve to be fourth preset opening degrees, wherein the fourth preset opening degree is smaller than the second preset opening degree and larger than the third preset opening degree.
In the technical scheme, if the frequency of the noise of the front-end compressor is greater than or equal to the frequency threshold, the front-end control valve and the rear-end control valve are opened, and after the valve core opening degrees of the front-end control valve and the rear-end control valve are kept to be the second preset opening degree, the frequency (which can be peak frequency) of the noise of the rear-end compressor is judged to be high frequency or low frequency, if the frequency of the noise of the rear-end compressor is greater than or equal to the frequency threshold, the valve core opening degrees of the front-end control valve and the rear-end control valve are changed to be the fourth preset opening degree, and the fourth preset opening degree is 1/8-1/4 of the total opening degree, so that large noise elimination quantity is obtained, and high-frequency transmission sound is eliminated. And if the frequency of the noise of the rear-end compressor is smaller than the frequency threshold value, the noise is judged to be low frequency, the opening degree of the valve core of the front-end control valve is kept unchanged (namely, the valve core is still the second preset opening degree), the opening degree of the valve core of the rear-end control valve is the third preset opening degree, and the third preset opening degree is zero, so that the silencing pipeline becomes a blind pipe, sound wave reflection is realized through sudden change of a blind pipe medium, and transmission sound transmission is reduced.
According to yet another aspect of the present invention, a computer-readable storage medium is provided, on which a computer program is stored, which, when being executed by a processor, implements the sound damping control method according to any one of the above-mentioned technical solutions.
The computer-readable storage medium provided by the present invention, when being executed by a processor, implements the steps of the noise cancellation control method according to any one of the above technical solutions, and therefore, the computer-readable storage medium includes all the beneficial effects of the noise cancellation control method according to any one of the above technical solutions.
Additional aspects and advantages of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention.
Drawings
The above and/or additional aspects and advantages of the present invention will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings of which:
fig. 1 shows a schematic block diagram of a muffler device of a first embodiment of the present invention;
fig. 2 shows a schematic view of a muffler device according to a second embodiment of the present invention;
fig. 3 shows a schematic view of a muffler device according to a third embodiment of the present invention;
fig. 4 shows a schematic view of a muffler device according to a fourth embodiment of the present invention;
FIG. 5 shows a schematic block diagram of an air conditioner of an embodiment of the present invention;
fig. 6 is a schematic structural view showing an air conditioner according to an embodiment of the present invention;
fig. 7 is a schematic structural view showing an air conditioner according to an embodiment of the present invention;
fig. 8 is a schematic structural view showing an air conditioner according to an embodiment of the present invention;
fig. 9 is a schematic structural view showing an air conditioner according to an embodiment of the present invention;
fig. 10 is a schematic structural view showing an air conditioner according to an embodiment of the present invention;
fig. 11 is a schematic structural view showing an air conditioner according to an embodiment of the present invention;
fig. 12 is a flow rate diagram showing a sound damping control method of the first embodiment of the invention;
fig. 13 is a flow rate diagram showing a sound damping control method according to a second embodiment of the present invention;
fig. 14 is a flow rate diagram showing a sound damping control method of the third embodiment of the invention;
FIG. 15 shows a flow diagram of a muffling control method of an embodiment of the present invention;
fig. 16 is a waveform diagram showing the amount of noise reduction of the cross-sectional area corresponding to each opening degree of the flow control valve according to the embodiment of the present invention.
Wherein, the correspondence between the reference numbers and the part names in fig. 1 to 11 is:
102, 104, 1042, first pressure sensor, 106, second flow control valve, 1062, second pressure sensor, 108, first connection pipe, 110, second connection pipe, 302, compressor, 304 reservoir, 306, four-way reversing valve, 308, outdoor heat exchanger, 310 throttling assembly, 312, indoor heat exchanger, 314 muffler, 3142 interference muffler pipe, 3144, first flow control valve, 3146, second flow control valve, 3148 tee, 316 middle partition, 318 high pressure valve assembly, 320, high pressure valve, 322, base 324, 326 valve mounting plate, 328, low pressure valve pipe, 330, 332 reservoir interface, 334 valve cold pipe, 336 outdoor heat exchanger interface, 338, 340, compressor exhaust interface.
Detailed Description
In order that the above objects, features and advantages of the present invention can be more clearly understood, a more particular description of the invention will be rendered by reference to the appended drawings. It should be noted that the embodiments of the present invention and features of the embodiments may be combined with each other without conflict.
In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention, however, the present invention may be practiced in other ways than those specifically described herein, and therefore the scope of the present invention is not limited to the specific embodiments disclosed below.
In an embodiment of the first aspect of the present invention, a muffler device is provided, which is suitable for an air conditioner including a refrigerant pipeline and a compressor, and fig. 1 shows a schematic block diagram of a muffler device 100 according to a first embodiment of the present invention. Wherein, this noise eliminator 100 includes:
the two ends of the silencing pipeline 102 are both connected with the refrigerant pipeline, and the length of the silencing pipeline 102 is an odd multiple of the half wavelength of the noise sound wave of the compressor.
In this embodiment, the muffling pipeline 102 is disposed on the pipeline through which the refrigerant flows from the outdoor unit to the indoor unit, so that the noise of the compressor flows in the refrigerant pipeline along with a portion of the refrigerant flowing out of the compressor, and a portion of the noise enters the muffling pipeline from one end of the muffling pipeline 102, while the portion of the noise of the compressor flowing through the refrigerant pipeline can branch into the muffling pipeline 102 through the other end of the muffling pipeline 102, and two sound waves meet each other in the muffling pipeline. Because the length of the silencing pipeline 102 is odd times of the half wavelength of the noise sound wave of the compressor, the phases of the two sound waves are opposite, so that the sound energy in the silencing pipeline is greatly reduced, the pulsation noise of the compressor transmitted to the indoor unit is reduced, and the use comfort of the indoor unit is prevented from being influenced.
Fig. 2 shows a schematic view of a muffler device according to a second embodiment of the present invention. Wherein, this noise eliminator includes:
the two ends of the silencing pipeline 102 are both connected with the refrigerant pipeline, and the length of the silencing pipeline 102 is an odd multiple of the half wavelength of the noise sound wave of the compressor;
the first flow control valve 104 is arranged on the muffling pipeline 102 and is close to the first end of the muffling pipeline 102, and the first end is one end, close to the compressor, of two ends of the muffling pipeline 102;
the second flow control valve 106 is disposed on the muffling pipeline 102, and is close to the second end of the muffling pipeline 102, where the second end is the other end of the two ends of the muffling pipeline 102 except the first end, the first flow control valve 104 controls the flow of the refrigerant flowing into the first end of the muffling pipeline 102 from the refrigerant pipeline, and the second flow control valve 106 controls the flow of the refrigerant flowing into the second end of the muffling pipeline 102 from the refrigerant pipeline.
In this embodiment, two flow control valves are disposed on the muffling pipeline 102, and are respectively disposed at two ends of the muffling pipeline 102, and the opening degrees of the two flow control valves are controlled to respectively control the flow rates of the refrigerant flowing into the two ends of the muffling pipeline 102, that is, the size of the cross-sectional area of the muffling pipeline 102 is controlled, so as to adjust the muffling amount and the muffling frequency, and meet the muffling requirements for high-frequency and low-frequency noise.
Fig. 3 shows a schematic view of a muffler device according to a third embodiment of the present invention. Wherein, this noise eliminator includes:
the two ends of the silencing pipeline 102 are both connected with the refrigerant pipeline, and the length of the silencing pipeline 102 is an odd multiple of the half wavelength of the noise sound wave of the compressor;
the first flow control valve 104 is arranged on the muffling pipeline 102 and is close to the first end of the muffling pipeline 102, and the first end is one end, close to the compressor, of two ends of the muffling pipeline 102;
the second flow control valve 106 is arranged on the silencing pipeline 102, and is close to the second end of the silencing pipeline 102, and the second end is the other end of the two ends of the silencing pipeline 102 except the first end;
the first flow control valve 104 is provided with a first pressure sensor 1042;
the second flow control valve 106 is provided with a second pressure sensor 1062, wherein the first flow control valve 104 controls the flow rate of the refrigerant flowing from the refrigerant pipeline into the first end of the muffler pipeline 102, the second flow control valve 106 controls the flow rate of the refrigerant flowing from the refrigerant pipeline into the second end of the muffler pipeline 102, the first pressure sensor 1042 detects the pressure pulsation of the refrigerant flowing from the refrigerant pipeline into the first end, and the second pressure sensor 1062 detects the pressure pulsation of the refrigerant flowing from the refrigerant pipeline into the second end.
In this embodiment, the flow control valve is provided with a pressure sensor, and the pressure sensor detects pressure pulsation of the refrigerant flowing into the two ends of the muffling pipeline 102, so as to determine the frequency of the compressor noise according to the pressure pulsation of the refrigerant, and thus, the opening degree of the flow control valve is controlled according to the frequency of the compressor noise, so as to achieve muffling of sound waves with different frequencies.
Fig. 4 shows a schematic view of a muffler device according to a fourth embodiment of the present invention. Wherein, this noise eliminator includes:
the two ends of the silencing pipeline 102 are both connected with the refrigerant pipeline, and the length of the silencing pipeline 102 is an odd multiple of the half wavelength of the noise sound wave of the compressor;
the first flow control valve 104 is arranged on the muffling pipeline 102 and is close to the first end of the muffling pipeline 102, and the first end is one end, close to the compressor, of two ends of the muffling pipeline 102;
the second flow control valve 106 is arranged on the silencing pipeline 102, and is close to the second end of the silencing pipeline 102, and the second end is the other end of the two ends of the silencing pipeline 102 except the first end;
the first connecting pipe 108, the first connecting pipe 108 is connected with the first ends of the refrigerant pipeline and the silencing pipeline;
the second connecting pipe 110, the second connecting pipe 110 is connected with the second end of the refrigerant pipeline and the silencing pipeline;
the first flow control valve 104 is provided with a first pressure sensor 1042;
the second flow control valve 106 is provided with a second pressure sensor 1062, wherein the first flow control valve 104 controls the flow rate of the refrigerant flowing from the refrigerant pipeline into the first end of the muffler pipeline 102, the second flow control valve 106 controls the flow rate of the refrigerant flowing from the refrigerant pipeline into the second end of the muffler pipeline 102, the first pressure sensor 1042 detects the pressure pulsation of the refrigerant flowing from the refrigerant pipeline into the first end, and the second pressure sensor 1062 detects the pressure pulsation of the refrigerant flowing from the refrigerant pipeline into the second end.
In this embodiment, the first connecting pipe 108 and the second connecting pipe 110 are three-way pipes, and two joints of the three-way pipes are connected to the refrigerant pipeline, and the other joint is connected to the muffling pipeline 102, so as to achieve a firm connection between the muffling pipeline 102 and the refrigerant pipeline.
In any of the above embodiments, the refrigerant line includes one or a combination of: the air conditioner comprises an exhaust pipe, a low-pressure valve pipe and an air return pipe, wherein the exhaust pipe is arranged between a reversing valve and a compressor of the air conditioner, the low-pressure valve pipe is arranged between the low-pressure valve and the reversing valve of the air conditioner, and the air return pipe is arranged between a liquid storage device and the reversing valve of the compressor of the air conditioner.
In this embodiment, the muffling pipeline 102 may be located between the outdoor unit and the indoor units according to the muffling requirement of the indoor compressor for transmitting sound during the cooling or heating operation of the air conditioner. The muffling pipeline 102 can be connected to an exhaust pipe, a low-pressure valve pipe or a muffler, for example, the muffling pipeline 102 can be located on the exhaust pipe or the low-pressure valve pipe under the heating working condition of the air conditioner, and the muffling pipeline 102 can be located on the muffler under the cooling working condition of the air conditioner, so that the muffling requirements under different working conditions are met, and the muffling effect is improved. In addition, the two flow control valves are not limited to be located on the same pipeline, and two ends of the muffling pipeline 102 are not limited to be connected to the same pipeline, for example, one end of the muffling pipeline 102 is connected to the exhaust pipe and the other end is connected to the low-pressure valve pipe, or one end of the muffling pipeline 102 is connected to the exhaust pipe and the other end is connected to the muffler pipe.
In any of the embodiments described above, the cross-sectional diameter of muffler pipe 102 ranges from 6.45 mm to 12 mm.
In this embodiment, the cross-sectional diameter of the muffling line 102 ranges from 6.45 mm to 12 mm, i.e., the cross-sectional area of the muffling line 102 can be varied to meet the muffling requirements for high and low frequency noise.
In a second aspect of the present invention, an air conditioner is provided, and fig. 5 shows a schematic block diagram of an air conditioner 200 according to an embodiment of the present invention. Wherein, this air conditioner 200 includes:
a compressor 202;
a refrigerant line 204; and
a muffler assembly 100 according to any of the embodiments described above.
In this embodiment, the air conditioner includes a compressor 202, a refrigerant pipeline 204 and a muffler device 100, and both ends of the muffler device 100 are connected to the refrigerant pipeline 204, so that the pulsation noise of the compressor transmitted to the indoor unit is reduced by the muffler device 100, and the comfort of the indoor unit is prevented from being affected.
Fig. 6 to 11 are schematic structural views illustrating an air conditioner according to an embodiment of the present invention, and the muffling apparatus of fig. 6 to 11 is connected to a low pressure valve pipe.
As shown in fig. 6, the air conditioner includes: the air conditioner comprises a compressor 302, an accumulator 304, a four-way reversing valve 306, an outdoor heat exchanger 308, a throttling assembly 310, an indoor heat exchanger 312 and a silencing device 314, wherein the silencing device 314 comprises an interference silencing pipe 3142, a first flow control valve 3144 and a second flow control valve 3146. In the heating condition, the first flow control valve 3144 is a front end control valve (i.e., the refrigerant flows through the first flow control valve 3144 before the second flow control valve 3146), and the refrigerant flows to the accumulator 304, the compressor 302, the four-way reversing valve 306, the muffler 314, the indoor heat exchanger 312, the throttle assembly 310, and the outdoor heat exchanger 308. In the cooling mode, the second flow control valve 3146 is a front end control valve (i.e., the refrigerant flows through the second flow control valve 3146 before the first flow control valve 3144), and the refrigerant flows to the accumulator 304, the compressor 302, the four-way reversing valve 306, the outdoor heat exchanger 308, the throttle assembly 310, the indoor heat exchanger 312, and the muffler 314.
As shown in fig. 7, 8 and 9 (wherein fig. 8 is a view from direction a of fig. 7, and fig. 9 is a view from direction B of fig. 7), the air conditioner includes: compressor 302, accumulator 304, four-way reversing valve 306, outdoor heat exchanger 308, interference muffler 3142, first flow control valve 3144, second flow control valve 3146, tee 3148, mid-diaphragm 316, high pressure valve assembly 318, high pressure valve 320, low pressure valve 322, base plate 324, valve mounting plate 326.
As shown in fig. 10 and 11, the air conditioner includes: interference muffling pipe 3142, first flow control valve 3144, second flow control valve 3146, tee 3148, four-way reversing valve 306, low pressure valve 322, low pressure valve pipe 328, return air pipe 330, reservoir interface 332, valve cooling pipe 334, outdoor heat exchanger interface 336, exhaust pipe 338, compressor exhaust interface 340.
In some embodiments, the muffler 314 includes an interference muffling pipe 3142, a first flow control valve 3144 and a second flow control valve 3146 at two ends of the muffling pipe, and a three-way pipe 3148 for connecting the interference muffling pipe 3142 to a main pipeline (a refrigerant flow pipeline), wherein the opening degree of the flow control valve is feedback controlled by the frequency of the indoor unit detecting the noise transmitted by the compressor.
In some embodiments, the length of the interference muffling pipe 3142 is the length of the pipeline between the two three-way pipes passing through the flow control valve, the length of the main pipeline is the length of the pipeline between the two three-way pipes, and in order to satisfy the muffling principle of interference muffling (the sound waves of the two pipelines meet and interfere with each other to cause the sound energy to be weakened), the length of the interference muffling pipe 3142 is the sum of the length of the main pipeline and the odd number times of half wavelength of the muffled sound waves.
In some embodiments, the muffling device 314 may be located between the outdoor unit and the indoor unit according to the sound transmission requirement of the indoor compressor in the cooling or heating operation of the air conditioner, the exhaust pipe 338 and the low pressure valve pipe 328 of the outdoor unit may be selected for the heating operation, the return pipe 330 may be selected for the cooling operation, and the two flow control valves are not limited to being located on the same pipe.
In some embodiments, the flow control valve can feed back the corresponding opening of the flow control valve through indoor detection noise frequency to meet the noise elimination requirement and the noise elimination frequency of different frequencies.
In an embodiment of the third aspect of the present invention, a sound damping control method is provided, which is applied to the sound damping device according to any one of the embodiments described above, and fig. 12 shows a flow rate diagram of the sound damping control method according to the first embodiment of the present invention. The noise elimination control method comprises the following steps:
step 402, controlling the noise elimination pipeline of the noise elimination device to be conducted, so that the refrigerant in the refrigerant pipeline flows into the noise elimination pipeline from two ends of the noise elimination pipeline respectively, and eliminating the noise of the compressor driven by the refrigerant.
In this embodiment, the noise elimination pipeline is controlled to be conducted, so that part of the noise of the compressor flows in the refrigerant pipeline along with the refrigerant flowing out of the compressor, part of the noise enters the noise elimination pipeline from one end of the noise elimination pipeline and flows in the noise elimination pipeline, the part of the noise of the compressor flowing through the refrigerant pipeline can branch into the noise elimination pipeline through the other end of the noise elimination pipeline, and the two sound waves meet in the noise elimination pipeline. Because the length of the silencing pipeline is odd times of the half wavelength of the noise sound wave of the compressor, the phases of the two sound waves are opposite, so that the sound energy in the silencing pipeline is greatly reduced, the pulsation noise of the compressor transmitted to the indoor unit is reduced, and the use comfort of the indoor unit is prevented from being influenced.
In this embodiment, two flow control valves are arranged on the muffling pipeline and are respectively arranged at two ends of the muffling pipeline, and the muffling pipeline is conducted by controlling the two flow control valves to be opened.
In any of the above embodiments, further comprising: and in the process of conducting the silencing pipeline, acquiring the frequency of the noise of the compressor, and controlling the opening of the first flow control valve of the silencing device and the opening of the second flow control valve of the silencing device according to the frequency of the noise of the compressor.
Fig. 13 shows a flow rate diagram of a sound damping control method of the second embodiment of the present invention. The noise elimination control method comprises the following steps:
and step 504, acquiring the frequency of the noise of the compressor in the process of conducting the noise elimination pipeline, and controlling the opening of the first flow control valve of the noise elimination device and the opening of the second flow control valve of the noise elimination device according to the frequency of the noise of the compressor.
In the technical scheme, the pressure pulsation of the refrigerant flowing into the silencing pipeline is obtained, so that the frequency of the noise of the compressor is determined according to the pressure pulsation of the refrigerant, the size of the cross section area of the silencing pipeline is controlled by controlling the opening degrees of the two flow control valves, the silencing quantity and the silencing frequency are adjusted, and the silencing requirements for high-frequency and low-frequency noise are met.
Fig. 14 shows a flow rate diagram of a sound damping control method of the third embodiment of the invention. The noise elimination control method comprises the following steps:
and step 618, controlling the opening degrees of the front-end control valve and the rear-end control valve to be fourth preset opening degrees, wherein the fourth preset opening degree is smaller than the second preset opening degree and larger than the third preset opening degree.
In this embodiment, when the air conditioner is in the heating mode, the refrigerant flowing out of the compressor first enters the indoor heat exchanger and then enters the outdoor heat exchanger, and the refrigerant first flows into the noise elimination pipeline through the first flow control valve close to the compressor, so the first flow control valve close to the compressor is set as a front end control valve, and the second flow control valve far from the compressor is set as a rear end control valve, or when the air conditioner is in the cooling mode, the refrigerant flowing out of the compressor first enters the outdoor heat exchanger and then enters the indoor heat exchanger, and the refrigerant first flows into the noise elimination pipeline through the second flow control valve far from the compressor, so the second flow control valve far from the compressor is set as a front end control valve, and the first flow control valve close to the compressor is set as a rear end control valve. The noise control method comprises the steps of calculating the frequency of noise of a front-end compressor according to refrigerant pressure pulsation detected by a pressure sensor of a front-end control valve, calculating the frequency of noise of a rear-end compressor according to refrigerant pressure pulsation detected by a pressure sensor of the rear-end control valve, wherein the noise of the front-end compressor is the noise of the position of a first flow control valve in a heating mode, the noise of the rear-end compressor is the noise of the position of a second flow control valve in a cooling mode, the noise of the front-end compressor is the noise of the position of the second flow control valve in the cooling mode, the noise of the rear-end compressor is the noise of the position of the first flow control valve, and the valve core opening degrees of the first flow control valve and the second flow control valve are controlled according to the frequency of the noise of the front-end compressor and the frequency of the noise of the rear-end compressor.
Specifically, as shown in fig. 15, it is determined that the current evaporator temperature defines that the control valve is the front end control valve, that is, the current operating condition of the air conditioner is determined according to the current evaporator temperature, the first flow control valve is the front end control valve in the heating operating condition, and the second flow control valve is the front end control valve in the cooling operating condition. The pressure pulsation of the refrigerant flowing in is detected through a pressure pulsation sensor arranged in the front-end control valve, the peak frequency f1 and the frequency threshold f0(f0 is 500Hz) of the noise of the front-end compressor are judged, if the peak frequency f1 of the noise of the front-end compressor is smaller than the frequency threshold f0, the noise is judged to be low frequency, the front-end control valve and the rear-end control valve are opened, the opening degrees of valve cores of the front-end control valve and the rear-end control valve are kept to be the total opening degree, so that sound waves flowing through the noise elimination pipeline and the refrigerant pipeline are mutually interfered at the rear-end convergence part, and the transmission of low-frequency transmission sound is reduced. If the peak frequency f1 of the noise of the front-end compressor is larger than or equal to the frequency threshold value f0, the front-end control valve and the rear-end control valve are opened, the valve core opening degrees of the front-end control valve and the rear-end control valve are kept at 1/2 of the total opening degree, the peak frequency f2 and the frequency threshold value f0 of the noise of the rear-end compressor are judged, if the peak frequency f2 of the noise of the rear-end compressor is larger than or equal to the frequency threshold value f0, the valve core opening degrees of the front-end control valve and the rear-end control valve are changed to 1/8-1/4 of the total opening degree, large noise elimination quantity is obtained, and high-frequency transmission sound is eliminated. And if the peak frequency f2 of the noise of the rear-end compressor is smaller than the frequency threshold value f0, the noise is judged to be low frequency, the opening degree of the valve core of the front-end control valve is kept unchanged, the opening degree of the valve core of the rear-end control valve is zero, the silencing pipeline becomes a blind pipe, sound wave reflection is realized through sudden change of a blind pipe medium, and transmission sound transmission is reduced.
Fig. 16 is a waveform diagram showing the muffling amount of the cross-sectional area corresponding to each opening of the flow control valve according to the embodiment of the present invention, where the waveform E is that the opening of the flow control valve is total opening 1/2, and a muffling amount in a wider frequency band is obtained, which has a better muffling effect for low-frequency noise. As the opening degree decreases to the total opening degree 1/4 (waveform D), it has a larger amount of muffling in the high frequency band, and has a better muffling effect for the high frequency. As the opening degree continues to decrease to the total opening degree 1/8 (waveform C), the high-frequency effective noise cancellation amount thereof further increases.
An embodiment of the fourth aspect of the present invention provides a computer-readable storage medium, on which a computer program is stored, which, when executed by a processor, implements the sound-deadening control method according to any one of the above-mentioned embodiments.
The present invention provides a computer-readable storage medium, which when executed by a processor implements the steps of the sound emission control method according to any one of the above embodiments, and therefore includes all the advantageous effects of the sound emission control method according to any one of the above embodiments.
In the description herein, the terms "first" and "second" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance unless explicitly stated or limited otherwise; the terms "connected," "mounted," "secured," and the like are to be construed broadly and include, for example, fixed connections, removable connections, or integral connections; may be directly connected or indirectly connected through an intermediate. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
In the description herein, the description of the terms "one embodiment," "some embodiments," "specific embodiments," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.
The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (12)
1. The utility model provides a noise eliminator, its characterized in that is applicable to the air conditioner, the air conditioner includes refrigerant pipeline and compressor, noise eliminator includes:
the two ends of the silencing pipeline are connected with the refrigerant pipeline, and the length of the silencing pipeline is odd times of the half wavelength of the noise sound wave of the compressor;
the first flow control valve is arranged on the silencing pipeline and is close to the first end of the silencing pipeline, and the first end is one end, close to the compressor, of two ends of the silencing pipeline;
the second flow control valve is arranged on the silencing pipeline and is close to the second end of the silencing pipeline, the second end is the other end of the two ends of the silencing pipeline except the first end,
the first flow control valve controls the flow of the refrigerant flowing into the first end of the sound attenuation pipeline from the refrigerant pipeline, and the second flow control valve controls the flow of the refrigerant flowing into the second end of the sound attenuation pipeline from the refrigerant pipeline.
2. The muffling device of claim 1,
the first flow control valve is provided with a first pressure sensor;
the second flow control valve is provided with a second pressure sensor,
the first pressure sensor detects pressure pulsation of refrigerant flowing from the refrigerant pipeline into the first end, and the second pressure sensor detects pressure pulsation of refrigerant flowing from the refrigerant pipeline into the second end.
3. The muffling device of claim 1, further comprising:
the first connecting pipe is connected with the first ends of the refrigerant pipeline and the silencing pipeline;
and the second connecting pipe is connected with the second ends of the refrigerant pipeline and the silencing pipeline.
4. A sound-damping arrangement according to any one of claims 1 to 3,
the refrigerant pipeline comprises one or the combination of the following components: blast pipe, low pressure valve pipe, muffler, the blast pipe set up in the switching-over valve of air conditioner with between the compressor, the low pressure valve pipe set up in the low pressure valve of air conditioner with between the switching-over valve, the muffler set up in the compressor reservoir of air conditioner with between the switching-over valve.
5. A sound-damping arrangement according to any one of claims 1 to 3,
the numerical range of the section diameter of the silencing pipeline is 6.45 mm to 12 mm.
6. An air conditioner, comprising:
a compressor;
a refrigerant pipeline; and
a sound damping device as claimed in any one of claims 1 to 5.
7. A sound damping control method applied to a sound damping device according to any one of claims 1 to 5, the sound damping control method comprising:
controlling the noise elimination pipeline of the noise elimination device to be conducted, so that the refrigerant in the refrigerant pipeline flows into the noise elimination pipeline from two ends of the noise elimination pipeline respectively, and eliminating the noise of the compressor driven by the refrigerant;
the method comprises the following steps of controlling the conduction of a silencing pipeline of the silencing device, and specifically comprises the following steps:
and controlling a first flow control valve of the muffler device to open and a second flow control valve of the muffler device to open.
8. The sound-damping control method according to claim 7, further comprising:
and in the process of conducting the silencing pipeline, acquiring the frequency of the noise of the compressor, and controlling the opening of a first flow control valve of the silencing device and the opening of a second flow control valve of the silencing device according to the frequency of the noise of the compressor.
9. The sound attenuation control method according to claim 8, wherein the step of acquiring a frequency of the noise of the compressor and controlling the opening degree of the first flow control valve of the sound attenuation device and the opening degree of the second flow control valve of the sound attenuation device according to the frequency of the noise of the compressor specifically includes:
when the air conditioner is in a heating mode, the first flow control valve is set as a front end control valve, and the second flow control valve is set as a rear end control valve, or when the air conditioner is in a cooling mode, the second flow control valve is set as a front end control valve, and the first flow control valve is set as a rear end control valve;
and calculating the frequency of the noise of the front-end compressor according to the refrigerant pressure pulsation detected by the pressure sensor of the front-end control valve, and controlling the opening of the front-end control valve and the opening of the rear-end control valve according to the frequency of the noise of the front-end compressor.
10. The sound attenuation control method according to claim 9, wherein the step of controlling the opening degree of the front end control valve and the opening degree of the rear end control valve in accordance with the frequency of the noise of the front end compressor specifically includes:
judging whether the frequency of the noise of the front-end compressor is smaller than a frequency threshold value;
when the frequency of the noise of the front-end compressor is judged to be smaller than the frequency threshold value, controlling the opening degree of the front-end control valve and the opening degree of the rear-end control valve to be first preset opening degrees;
and when the frequency of the noise of the front-end compressor is judged to be greater than or equal to the frequency threshold value, controlling the opening of the front-end control valve and the opening of the rear-end control valve to be second preset openings, calculating the noise of the rear-end compressor according to the refrigerant pressure pulsation detected by a pressure sensor of the rear-end control valve, and controlling the opening of the front-end control valve and the opening of the rear-end control valve according to the frequency of the noise of the rear-end compressor, wherein the second preset opening is smaller than the first preset opening.
11. The sound attenuation control method according to claim 10, wherein the step of controlling the opening degree of the front end control valve and the opening degree of the rear end control valve in accordance with the frequency of the noise of the rear end compressor specifically includes:
judging whether the frequency of the noise of the rear-end compressor is smaller than the frequency threshold value;
when the frequency of the noise of the rear-end compressor is judged to be smaller than the frequency threshold value, controlling the opening degree of the front-end control valve to be kept at the second preset opening degree, and controlling the opening degree of the rear-end control valve to be a third preset opening degree, wherein the third preset opening degree is smaller than the second preset opening degree;
and when the frequency of the noise of the rear-end compressor is judged to be greater than or equal to the frequency threshold value, controlling the opening degree of the front-end control valve and the opening degree of the rear-end control valve to be fourth preset opening degrees, wherein the fourth preset opening degree is smaller than the second preset opening degree and larger than the third preset opening degree.
12. A computer-readable storage medium, on which a computer program is stored, which, when being executed by a processor, implements the sound damping control method according to any one of claims 7 to 11.
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| CN112460785B (en) * | 2020-10-26 | 2022-07-26 | 珠海格力节能环保制冷技术研究中心有限公司 | Air conditioner pipeline noise elimination method and system and air conditioner |
| CN114440395B (en) * | 2022-02-24 | 2023-10-27 | 海信空调有限公司 | Air conditioner noise reduction control method and device, air conditioner and storage medium |
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| WO2008030060A1 (en) * | 2006-09-07 | 2008-03-13 | Ls Cable Ltd. | A refrigerator with noise reduction structure using inverse phase sound wave |
| KR101232821B1 (en) * | 2012-09-28 | 2013-02-13 | 주식회사 화승알앤에이 | A silencer tube of automobile muffler |
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