JP2006336999A - Heat pump type air conditioner - Google Patents
Heat pump type air conditioner Download PDFInfo
- Publication number
- JP2006336999A JP2006336999A JP2005165303A JP2005165303A JP2006336999A JP 2006336999 A JP2006336999 A JP 2006336999A JP 2005165303 A JP2005165303 A JP 2005165303A JP 2005165303 A JP2005165303 A JP 2005165303A JP 2006336999 A JP2006336999 A JP 2006336999A
- Authority
- JP
- Japan
- Prior art keywords
- air
- heat exchanger
- water
- supply
- return air
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 238000001816 cooling Methods 0.000 claims abstract description 20
- 239000003507 refrigerant Substances 0.000 claims abstract description 10
- 238000010438 heat treatment Methods 0.000 claims abstract description 7
- 239000000463 materials Substances 0.000 claims description 11
- 239000003570 air Substances 0.000 claims 31
- 239000011901 water Substances 0.000 claims 18
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances data:image/svg+xml;base64,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 data:image/svg+xml;base64,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 O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 abstract description 66
- 230000005494 condensation Effects 0.000 abstract description 4
- 238000009833 condensation Methods 0.000 abstract description 4
- 238000011144 upstream manufacturing Methods 0.000 description 6
- 238000010586 diagram Methods 0.000 description 3
- 239000007788 liquid Substances 0.000 description 2
- 238000005192 partition Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 1
- JOYRKODLDBILNP-UHFFFAOYSA-N ethyl urethane Chemical compound 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Images
Abstract
<P>PROBLEM TO BE SOLVED: To reduce operating power by lowering exhaust temperature by means of condensed water during cooling operation, and lowering condensation temperature. <P>SOLUTION: The heat pump type air conditioner has inside a casing 1 a supply air passage 2 extending from a fresh air opening 2a to an air supply opening 2b and a return air passage 3 extending from a return air opening 3a to an exhaust opening 3b. The heat pump type air conditioner alternately carries out cooling and heating operations for a room to be air-conditioned, by causing refrigerant from a compressor 12 to circulate through a supply side heat exchanger 7 provided in the air supply passage 2 and a return side heat exchanger 10 provided in the return air passage 3, from the return side heat exchanger 10 to the supply side heat exchanger 7, or in the reverse order. The air conditioner includes a drain pan 19 provided under the supply side heat exchanger, a water supply means 21 for supplying water around the return side heat exchanger 10, and a water feed means 20 for feeding drain water collected in the drain pan 19 to the water supply means 21. <P>COPYRIGHT: (C)2007,JPO&INPIT
Description
The present invention relates to a heat pump type air conditioner capable of switching between cooling and heating by operating a refrigerant circuit, and more particularly to an air conditioner capable of realizing a reduction in exhaust temperature during cooling operation.
In the outside air introduction type heat pump type air conditioner, the air supply side heat exchanger acts as an evaporator during cooling operation, and excess moisture in the introduced outside air is condensed by cooling, and the condensed moisture is discharged to the outside as drain. (For example, see Patent Documents 1 and 2), and the present situation is that the condensed moisture is not particularly utilized.
By the way, in recent years, outdoor exhaust during the cooling operation of the air conditioner has become a social problem that causes a remarkable heat island phenomenon in urban areas, and has been conventionally adopted as a means for lowering the exhaust temperature. Is only about lowering the set temperature.
JP 2003-42479 A (pages 1 to 3, FIGS. 1 to 5) Japanese Patent Laid-Open No. 2003-314846 (pages 1-7, FIGS. 1-5)
An object of the present invention is to provide a heat pump type air conditioner that can reduce exhaust gas temperature by using condensed water generated during cooling operation and can reduce the operation power by reducing the condensation temperature. .
In order to solve the above-described problem, a heat pump air conditioner according to claim 1 of the present invention includes an air supply channel from an outside air inlet to an air supply port to an air-conditioned room, and an air supply from the air-conditioned room. A return air passage extending from the return air outlet to the exhaust outlet, the supply side heat exchanger provided in the supply air passage, and the return air side heat exchanger provided in the return air passage from the compressor In the heat pump type air conditioner configured to switch between the cooling operation and the heating operation for the air-conditioned room by circulating the refrigerant of the return air side heat exchanger and the air supply side heat exchanger in the order or vice versa, A drain pan provided below the air supply side heat exchanger, water supply means for supplying water around the return air side heat exchanger, and water supply means for sending drain water collected by the drain pan to the water supply means It is as a thing of the structure which becomes.
The heat pump type air conditioner according to claim 2 of the present invention is the heat pump type air conditioner according to claim 1, wherein the water supply means is constituted by a humidifier provided on the upstream side of the return air side heat exchanger. .
The heat pump type air conditioner according to claim 3 of the present invention is configured such that the water supply means drops water from a water receiver provided above the return air side heat exchanger to the return air side heat exchanger. As a thing.
In the heat pump type air conditioner according to claim 4 of the present invention, the water receiver is in a dish-like shape having a large number of water passage holes at the bottom, and water is supplied from the water passage holes to the return air side heat exchanger. Is configured to be dripped.
In the heat pump type air conditioner according to claim 5 of the present invention, the water receiver is made of a water retention material, and water exceeding the water retention amount of the water retention material is dripped and supplied to the return air side heat exchanger. It is as the thing of the structure made to do.
A heat pump air conditioner according to a sixth aspect of the present invention includes an air supply passage in an upstream portion of an air supply side heat exchanger in the air supply passage and an upstream portion of the return air side heat exchanger in the return air passage. And a total heat exchanger across the return air flow path.
According to the present invention, the water condensed by cooling is collected by the drain pan in the supply-side heat exchanger that acts as an evaporator during the cooling operation, and the collected condensed water is condensed during the cooling operation. The heat is supplied to the return air side heat exchanger acting as a heat exchanger, and the heat generated from the return air side heat exchanger is taken away, so that the exhaust temperature can be lowered.
In addition, since the return air side heat exchanger is cooled by the condensed water, the condensation temperature in the return air side heat exchanger during cooling operation can be reduced, and the operating power can be reduced, that is, the running cost is reduced. Energy saving can be expected.
An embodiment of a heat pump type air conditioner according to the present invention will be described in detail with reference to the accompanying drawings.
In the casing 1, the supply air flow path 2 extending from the outside air inlet 2 a to the air supply port 2 b to the air-conditioned room (not shown) and the exhaust from the return air port 3 a for introducing the return air from the air-conditioned room to the outside. The return air flow path 3 reaching the port 3b is partitioned by a partition plate 1a, and a total heat exchanger 4 straddling the two flow paths is provided between the supply air flow path 2 and the return air flow path 3. .
In the casing 1, the supply air flow path 2 extending from the outside air inlet 2 a to the air supply port 2 b to the air-conditioned room (not shown) and the exhaust from the return air port 3 a for introducing the return air from the air-conditioned room to the outside. The return air flow path 3 reaching the port 3b is partitioned by a partition plate 1a, and a total heat exchanger 4 straddling the two flow paths is provided between the supply air flow path 2 and the return air flow path 3. .
The air supply flow path 2 is provided with a filter 5, the total heat exchanger 4, the humidifier 6, the air supply side heat exchanger 7, and the blower 8 in order from the outside air inlet 2 a side toward the air inlet 2 b. The return air flow path 3 is provided with a filter 9, the total heat exchanger 4, the return air side heat exchanger 10, and a blower 11 in this order from the return air port 3a to the exhaust port 3b.
The filter 5 in the air supply channel 2 has a two-stage configuration of, for example, a pre-filter 5a and a medium performance filter 5b.
Further, a compressor 12 of a refrigerant circuit is provided between the filter 9 and the total heat exchanger 4 in the return air flow path 3, and the refrigerant from the compressor 12 is supplied to the supply side heat exchanger 7. And the return air side heat exchanger 10 are switched and supplied by the four-way valve 13 in this order or vice versa, and are returned to the compressor via the accumulator 14. Switching between heating operation and cooling operation.
The compressor 12, the four-way valve 13 and the accumulator 14 may be provided between the total heat exchanger 4 and the return air side heat exchanger 10, or may be provided at other positions.
Further, in FIG. 1, reference numerals 15 and 16 denote expansion valves for the first heat exchanger and the second heat exchanger, respectively, and 17 and 18 denote the supply side heat exchanger 7 and the return air side heat exchanger 10, respectively. The check valve is shown.
Further, in FIG. 1, reference numerals 15 and 16 denote expansion valves for the first heat exchanger and the second heat exchanger, respectively, and 17 and 18 denote the supply side heat exchanger 7 and the return air side heat exchanger 10, respectively. The check valve is shown.
Specifically, during the cooling operation, as indicated by solid arrows in FIG. 1, the refrigerant from the compressor 12 is sent to the return air side heat exchanger 10 through the four-way valve 13 and flows through the return air flow path 3. The air is condensed by heat exchange with excess air and sent to the supply air side heat exchanger 7, evaporated in the supply air side heat exchanger and cooled in the supply air passage 2 to cool the accumulator 14. The gas is separated into gas and liquid by the accumulator and returned to the compressor 12.
In addition, the air cooled with the air supply side heat exchanger 7 is sent to an air-conditioned room.
In addition, the air cooled with the air supply side heat exchanger 7 is sent to an air-conditioned room.
Further, during the heating operation, as indicated by broken line arrows in FIG. 1, the refrigerant from the compressor 12 is sent to the supply side heat exchanger 7 through the four-way valve 13 and flows through the supply passage 2. The heat of the air that flows through the return air passage 3 is condensed by heat exchange with the air and heats the air in the air supply passage, and the condensed refrigerant is sent to the return air side heat exchanger 10 to be evaporated. The gas is then separated into gas and liquid by an accumulator and returned to the compressor 12.
In addition, the air heated with the air supply side heat exchanger 7 is sent to an air-conditioned room.
In addition, the air heated with the air supply side heat exchanger 7 is sent to an air-conditioned room.
Therefore, in the apparatus of the present invention, a drain pan 19 is provided below the air supply side heat exchanger 7, and condensed water generated on the surface of the air supply side heat exchanger that acts as an evaporator during cooling operation is collected. It is supposed to collect.
And the other end of the water supply pipe 20 as one of the water supply means connected at one end to the bottom of the drain pan 19 is connected to the humidifier 21 as the water supply means provided on the upstream side of the return air side heat exchanger 10 via the partition plate 1a. Condensed water that is connected and collected by the drain pan is used as humidifying water for the humidifier 21, and a vaporizing humidifier is used as the humidifier, for example.
The water pipe 20 has a downward gradient toward the humidifier 21 side, and the condensed water flows and is supplied by natural fall. However, depending on the specifications of the apparatus, the gradient as described above may be used. In some cases, a pump for water supply is appropriately provided in the middle of the water supply pipe.
In addition, the code | symbol 22 in FIG. 1 shows the drain pan for collecting the surplus water around a return air side heat exchanger, and the water dripped in the drain pan (the surplus water for humidification or the condensed water at the time of heating operation) is It is discharged outside.
In addition, the code | symbol 22 in FIG. 1 shows the drain pan for collecting the surplus water around a return air side heat exchanger, and the water dripped in the drain pan (the surplus water for humidification or the condensed water at the time of heating operation) is It is discharged outside.
As described above, the water condensed in the supply air side heat exchanger 7 during the cooling operation is vaporized by the humidifier 21 provided upstream of the return air side heat exchanger 10 and discharged to the return air side heat exchanger. Accordingly, the moisture released from the return air side heat exchanger 10 is deprived of moisture from the humidifier, and the exhaust temperature is lowered.
Further, since the temperature of the return air side heat exchanger 10 acting as a condenser during the cooling operation is lowered by moisture from the humidifier 21, the condensing temperature is lowered, and thus the operating power in the compressor is reduced. This can save energy.
FIG. 2 is a wet air diagram showing an example of the air state during cooling operation by the apparatus of the present invention having the above-described configuration. The supply air volume is 6000 CMH, and the supply air side heat exchanger 7 has an inlet. When calculation is performed assuming that the air is 29.4 ° C. at the dry bulb temperature, 23.0 ° C. at the wet bulb temperature, and the evaporator capacity of the supply side heat exchanger is 14.7 kW, at the supply side heat exchanger outlet Air has a dry bulb temperature of 26.0 ° C. and a wet bulb temperature of 21.0 ° C., and the amount of condensed water generated is 10.8 g / h.
If the air at the inlet of the humidifier 21 is 31.1 ° C. at the dry bulb temperature, 24.8 ° C. at the wet bulb temperature, and the humidification efficiency by the humidifier is 30%, the air temperature at the outlet of the humidifier 21 is dry bulb. The temperature is 30.0 ° C., that is, 1.1 ° C. lower than when humidification with condensed water is not performed. Therefore, the exhaust temperature discharged from the exhaust port 3b to the outside can also be reduced by 1.1 ° C. .
Further, it is assumed that the condensation temperature of the refrigerant in the return air side heat exchanger 10 is 15 ° C. higher than the temperature of the air flowing into the return air side heat exchanger (inlet temperature) by a dry bulb temperature. When the mobility is calculated, it is 3.43 kW when humidification with condensed water is not performed, 3.31 kW when humidification is performed, and a 3.5% reduction in power is expected when humidification with condensed water is performed. Can do.
In the embodiment described above, the air in the supply air flow path 2 and the return air flow path 3 is configured to exchange heat with the total heat exchanger 4, but the total heat exchanger may not be provided.
FIG. 3 shows another example of the water supply means. In the example shown in FIG. 3, instead of the humidifier 21, a water receiving tray 23 serving as a water receiver is arranged above the return air side heat exchanger 10. The water receiving tray has a plurality of holes 24 and 24 for passing water at the bottom, and the surface of the return air side heat exchanger 10 flows down by dripping water from these holes. Thus, the amount of water dropped can be set as appropriate depending on the number and diameter of the holes.
FIG. 4 shows still another example of the water supply means, in which a water receiver is constituted by a water retention material 26 accommodated in a frame 25, and the water supplied on the water retention material is the saturation amount of the water retention material. If it exceeds, it will be dripped at the return air side heat exchanger 10 from the lower side.
The water-retaining material 26 is preferably one in which the supplied water drops almost uniformly on the return air side heat exchanger. For example, a foamable resin material such as urethane foam or a sponge-like material such as the sea surface is used. it can.
The water-retaining material 26 is preferably one in which the supplied water drops almost uniformly on the return air side heat exchanger. For example, a foamable resin material such as urethane foam or a sponge-like material such as the sea surface is used. it can.
In addition to the water supply means described above, there may be a configuration in which condensed water is forcibly sprayed to the inlet of the return air side heat exchanger 10 using a pump or an ejector. There is a case where the condensed water is dropped in a water curtain shape on the upstream side.
DESCRIPTION OF SYMBOLS 1 Casing 2 Supply air flow path 3 Return air flow path 4 Total heat exchanger 5 Filter 6 Humidifier 7 Supply air side heat exchanger 8 Blower 9 Filter 10 Return air side heat exchanger 11 Blower 12 Compressor 13 Four-way valve 14 Accumulator 15, 16 Expansion valves 17 and 18 Check valve 19 Drain pan 20 Water supply pipe 21 Humidifier 22 for condensed water Drain pan 23 Water receiving tray 24 Water passage hole 25 Frame 26 Water retaining material
Claims (6)
- The casing has an air supply channel from the outside air inlet to the air supply port to the air-conditioned room, and a return air channel from the return air port to the air-conditioned room to the exhaust port, and is provided in the air supply channel. For the air side heat exchanger and the return air side heat exchanger provided in the return air flow path, the refrigerant from the compressor is transferred in the order of the return air side heat exchanger and the supply air side heat exchanger or vice versa. In a heat pump air conditioner configured to circulate and switch between cooling operation and heating operation for the air-conditioned room,
A drain pan provided below the air supply side heat exchanger, water supply means for supplying water around the return air side heat exchanger, and water supply means for sending drain water collected by the drain pan to the water supply means A heat pump air conditioner. - The heat pump air conditioner according to claim 1, wherein the water supply means is configured by a humidifier provided on the upstream side of the return air side heat exchanger.
- The heat pump air conditioner according to claim 1, wherein the water supply means is configured to drop water from a water receiver provided above the return air side heat exchanger to the return air side heat exchanger.
- The said water receiver is made into the dish-shaped thing which has many water flow holes in the bottom part, and is comprised so that water may be dripped from the said water flow hole to a return air side heat exchanger. Heat pump type air conditioner.
- 4. The heat pump according to claim 3, wherein the water receiver is made of a water retentive material, and water that exceeds the water retentivity of the water retentive material is supplied dropwise to the return air side heat exchanger. Air conditioner.
- A total heat exchanger straddling the supply air channel and the return air channel is provided at an upstream portion of the supply air side heat exchanger in the supply air channel and an upstream portion of the return air side heat exchanger in the return air channel. Item 2. A heat pump type air conditioner according to Item 1.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2005165303A JP2006336999A (en) | 2005-06-06 | 2005-06-06 | Heat pump type air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2005165303A JP2006336999A (en) | 2005-06-06 | 2005-06-06 | Heat pump type air conditioner |
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| JP2006336999A true JP2006336999A (en) | 2006-12-14 |
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| Application Number | Title | Priority Date | Filing Date |
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| JP2005165303A Pending JP2006336999A (en) | 2005-06-06 | 2005-06-06 | Heat pump type air conditioner |
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| JP2007327712A (en) * | 2006-06-09 | 2007-12-20 | Japan Exlan Co Ltd | Humidity control system |
| JP2009198023A (en) * | 2008-02-19 | 2009-09-03 | Toyo Eng Works Ltd | Heat pump type air conditioning device |
| JP2010002156A (en) * | 2008-06-23 | 2010-01-07 | Toyo Eng Works Ltd | Heat pump type air conditioner |
| CN102818325A (en) * | 2012-08-17 | 2012-12-12 | 浙江天洲制冷机电有限公司 | Air treatment heat pump unit |
| CN103712301A (en) * | 2013-12-26 | 2014-04-09 | 中机中联工程有限公司 | Composite evaporation cold type temperature-humidity-separate-control air processor |
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| CN104061630A (en) * | 2014-07-07 | 2014-09-24 | 叶立英 | Unit type fresh air processing machine |
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| CN105135554A (en) * | 2015-09-17 | 2015-12-09 | 丛旭日 | Pre-cooling energy-saving dehumidifying system and method |
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| JP2016035380A (en) * | 2009-11-19 | 2016-03-17 | フィパック・リサーチ・アンド・ディベロップメント・カンパニー | Method and apparatus for operating ducted fumehoods with increased energy efficiency |
| CN105698297A (en) * | 2016-03-23 | 2016-06-22 | 凯天环保科技股份有限公司 | Combined oil mist purifying unit of air conditioner |
| JP2017514092A (en) * | 2014-04-18 | 2017-06-01 | キュンドン ナビエン カンパニー リミテッドＫｙｕｎｇｄｏｎｇ Ｎａｖｉｅｎ Ｃｏ．，Ｌｔｄ． | Dehumidifying and cooling device |
| CN107036198A (en) * | 2017-03-21 | 2017-08-11 | 李元哲 | Air source heat pump New-air purifying system |
| US9772124B2 (en) | 2013-03-13 | 2017-09-26 | Nortek Air Solutions Canada, Inc. | Heat pump defrosting system and method |
| US9885486B2 (en) | 2010-08-27 | 2018-02-06 | Nortek Air Solutions Canada, Inc. | Heat pump humidifier and dehumidifier system and method |
| CN108613330A (en) * | 2018-04-27 | 2018-10-02 | 广东美的制冷设备有限公司 | Air conditioner and its control method and computer readable storage medium |
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| JP2007327712A (en) * | 2006-06-09 | 2007-12-20 | Japan Exlan Co Ltd | Humidity control system |
| KR101430440B1 (en) | 2007-01-26 | 2014-08-14 | 엘지전자 주식회사 | Air conditioner |
| JP2009198023A (en) * | 2008-02-19 | 2009-09-03 | Toyo Eng Works Ltd | Heat pump type air conditioning device |
| JP2010002156A (en) * | 2008-06-23 | 2010-01-07 | Toyo Eng Works Ltd | Heat pump type air conditioner |
| JP2016035380A (en) * | 2009-11-19 | 2016-03-17 | フィパック・リサーチ・アンド・ディベロップメント・カンパニー | Method and apparatus for operating ducted fumehoods with increased energy efficiency |
| US10274210B2 (en) | 2010-08-27 | 2019-04-30 | Nortek Air Solutions Canada, Inc. | Heat pump humidifier and dehumidifier system and method |
| US9885486B2 (en) | 2010-08-27 | 2018-02-06 | Nortek Air Solutions Canada, Inc. | Heat pump humidifier and dehumidifier system and method |
| CN105202795A (en) * | 2011-01-19 | 2015-12-30 | 北狄空气应对加拿大公司 | Heat pump system having a pre-processing module |
| US9920960B2 (en) | 2011-01-19 | 2018-03-20 | Nortek Air Solutions Canada, Inc. | Heat pump system having a pre-processing module |
| CN102818325A (en) * | 2012-08-17 | 2012-12-12 | 浙江天洲制冷机电有限公司 | Air treatment heat pump unit |
| US9772124B2 (en) | 2013-03-13 | 2017-09-26 | Nortek Air Solutions Canada, Inc. | Heat pump defrosting system and method |
| US10634392B2 (en) | 2013-03-13 | 2020-04-28 | Nortek Air Solutions Canada, Inc. | Heat pump defrosting system and method |
| CN103712301A (en) * | 2013-12-26 | 2014-04-09 | 中机中联工程有限公司 | Composite evaporation cold type temperature-humidity-separate-control air processor |
| CN103791570A (en) * | 2014-01-14 | 2014-05-14 | 西安工程大学 | Air conditioning device provided with evaporative condenser and ventilating system and used for power plant |
| CN103743008B (en) * | 2014-01-23 | 2017-03-15 | 南方风机股份有限公司 | Core level air-treatment unit |
| CN103743008A (en) * | 2014-01-23 | 2014-04-23 | 南方风机股份有限公司 | Low-noise low-vibration low-leakage high-seismic nuclear air-handling unit |
| JP2017514092A (en) * | 2014-04-18 | 2017-06-01 | キュンドン ナビエン カンパニー リミテッドＫｙｕｎｇｄｏｎｇ Ｎａｖｉｅｎ Ｃｏ．，Ｌｔｄ． | Dehumidifying and cooling device |
| US10502437B2 (en) | 2014-04-18 | 2019-12-10 | Kyungdong Navien Co., Ltd | Dehumidifying and cooling apparatus |
| CN104061630A (en) * | 2014-07-07 | 2014-09-24 | 叶立英 | Unit type fresh air processing machine |
| CN104676761A (en) * | 2015-03-09 | 2015-06-03 | 黎雅伟 | Indoor air supply device |
| CN105135554A (en) * | 2015-09-17 | 2015-12-09 | 丛旭日 | Pre-cooling energy-saving dehumidifying system and method |
| CN105698297A (en) * | 2016-03-23 | 2016-06-22 | 凯天环保科技股份有限公司 | Combined oil mist purifying unit of air conditioner |
| CN107036198A (en) * | 2017-03-21 | 2017-08-11 | 李元哲 | Air source heat pump New-air purifying system |
| CN108613330A (en) * | 2018-04-27 | 2018-10-02 | 广东美的制冷设备有限公司 | Air conditioner and its control method and computer readable storage medium |
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