CN106403348B - Air conditioner and refrigeration control method thereof - Google Patents
Air conditioner and refrigeration control method thereof Download PDFInfo
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- CN106403348B CN106403348B CN201611064532.7A CN201611064532A CN106403348B CN 106403348 B CN106403348 B CN 106403348B CN 201611064532 A CN201611064532 A CN 201611064532A CN 106403348 B CN106403348 B CN 106403348B
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- 238000005057 refrigeration Methods 0.000 title claims abstract description 36
- 238000000034 method Methods 0.000 title claims abstract description 23
- 239000003507 refrigerant Substances 0.000 claims abstract description 120
- 239000007788 liquid Substances 0.000 claims description 28
- 244000241872 Lycium chinense Species 0.000 claims description 19
- 235000015468 Lycium chinense Nutrition 0.000 claims description 19
- 238000001816 cooling Methods 0.000 claims description 11
- 230000005484 gravity Effects 0.000 claims description 4
- 238000007664 blowing Methods 0.000 claims description 3
- 238000006073 displacement reaction Methods 0.000 claims description 3
- 230000009471 action Effects 0.000 claims description 2
- 230000008859 change Effects 0.000 claims description 2
- 229920006395 saturated elastomer Polymers 0.000 claims description 2
- 238000004378 air conditioning Methods 0.000 abstract description 2
- 238000010438 heat treatment Methods 0.000 description 6
- 230000008569 process Effects 0.000 description 4
- 230000001276 controlling effect Effects 0.000 description 3
- 238000005192 partition Methods 0.000 description 3
- 230000001105 regulatory effect Effects 0.000 description 3
- 230000003750 conditioning effect Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000001704 evaporation Methods 0.000 description 2
- 230000008020 evaporation Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 230000005483 Hooke's law Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000002123 temporal effect Effects 0.000 description 1
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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
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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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
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
- F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
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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
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/006—Accumulators
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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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
- F25B49/022—Compressor control 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
- F25B2600/00—Control issues
- F25B2600/02—Compressor control
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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
- F25B2600/00—Control issues
- F25B2600/05—Refrigerant levels
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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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion valves
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Power Engineering (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Air Conditioning Control Device (AREA)
Abstract
The invention relates to the technical field of air conditioning, in particular to an air conditioner and a refrigeration control method thereof. The pipe section between the outdoor heat exchanger and the throttling device of the air conditioner is connected with any bypass branch in parallel, and a first switch valve and a refrigerant storage device are sequentially arranged on each bypass branch along the direction from the outdoor heat exchanger to the throttling device. When the high-pressure value of the refrigerant in the air conditioner is too high, the redundant refrigerant in the refrigeration loop of the air conditioner is stored through the bypass branch, and the pressure of the refrigerant in the refrigeration loop is reduced until the high-pressure value of the refrigerant meets the requirement. Therefore, the air conditioner can be normally refrigerated under high-temperature or even ultra-high-temperature environment, and the problem that the high temperature of a user cannot be refrigerated is effectively solved.
Description
Technical Field
The invention relates to the technical field of air conditioning, in particular to an air conditioner and a refrigeration control method thereof.
Background
The maximum operating temperature of a traditional T3 air conditioner is 52 ℃, and a design margin of 2-3 ℃ is reserved when an air conditioner manufacturer designs the air conditioner, namely, the maximum operating environment temperature of the air conditioner is about 55 ℃. However, even if the product has such a margin, the frequency of failure is still high after the product is installed in the home of a user, and the maintenance rate is high. Especially, the middle east environment is severe, and when the weather forecast atmospheric temperature is about 45 ℃, the temperature of the air exposed outdoors can often reach more than 60 ℃, even between 67 and 68 ℃. In the temperature environment, the conventional T3 air conditioner under the working condition is protected to stop due to high temperature, high voltage and large current, and even is burnt out by high temperature. Therefore, for users, the more the high-temperature environment needs cooling capacity, the more the air conditioner is protected to stop and cannot cool.
Disclosure of Invention
Technical problem to be solved
The purpose of the invention is: the air conditioner and the refrigeration control method thereof are provided to solve the problem that normal refrigeration cannot be performed in a high-temperature environment in the prior art.
(II) technical scheme
In order to solve the above technical problem, the present invention provides an air conditioner, comprising: the compressor, the indoor heat exchanger and the outdoor heat exchanger are connected through pipelines to form a loop, wherein a throttling device is connected between the indoor heat exchanger and the outdoor heat exchanger, any bypass branch is connected in parallel with a pipe section between the outdoor heat exchanger and the throttling device, and a first switch valve and a refrigerant storage device are sequentially arranged on each bypass branch along the direction from the outdoor heat exchanger to the throttling device.
Preferably, the compressor is connected with the indoor heat exchanger and the outdoor heat exchanger through a reversing device; the bypass branch is further provided with a one-way stop valve, so that the first switch valve, the refrigerant storage and the one-way stop valve are sequentially arranged along the direction from the outdoor heat exchanger to the throttling device, and the one-way stop valve is communicated along the direction from the outdoor heat exchanger to the throttling device.
Preferably, the compressor is a double-cylinder variable-capacity compressor, and comprises a large cylinder and a small cylinder; the reversing device is a four-way valve, and the air return port of the large cylinder and the air return port of the small cylinder are respectively connected with the outlet of the four-way valve through a second switch valve.
Preferably, the number of the bypass branches is more than two, and all the bypass branches are connected in parallel and/or in series.
Preferably, the throttling device is a thermal expansion valve or an electronic expansion valve.
The present invention also provides an air conditioner including: the refrigerant storage device comprises a compressor, an indoor heat exchanger and an outdoor heat exchanger which are connected through pipelines to form a loop, wherein a throttling device is connected between the indoor heat exchanger and the outdoor heat exchanger, any bypass branch is connected in parallel with a pipe section between the outdoor heat exchanger and the throttling device, an adjustable refrigerant storage device is connected to each bypass branch, the adjustable refrigerant storage device comprises a vertically placed cylindrical shell and a plug part which is arranged in the cylindrical shell and can reciprocate along the axial direction of the cylindrical shell, the plug part is sealed with the inner side wall of the cylindrical shell, and a liquid storage chamber is formed between the action surface of the plug part and the cylindrical shell; the cylindrical shell is provided with a liquid inlet and a liquid outlet which are communicated with the liquid storage chamber, the liquid inlet is connected with the outdoor heat exchanger, and the liquid outlet is connected with the throttling device; the plug member is connected with an elastic member provided along a moving direction of the plug member, and the elastic member is deformed to adjust the balance of the plug member when the plug member moves under refrigerant pressure so that the volume of the reservoir chamber and the gravity of the refrigerant in the reservoir chamber are changed.
The invention also provides a refrigeration control method of the air conditioner, which comprises the following steps:
s1, starting the compressor, and switching the air conditioner to a refrigeration running mode to enable the refrigerant to enter the throttling device from the outlet of the outdoor heat exchanger;
s2, measuring the high pressure value P of the refrigerant of the air conditionerFruit of Chinese wolfberryAnd is combined with PFruit of Chinese wolfberryAnd PIs provided withBy comparison, wherein PIs provided withEqual to the maximum refrigerant high pressure value allowed when the air conditioner is in a refrigeration state:
if P isFruit of Chinese wolfberry≤PIs provided withIf so, the air conditioner keeps running in the current state;
if P isFruit of Chinese wolfberry＞PIs provided withStoring the refrigerant flowing from the outdoor heat exchanger to the throttling device through the bypass branch until PFruit of Chinese wolfberryNot more than PIs provided withThe air conditioner keeps running in the current state; if P after saturation of the bypass branch storageFruit of Chinese wolfberryIs still greater than PIs provided withThen proceed to S3;
s3, judging the type of the compressor:
if the compressor is a double-cylinder variable-capacity compressor, P is reduced by switching the operation mode of the compressorFruit of Chinese wolfberryUp to PFruit of Chinese wolfberryNot more than PIs provided with(ii) a Or if the double-cylinder variable-capacity compressor is in a small-cylinder running state, PFruit of Chinese wolfberryIs still greater than PIs provided withSwitching the air conditioner to an air supply mode;
if the compressor is a single-cylinder compressor, the air conditioner is directly switched to the air supply mode.
Preferably, the method further comprises the following steps: s4, the throttle device automatically adjusts the opening degree by judging the return air superheat degree of the compressor, so that the air conditioner is always in the optimal running state;
when the throttling device is an electronic expansion valve, the method comprises the following steps:
s401, measuring actual air suction temperature T of compressorsThe actual suction temperature T of the compressorsWith set suction temperature T of the compressor0Calculating the superheat degree delta T ═ T of return air of the compressor by taking the differences-T0；
S402, judging the size of delta T:
if delta T is less than-1, reducing the opening of the electronic expansion valve;
if delta T is larger than 1, the opening of the electronic expansion valve is increased;
if delta T is more than or equal to-1 and less than or equal to 1, keeping the opening of the current electronic expansion valve unchanged.
Preferably, in S2, a first switch valve, a refrigerant storage, and a one-way shutoff valve are connected in series in this order on the bypass branch, and the first switch valve is located on the side of the refrigerant storage close to the outdoor heat exchanger, and the one-way shutoff valve is opened in the direction of the throttling device along the outdoor heat exchanger;
when the refrigerant is required to be stored through the bypass branch, the first switching valve is opened so that the refrigerant flows into the refrigerant storage.
Preferably, in S3, if the compressor is a two-cylinder variable capacity compressor, the method includes:
s301, switching the compressor from a double-cylinder running state to a large-cylinder running state, and judging P after running is stableFruit of Chinese wolfberryAnd PIs provided withThe relationship of (1):
if P isFruit of Chinese wolfberry≤PIs provided withThen the air conditioner keeps the current stateOperating the state;
if P isFruit of Chinese wolfberry＞PIs provided withSwitching the compressor from a large-cylinder operation state to a small-cylinder operation state;
s302, in the small cylinder running state, P is judgedFruit of Chinese wolfberryAnd PIs provided withThe relationship of (1):
if P isFruit of Chinese wolfberry≤PIs provided withIf so, the air conditioner keeps running in the current state;
if P isFruit of Chinese wolfberry＞PIs provided withThe air conditioner is switched to the blowing mode.
(III) advantageous effects
The technical scheme of the invention has the following advantages: in the air conditioner, any bypass branch is connected in parallel with the pipe section between the outdoor heat exchanger and the throttling device, and a first switch valve and a refrigerant storage are sequentially arranged on each bypass branch along the direction from the outdoor heat exchanger to the throttling device. When the high-pressure value of the refrigerant in the air conditioner is too high, the redundant refrigerant in the refrigeration loop of the air conditioner is stored through the bypass branch, and the pressure of the refrigerant in the refrigeration loop is reduced until the high-pressure value of the refrigerant meets the requirement. Therefore, the air conditioner can be normally refrigerated under high-temperature or even ultra-high-temperature environment, and the problem that the high temperature of a user cannot be refrigerated is effectively solved.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the drawings without creative efforts.
Fig. 1 is a schematic structural view of an air conditioner according to a first embodiment;
fig. 2 is a schematic structural view of another air conditioner according to the first embodiment;
fig. 3 is a schematic structural view of an air conditioner according to a second embodiment;
FIG. 4 is a schematic view showing the structure of an adjustable refrigerant storage according to the second embodiment;
fig. 5 is a flowchart illustrating a cooling control method of an air conditioner according to a third embodiment;
in the figure: 1. an indoor heat exchanger; 2. an outdoor heat exchanger; 3. a reversing device; 4. a throttling device; 5. a bypass branch; 51. a first on-off valve; 52. a refrigerant reservoir; 521. a cylindrical housing; 522. a plug member; 523. a liquid storage chamber; 524. a liquid inlet; 525. a liquid discharge port; 526. a conditioning chamber; 527. an elastic member; 53. a one-way stop valve; 6. a second on-off valve; 7. a compressor.
Detailed Description
The embodiments of the present invention will be described in further detail with reference to the drawings and examples. The following examples are intended to illustrate the invention but are not intended to limit the scope of the invention.
In the description of the present invention, it should be noted that the terms "center", "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of description and simplicity of description, but do not indicate or imply that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
In the description of the present invention, it is to be noted that, unless otherwise explicitly specified or limited, the terms "connected" and "connected" are to be interpreted broadly, e.g., as being fixed or detachable or integrally connected; can be mechanically or electrically connected; may be directly connected or indirectly connected through an intermediate. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
Example one
Referring to fig. 1, an air conditioner of the first embodiment includes: the heat exchanger comprises a compressor 7, an indoor heat exchanger 1 and an outdoor heat exchanger 2 which are connected through pipelines to form a loop, wherein a throttling device 4 is connected between the indoor heat exchanger 1 and the outdoor heat exchanger 2, any bypass branch 5 is connected in parallel with a pipe section between the outdoor heat exchanger 2 and the throttling device 4, and a first switch valve 51 and a refrigerant storage 52 are sequentially arranged on each bypass branch 5 along the direction from the outdoor heat exchanger 2 to the throttling device 4.
It should be noted that, in the air conditioner of the first embodiment, the bypass branch 5 is provided to adjust the refrigerant in the refrigeration circuit of the air conditioner in the high temperature environment, mainly for achieving normal refrigeration in the high temperature environment. Therefore, the air conditioner of the present embodiment only needs to have a cooling function.
Therefore, although the air conditioner in fig. 1 is provided with the reversing device 3, the reversing device 3 is not necessarily a structure that the air conditioner has, and should not constitute a limitation of the present application. And the reversing device 3 is arranged and used for enabling the air conditioner to also heat by changing the flow direction of the refrigerant on the basis of having a cooling function.
Further, referring to fig. 1, when the air conditioner is refrigerating, the refrigerant passes through the outdoor heat exchanger 2 and then enters the pipe section between the outdoor heat exchanger 2 and the throttling device 4. When the refrigerant has a high pressure PFruit of Chinese wolfberryIs not more than the maximum refrigerant high-pressure value P allowed when the air conditioner is in a refrigeration stateIs provided withThe first switching valve 51 is opened, thereby disconnecting the bypass branch 5. At this time, the refrigerant flows out of the outdoor heat exchanger 2 and flows into the expansion device 4. When the refrigerant has a high pressure PFruit of Chinese wolfberryIs greater than the maximum refrigerant high-pressure value P allowed when the air conditioner is in a refrigeration stateIs provided withAt this time, at least one first on-off valve 51 is turned on, so that at least one bypass branch 5 is connected, and the redundant refrigerant in the refrigeration circuit enters the refrigerant storage 52 until the refrigerant high pressure PFruit of Chinese wolfberryEqual to the maximum refrigerant high pressure value PIs provided with。
Wherein the refrigeration is carried outAgent high pressure PFruit of Chinese wolfberryRefers to the pressure between the outlet of the outdoor heat exchanger 2 and the inlet of the throttling device 4 in the cooling state of the air conditioner. Obviously, the first embodiment is only to use the refrigerant high pressure PFruit of Chinese wolfberryTo determine whether the amount and pressure of refrigerant in the refrigeration circuit meet requirements. Of course, other references with equal judgment may be used to judge the amount and pressure of the refrigerant in the refrigeration circuit and control the on/off of the first on/off valve 51 based on the judgment. Also, hereinafter, the refrigerant high pressure PFruit of Chinese wolfberryBut also in order to make the refrigeration circuit work under specific conditions.
As the compressor 7 is connected to the indoor heat exchanger 1 and the outdoor heat exchanger 2 through the reversing device 3, that is, the structure of the air conditioner illustrated in fig. 1, it can be understood from the above description that the air conditioner can be used for heating in this case. In order to avoid that the refrigerant enters the bypass 5 and is stored during heating, and the refrigerant in the heating circuit is insufficient, a one-way shut-off valve 53 is provided in the bypass 5. The first on-off valve 51, the refrigerant accumulator 52, and the check shutoff valve 53 are sequentially provided along the direction from the outdoor heat exchanger 2 to the expansion device 4, and the check shutoff valve 53 is opened along the direction from the outdoor heat exchanger 2 to the expansion device 4. By providing the one-way shutoff valve 53, the line from the expansion device 4 to the refrigerant storage 52 is shut off, and the bypass branch 5 is shut off during heating, thereby preventing the heating effect from being affected.
Further, in the first embodiment, the compressor 7 is preferably a two-cylinder variable displacement compressor 7, so that the amount of refrigerant in the refrigerant circuit can be controlled in an auxiliary manner by controlling the operation mode of the compressor 7. Among them, it is preferable that the compressor 7 includes a large cylinder and a small cylinder, so that the compressor 7 includes a large cylinder operation mode, a small cylinder operation mode and a double cylinder operation mode. When the high pressure of the refrigerant in the refrigeration circuit can meet the set requirement by the bypass branch 5, the compressor 7 is operated in the two-cylinder operation mode. When the requirement for adjusting the high pressure of the refrigerant in the refrigerant circuit cannot be met through the bypass branch 5, the compressor 7 can be operated in a large-cylinder operation mode or even a small-cylinder operation mode, so that the amount of the refrigerant entering the refrigerant circuit is reduced.
On the basis that the air conditioner is provided with the reversing device 3, the reversing device 3 is preferably a four-way valve. At this time, the return port of the large cylinder and the return port of the small cylinder may be connected to the outlet of the four-way valve through one second switching valve 6, respectively. Thereby controlling the operation mode of the compressor 7 by controlling the on-off of the second switching valve 6.
It should be noted that the phrase "any bypass branch 5 is connected in parallel to the pipe section between the outdoor heat exchanger 2 and the throttling device 4" means that the pipe section and the bypass branch 5 are connected in parallel, but when the number of the bypass branches 5 is large, the bypass branches 5 may be connected in series or in parallel.
For example, as can be seen from fig. 1, the number of the bypass branches 5 is two, and the two bypass branches 5 are connected in parallel, so that the two-stage regulation of the refrigeration circuit can be realized. When one bypass branch 5 is sufficient to bring the refrigerant circuit to equilibrium, it is not necessary to re-conduct the other bypass branch 5. Otherwise, two bypass branches 5 can be opened in sequence. It should be noted that fig. 1 is not intended to limit the present application, and the number of the bypass branches 5 may be one or more than three.
For another example, in fig. 2, a plurality of bypass branches 5 are connected in series, and the bypass branches 5 are connected in parallel to the pipe sections between the outdoor heat exchanger 2 and the throttling device 4. Alternatively, when the number of the bypass branches 5 is more than three, the bypass branches 5 may be connected in series or in parallel, and the illustration is not given here.
It should be noted that the form of the throttling device 4 in the first embodiment is not limited, and for example, an electronic expansion valve or a thermal expansion valve is included in the protection scope of the present application. In the refrigerant accumulator 52 of the first embodiment, any shape of container may be selected as long as it has a storage capacity.
Example two
Referring to fig. 3, the air conditioner of the second embodiment is different from the first embodiment in that the bypass branch 5 is not provided with the first switch valve 51 and the one-way stop valve 53, and the refrigerant storage 52 is in the form of an adjustable refrigerant storage 52. Other structures are the same as those in the first embodiment, and thus are not described herein.
With further reference to fig. 4, the adjustable refrigerant storage 52 includes a vertically placed cylindrical housing 521, and a plug member 522 disposed in the cylindrical housing 521 and capable of reciprocating along the axial direction of the cylindrical housing 521, wherein the plug member 522 is sealed with the inner sidewall of the cylindrical housing 521, and a liquid storage chamber 523 is formed between the acting surface of the plug member 522 and the cylindrical housing 521; a liquid inlet 524 and a liquid inlet and outlet 525 which are communicated with the liquid storage chamber 523 are formed in the cylindrical shell 521, the liquid inlet 524 is connected with the outdoor heat exchanger 2, and the liquid inlet and outlet 525 is connected with the throttling device 4; the plug member 522 is connected to an elastic member 527 provided along a moving direction of the plug member 522, and when the plug member 522 is moved under a refrigerant pressure so that a volume of the reservoir chamber 523 and a gravity of the refrigerant in the reservoir chamber 523 are changed, the elastic member 527 is deformed to adjust a balance of the plug member 522.
It should be noted that the initial position of the plug 522 of the adjustable refrigerant storage 52 is close to the top of the cylindrical housing 521, and the volume of the liquid storage chamber 523 is very small, so that the liquid storage chamber 523 can be regarded as a refrigerant pipe section connected to the air conditioner; even more, the initial position of the plug member 522 may be against the top of the cylindrical housing 521, so that the adjustable refrigerant reservoir 52 may now be seen as an open circuit, so that the entire bypass branch 5 may be seen as an open circuit. Also, when the air conditioner heats up, since the pressure value of the refrigerant flowing out of the throttling means 4 is already very low, it is impossible to move the plug member 522, so that the design of the bypass branch 5 according to the initial position of the plug member 522 can be regarded as a circulation line or an open circuit at this time. That is, the bypass branch 5 in the second embodiment has no influence on the heating of the air conditioner.
Only when the air conditioner is in a cooling mode and the high pressure of the refrigerant is too high, the compression pressure difference is generated between the upper side and the lower side of the plug part 522 of the adjustable refrigerant storage 52, the plug part 522 moves downwards under the pressure of the refrigerant to increase the volume of the liquid storage chamber 523, so that a part of the refrigerant in the cooling circuit is stored in the liquid storage chamber 523, the pressure of the refrigerant in the pipeline of the air conditioner is reduced until the high pressure value of the refrigerant meets the requirement, and the plug part 522 is balanced. Especially, when the air conditioner is placed in a high-temperature or ultra-high-temperature environment for refrigeration, the refrigerant discharged from the outdoor heat exchanger 2 has very high pressure, and the problem that the user cannot refrigerate at high temperature can be effectively solved by storing the refrigerant release pressure in the adjustable refrigerant storage 52. Also, if the high pressure of the refrigerant is too low, the receiver chamber 523 may release a portion of the refrigerant into the air conditioner pipe, on the basis that the receiver chamber 523 stores the refrigerant.
Referring to fig. 4, in the second embodiment, the cylindrical housing 521 includes a top plate and a bottom plate, so that the plug member 522 partitions the inner cavity of the cylindrical housing 521 to form an adjusting chamber 526 and the reservoir 523, and the reservoir 523 is located above the adjusting chamber 526. Therein, it is preferred, but not necessary, to evacuate the regulated chamber 526 to avoid a change in the gas pressure in the regulated chamber 526 during movement of the plug member 522. Alternatively, the adjustment chamber 526 may be vented to atmosphere to ensure that the pressure in the adjustment chamber 526 is stable.
On the basis of the above, the elastic member 527 is preferably located in the conditioning chamber 526. Wherein the elastic member 527 has a bottom end fixed to the bottom plate of the regulation chamber 526 and a top end supporting the plug member 522. Thus, when the refrigerant high pressure is excessive, the plug member 522 moves downward and compresses the elastic member 527 until the refrigerant high pressure meets the set requirement, at which time the plug member 522 reaches equilibrium. Of course, the elastic member 527 may be disposed in the reservoir 523 in a case where it meets a specific requirement, but in this case, not only is the protection of the elastic member 527 unfavorable, but also the adjustment range of the volume of the reservoir 523 is affected.
A spring can be selected as the elastic member 527 in this embodiment two from the drawings. When the plug member 522 is balanced, neglecting air pressure, the force relationship is: mg + V ρ g + F ═ k × s, where mg refers to the gravity of the plug member 522, and is a constant value; a volume corresponding to a portion for storing the refrigerant after a portion for flowing the refrigerant is removed from the liquid storage chamber 523 denoted by V; ρ denotes the density of the refrigerant; f refers to the pressure of the flowing refrigerant against the plug member 522; k is the spring force of the spring obtained by hooke's law, wherein k is the elastic coefficient of the spring, and s is the deformation of the spring.
In a modification of the above formula, V × ρ g — k × s-mg-F is obtained, and since mg is a constant value and when the plug member 522 is balanced, the high-pressure of the flowing refrigerant reaches a set value, and F is also a constant value, V × ρ g — k × s'. Where V ═ a × s', a is the cross-sectional area of cylindrical housing 521. Thus, with the cylindrical housing 521 in place, the spring k can be found to ensure that the adjustable refrigerant reservoir 52 can adjust the refrigerant high pressure in the air conditioner line.
Of course, the elastic member 527 of the second embodiment may also be in other forms other than a spring.
The specific form of the plug member 522 of the second embodiment is not limited by the drawings, and may be in the form of a partition plate shown in fig. 2, or in the form of a plunger or a piston. The partition plate is simple in form and structure, low in manufacturing cost, but poor in sealing performance; in the form of a plunger and a piston, although good in sealing, the manufacturing cost is higher.
In addition, the cross section of the cylindrical housing 521 may be any shape such as a circle, a square, a triangle, etc.
EXAMPLE III
According to the air conditioner of the foregoing embodiment, the third embodiment provides a refrigeration control method of an air conditioner, including the following steps:
s1, starting the compressor 7, and switching the air conditioner to a cooling operation mode to enable the refrigerant to enter the throttling device 4 from the outlet of the outdoor heat exchanger 2;
s2, measuring the high pressure value P of the refrigerant of the air conditionerFruit of Chinese wolfberryAnd is combined with PFruit of Chinese wolfberryAnd PIs provided withBy comparison, wherein PIs provided withEqual to the maximum allowable of the air conditioner in the cooling stateRefrigerant high pressure value:
if P isFruit of Chinese wolfberry≤PIs provided withIf so, the air conditioner keeps running in the current state;
if P isFruit of Chinese wolfberry＞PIs provided withThe refrigerant flowing from the outdoor heat exchanger 2 to the expansion device 4 is stored through the bypass branch 5 until PFruit of Chinese wolfberryNot more than PIs provided withThe air conditioner keeps running in the current state; if P after saturation of the storage of the bypass branch 5Fruit of Chinese wolfberryIs still greater than PIs provided withThen proceed to S3;
s3, determining the type of the compressor 7:
if the compressor 7 is a two-cylinder variable displacement compressor 7, P is reduced by switching the operating mode of the compressor 7Fruit of Chinese wolfberryUp to PFruit of Chinese wolfberryNot more than PIs provided with(ii) a Or P if the double-cylinder variable-capacity compressor 7 is in a small-cylinder operating stateFruit of Chinese wolfberryIs still greater than PIs provided withIf so, switching the air conditioner to an air supply mode;
if the compressor 7 is a single cylinder compressor 7, the air conditioner is directly switched to the air supply mode.
When the number of the bypass branches 5 is multiple, the bypass branches 5 are connected into the refrigeration circuit one by one until the amount of the refrigerant in the refrigeration circuit meets the requirement, or until all the bypass branches 5 are stored and saturated. The storage saturation of the bypass branch 5 refers to a state in which the pressure of the refrigerant storage 52 and the outlet pressure of the outdoor heat exchanger 2, i.e., the high-pressure of the refrigerant, are balanced, and the refrigerant is no longer stored in the refrigerant storage 52 but flows along the bypass branch 5 to the throttling device 4.
It is obvious that the bypass branch 5 may adopt the structural form of the first embodiment, and may also adopt the structural form of the second embodiment.
When the bypass branch 5 of the first embodiment is adopted, a sensor is required to measure the high-pressure P of the refrigerantFruit of Chinese wolfberryThus to PFruit of Chinese wolfberryAnd PIs provided withThe magnitude relation of (2) is judged, and the on-off of the first on-off valve 51 is controlled according to the judgment result. Only at PFruit of Chinese wolfberry＞PIs provided withIn the case of (1), the first switching valve 51 is opened to turn on the bypass branch 5. Obviously, this situation isThe refrigeration control method described below requires a sensor and a control unit although the refrigerant reservoir 52 in the bypass branch 5 is simple in structure.
When the bypass branch 5 of the second embodiment is adopted, it can be operated according to P due to the adjustable refrigerant reservoir 52 of the bypass branch 5Fruit of Chinese wolfberryThe on-off of the bypass branch 5 is controlled, so that a sensor and a control unit are not needed. However, in this case, the structure of the adjustable refrigerant reservoir 52 is relatively complicated.
As can be seen from the above description, the bypass branch 5 has a main regulating effect on the amount of refrigerant in the refrigeration circuit. When all the bypass branches 5 are insufficient so that the refrigerant high pressure is satisfactory, the auxiliary regulation can be performed by switching the operation mode of the compressor 7.
Specifically, if the compressor 7 in S3 is a two-cylinder variable capacity compressor 7, S3 further includes:
s301, switching the compressor 7 from a double-cylinder running state to a large-cylinder running state, and judging P after running is stableFruit of Chinese wolfberryAnd PIs provided withThe relationship of (1):
if P isFruit of Chinese wolfberry≤PIs provided withIf so, the air conditioner keeps running in the current state;
if P isFruit of Chinese wolfberry＞PIs provided withThen, the compressor 7 is switched from the large cylinder operation state to the small cylinder operation state;
s302, in the small cylinder running state, P is judgedFruit of Chinese wolfberryAnd PIs provided withThe relationship of (1):
if P isFruit of Chinese wolfberry≤PIs provided withIf so, the air conditioner keeps running in the current state;
if P isFruit of Chinese wolfberry＞PIs provided withThe air conditioner is switched to the blowing mode.
On the basis, the method of the third embodiment further includes step S4, where the throttle device 4 automatically adjusts the opening degree by judging the superheat degree of the returned air of the compressor 7, so that the air conditioner is always in the optimal operation state.
Obviously, the opening degree adjustment of the throttle device 4 is accompanied with the whole operation process of the air conditioner, which is S4, but does not mean that there is a temporal relationship with S1-S3.
When the expansion device 4 is an electronic expansion valve, the expansion device includes:
s401, measuring actual suction temperature T of compressor 7sThe actual suction temperature T of the compressor 7sWith the set suction temperature T of the compressor 70The difference is calculated to obtain the degree of superheat delta T ═ T of the return air of the compressor 7s-T0；
S402, judging the size of delta T:
if delta T is less than-1, the refrigerant flow of the refrigeration system is too large, the evaporation temperature is lower, and the opening of the electronic expansion valve is reduced by one level;
if delta T is more than 1, the refrigerant flow of the refrigeration system is small, the evaporation temperature is high, and the opening of the electronic expansion valve is increased by one step;
if delta T is more than or equal to-1 and less than or equal to 1, the operation state of the current refrigeration system is better, and the opening of the current electronic expansion valve is kept unchanged.
In this case, an execution period T may be set so that the degree of superheat Δ T of return air is determined every time T, and the opening degree of the electronic expansion valve is adjusted according to the determination each time.
Of course, if the throttle device 4 is a thermal expansion valve, it can also adjust its opening degree by judging the superheat of the return air of the compressor 7.
When the number of the bypass branches 5 is two and the compressor 7 is a two-cylinder variable capacity compressor 7, please refer to fig. 5 for the process of the refrigeration control method of the air conditioner. Although not shown in fig. 5, the opening degree adjustment process of the throttle device 4 is performed throughout the entire cooling process. For example, each judgment P in FIG. 5Fruit of Chinese wolfberryAnd PIs provided withBefore the relationship (2) is obtained, the opening degree of the throttle device 4 can be adjusted by determining the degree of superheat Δ T of the returned air of the compressor 7. Of course, the opening degree of the expansion device 4 may be adjusted by determining the degree Δ T of superheat of the returned air of the compressor 7 after each determination of the relationship between real and P.
The above embodiments are merely illustrative of the present invention and are not to be construed as limiting the invention. Although the present invention has been described in detail with reference to the embodiments, it should be understood by those skilled in the art that various combinations, modifications or equivalents may be made to the technical solution of the present invention without departing from the spirit and scope of the technical solution of the present invention, and the technical solution of the present invention is covered by the claims of the present invention.
Claims (5)
1. An air conditioner comprising: the refrigerant storage device comprises a compressor, an indoor heat exchanger and an outdoor heat exchanger which are connected through pipelines to form a loop, wherein a throttling device is connected between the indoor heat exchanger and the outdoor heat exchanger, and the refrigerant storage device is characterized in that a pipe section between the outdoor heat exchanger and the throttling device is connected in parallel with a plurality of bypass branches, each bypass branch is connected with an adjustable refrigerant storage device, each adjustable refrigerant storage device comprises a vertically-placed cylindrical shell and a plug part which is arranged in the cylindrical shell and can reciprocate along the axial direction of the cylindrical shell, the plug part is sealed with the inner side wall of the cylindrical shell, and a liquid storage chamber is formed between the action surface of the plug part and the cylindrical shell; the cylindrical shell is provided with a liquid inlet and a liquid outlet which are communicated with the liquid storage chamber, the liquid inlet is connected with the outdoor heat exchanger, and the liquid outlet is connected with the throttling device; the plug member is connected with an elastic member arranged along the moving direction of the plug member, and when the plug member moves under the pressure of the refrigerant to change the volume of the liquid storage chamber and the gravity of the refrigerant in the liquid storage chamber, the elastic member deforms to adjust the balance of the plug member; the initial position of the plug part is propped against the top of the cylindrical shell, at the moment, the adjustable refrigerant storage is an open circuit, and the compressor is a double-cylinder variable-capacity compressor and comprises a large cylinder and a small cylinder.
2. A cooling control method of an air conditioner according to claim 1, comprising the steps of:
s1, starting the compressor, and switching the air conditioner to a refrigeration running mode to enable the refrigerant to enter the throttling device from the outlet of the outdoor heat exchanger;
s2, measuring the high pressure value P of the refrigerant of the air conditionerFruit of Chinese wolfberryAnd is combined with PFruit of Chinese wolfberryAnd PIs provided withBy comparison, wherein PIs provided withEqual to the maximum refrigerant high pressure value allowed when the air conditioner is in a refrigeration state:
if P isFruit of Chinese wolfberry≤PIs provided withIf so, the air conditioner keeps running in the current state;
if P isFruit of Chinese wolfberry＞PIs provided withStoring the refrigerant flowing from the outdoor heat exchanger to the throttling device through the bypass branch until PFruit of Chinese wolfberryNot more than PIs provided withThe air conditioner keeps running in the current state; if the bypass branch is saturated with PFruit of Chinese wolfberryIs still greater than PIs provided withThen proceed to S3;
s3, judging the type of the compressor:
if the compressor is a double-cylinder variable-capacity compressor, P is reduced by switching the operation mode of the compressorFruit of Chinese wolfberryUp to PFruit of Chinese wolfberryNot more than PIs provided with(ii) a Or if the double-cylinder variable-capacity compressor is in a small-cylinder running state, PFruit of Chinese wolfberryIs still greater than PIs provided withSwitching the air conditioner to an air supply mode;
if the compressor is a single-cylinder compressor, the air conditioner is directly switched to the air supply mode.
3. The method of claim 2, further comprising: s4, the throttle device automatically adjusts the opening degree by judging the return air superheat degree of the compressor, so that the air conditioner is always in the optimal running state;
when the throttling device is an electronic expansion valve, the throttling device comprises:
s401, measuring actual suction temperature T of compressorsThe actual suction temperature T of the compressorsWith set suction temperature T of the compressor0Calculating the superheat degree delta T ═ T of return air of the compressor by taking the differences-T0；
S402, judging the size of delta T:
if delta T is less than-1, reducing the opening of the electronic expansion valve;
if delta T is larger than 1, the opening of the electronic expansion valve is increased;
if delta T is more than or equal to-1 and less than or equal to 1, keeping the opening of the current electronic expansion valve unchanged.
4. The method according to claim 2, wherein in S2, a first switch valve, a refrigerant storage and a one-way stop valve are connected in series in sequence on a bypass branch, and the first switch valve is located on a side of the refrigerant storage close to the outdoor heat exchanger, and the one-way stop valve is turned on in a direction of the outdoor heat exchanger toward the throttling device;
when the refrigerant is required to be stored through the bypass branch, the first switching valve is opened so that the refrigerant flows into the refrigerant storage.
5. The method of claim 2, wherein in S3, if the compressor is a twin cylinder variable displacement compressor, the method comprises:
s301, switching the compressor from a double-cylinder running state to a large-cylinder running state, and judging P after running is stableFruit of Chinese wolfberryAnd PIs provided withThe relationship of (1):
if P isFruit of Chinese wolfberry≤PIs provided withIf so, the air conditioner keeps running in the current state;
if P isFruit of Chinese wolfberry＞PIs provided withSwitching the compressor from a large-cylinder operation state to a small-cylinder operation state;
s302, in the small cylinder running state, P is judgedFruit of Chinese wolfberryAnd PIs provided withThe relationship of (1):
if P isFruit of Chinese wolfberry≤PIs provided withIf so, the air conditioner keeps running in the current state;
if P isFruit of Chinese wolfberry＞PIs provided withThe air conditioner is switched to the blowing mode.
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| CN201611064532.7A CN106403348B (en) | 2016-11-28 | 2016-11-28 | Air conditioner and refrigeration control method thereof |
| PCT/CN2016/113564 WO2018094841A1 (en) | 2016-11-28 | 2016-12-30 | Air conditioner and refrigeration control method therefor |
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| CN106403413A (en) * | 2016-11-25 | 2017-02-15 | 广州华凌制冷设备有限公司 | Air conditioning system and control method |
| CN107024015A (en) * | 2017-03-27 | 2017-08-08 | 合肥美的电冰箱有限公司 | A kind of refrigerating method of refrigeration system, refrigerator and refrigerator |
| CN106949683B (en) * | 2017-04-27 | 2022-10-21 | 华南理工大学 | Flexible pressure control system for low-temperature refrigeration and cooling of mixed working medium and operation method thereof |
| CN107869864A (en) * | 2017-06-09 | 2018-04-03 | 南京平日制冷科技有限公司 | One kind decompression removes defrosting system |
| CN107270517B (en) * | 2017-07-26 | 2019-12-10 | 美的集团武汉制冷设备有限公司 | Air conditioning system, and control device and method of air conditioning system |
| CN107560117A (en) * | 2017-08-22 | 2018-01-09 | 珠海格力电器股份有限公司 | Air conditioning system and control method thereof |
| CN109708376B (en) * | 2018-07-13 | 2020-06-23 | 青岛海尔股份有限公司 | Refrigerator refrigerating system |
| JP7117945B2 (en) * | 2018-08-30 | 2022-08-15 | サンデン株式会社 | Heat pump system for vehicle air conditioner |
| CN111578467A (en) * | 2020-05-12 | 2020-08-25 | 广东美的制冷设备有限公司 | Control method of air conditioning system and air conditioning system |
| CN213020386U (en) * | 2020-07-31 | 2021-04-20 | 青岛海尔空调器有限总公司 | Air conditioner |
| CN113720057B (en) * | 2021-09-01 | 2022-10-04 | 珠海格力电器股份有限公司 | Refrigerating unit, control method and refrigerating equipment |
| CN115493320B (en) * | 2022-08-31 | 2024-05-10 | 青岛海尔空调电子有限公司 | Air source heat pump system and control method thereof |
| CN115388584B (en) * | 2022-10-24 | 2023-01-17 | 冰轮环境技术股份有限公司 | Self-adaptive liquid supply device and cascade refrigeration system with same |
Family Cites Families (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001108317A (en) * | 1999-10-05 | 2001-04-20 | Daikin Ind Ltd | Heat pump cooling and heating type air conditioner carbon dioxide refrigerant |
| JP2002168536A (en) * | 2000-11-29 | 2002-06-14 | Mitsubishi Heavy Ind Ltd | Air conditioner |
| US7010927B2 (en) * | 2003-11-07 | 2006-03-14 | Carrier Corporation | Refrigerant system with controlled refrigerant charge amount |
| CN1888668A (en) * | 2005-06-30 | 2007-01-03 | 乐金电子(天津)电器有限公司 | Air conditioner for improving performance when overloading and controlling method thereof |
| CN202328541U (en) * | 2011-12-14 | 2012-07-11 | Tcl空调器(中山)有限公司 | T3 working condition air-conditioner. |
| CN202648269U (en) * | 2012-06-04 | 2013-01-02 | 海尔集团公司 | Air conditioner |
| CN103868291B (en) * | 2012-12-14 | 2016-05-18 | 美的集团股份有限公司 | For the fluid reservoir of heat-exchange system and there is its heat-exchange system and air-conditioner |
| CN103913005B (en) * | 2013-01-09 | 2016-05-11 | 美的集团股份有限公司 | The air-conditioning of refrigeration system and control method thereof and this refrigeration system of tool |
| CN203231423U (en) * | 2013-04-15 | 2013-10-09 | 广东美的制冷设备有限公司 | Air conditioner with function of automatically adjusting quantity of refrigerants of system |
| CN103307818B (en) * | 2013-06-25 | 2016-05-04 | Tcl空调器(中山)有限公司 | The control method of air-conditioning system and the anti-liquid hammer of air-conditioning system |
| CN104676944B (en) * | 2013-11-28 | 2018-04-03 | 合肥美的暖通设备有限公司 | Air-conditioning system and its refrigerant adjusting method |
| CN104949297B (en) * | 2014-03-27 | 2018-02-16 | 珠海格力电器股份有限公司 | air conditioning unit and pressure control method thereof |
| CN104990320A (en) * | 2015-07-16 | 2015-10-21 | 广东美的暖通设备有限公司 | Control method and system capable of automatically filling refrigerants |
| CN204902340U (en) * | 2015-08-21 | 2015-12-23 | 广东美的制冷设备有限公司 | Air conditioner system |
| CN206281239U (en) * | 2016-11-28 | 2017-06-27 | 广州华凌制冷设备有限公司 | A kind of air-conditioner |
-
2016
- 2016-11-28 CN CN201611064532.7A patent/CN106403348B/en active Active
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