WO2017010007A1 - Climatiseur - Google Patents

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Publication number
WO2017010007A1
WO2017010007A1 PCT/JP2015/070441 JP2015070441W WO2017010007A1 WO 2017010007 A1 WO2017010007 A1 WO 2017010007A1 JP 2015070441 W JP2015070441 W JP 2015070441W WO 2017010007 A1 WO2017010007 A1 WO 2017010007A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
heat source
source side
heat exchanger
pipe
Prior art date
Application number
PCT/JP2015/070441
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English (en)
Japanese (ja)
Inventor
侑哉 森下
Original Assignee
三菱電機株式会社
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Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2015/070441 priority Critical patent/WO2017010007A1/fr
Publication of WO2017010007A1 publication Critical patent/WO2017010007A1/fr

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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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • 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
    • 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
    • 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

Definitions

  • the present invention relates to an air conditioner used for a building multi air conditioner or the like.
  • a receiver As an air conditioner used in a conventional multi air conditioner for buildings, for example, a receiver is provided as an excess refrigerant storage device, and the amount of refrigerant circulating in the refrigerant circuit can be adjusted according to the operating capacity of the indoor unit.
  • the thing is known (for example, patent document 1).
  • the air conditioner of Patent Document 1 for example, when the cooling operation is performed in a temperature environment where the outside air is 25 ° C. or less, the amount of refrigerant circulating in the refrigerant circuit becomes excessive, and the pressure in the outdoor unit increases. . Therefore, in the air conditioner of Patent Document 1, depending on the temperature condition of the cooling operation, the compressor input increases due to an increase in the pressure in the outdoor unit, which may reduce the operating efficiency of the air conditioner.
  • the present invention has been made to solve the above-described problems, and provides an air conditioner capable of efficiently operating by appropriately adjusting the input of the compressor according to the temperature condition of the outside air during cooling. For the purpose.
  • An air conditioner according to the present invention is divided into a compressor that compresses a refrigerant, a heat source side heat exchanger that is divided into a plurality of regions that perform heat exchange between the refrigerant and outside air, and each of the plurality of regions.
  • a refrigerant flow switching device that changes the flow direction of the refrigerant passing through the heat source side heat exchanger, a decompression device that depressurizes the refrigerant, and a load side heat exchanger that exchanges heat between the refrigerant and the indoor space.
  • a refrigeration cycle circuit that circulates refrigerant by connecting a pipe, and is provided in the middle of the refrigerant pipe that branches from the refrigerant pipe between the heat source side heat exchanger and the load side heat exchanger and leads to the suction side of the compressor
  • the refrigerant is stored in the refrigerant pipe between the heat source side heat exchanger and the load side heat exchanger, and is connected to the inlet side of the receiver.
  • the heat source side divided into the plurality of regions A control device that uses only some of the heat source side heat exchangers of the heat exchanger and performs control to store the refrigerant in the receiver.
  • the air conditioning apparatus which can reduce energy consumption can be provided.
  • FIG. 3 is a schematic refrigerant circuit diagram illustrating an example of a refrigerant flow in the first cooling operation mode (normal cooling operation) of the air-conditioning apparatus 1 according to Embodiment 1 of the present invention.
  • FIG. 1 is a schematic diagram illustrating an installation example of the air-conditioning apparatus 1 according to the first embodiment.
  • the dimensional relationship and shape of each component may be different from the actual one.
  • the same or similar members or parts are denoted by the same reference numerals, or the reference numerals are omitted.
  • the air conditioner 1 includes an outdoor unit 100 (for example, an outdoor unit that is a heat source unit), and a plurality of indoor units 200 (for example, indoor units) arranged in parallel to the outdoor unit 100. Is provided.
  • the outdoor unit 100 and the plurality of indoor units 200 are configured as separate housings.
  • the outdoor unit 100 and the indoor unit 200 are connected by a first communication pipe 300 and a second communication pipe 400.
  • the first connection pipe 300 and the second connection pipe 400 may be local pipes that are existing pipes.
  • the outdoor unit 100 (heat source side unit) is usually disposed in an outdoor space 600 (for example, the rooftop of a building 500 such as a building), and the indoor unit passes through the first communication pipe 300 or the second communication pipe 400. 200 is supplied with cold or warm heat.
  • the indoor unit 200 (load-side unit) supplies air for cooling or heating to an indoor space 700 (for example, a living room of the building 500).
  • the indoor unit 200 is a ceiling cassette type room as shown in FIG. Can be configured as a machine.
  • the outdoor unit 100 can be configured to supply warm heat to the underfloor pipe 800 in the indoor space 700 to provide floor heating for the indoor space 700.
  • FIG. 2 is a schematic refrigerant circuit diagram illustrating an example of the air-conditioning apparatus 1 according to the first embodiment.
  • one outdoor unit 100 and one indoor unit 200 are connected by a first connecting pipe 300 and a second connecting pipe 400.
  • the air conditioner 1 of the first embodiment includes a compressor 2, an oil separator 4, a first refrigerant flow switching device 6, a second refrigerant flow switching device 7, and a heat source side heat exchanger.
  • the supercooling heat exchanger 10 the first heat source side pressure reducing device 12, the load side pressure reducing device 14, the load side heat exchanger 16, and the accumulator 18 are connected via a refrigerant pipe, A refrigeration cycle circuit for circulation is provided.
  • Compressor 2, oil separator 4, first refrigerant flow switching device 6, second refrigerant flow switching device 7, heat source side heat exchanger 8, supercooling heat exchanger 10, first heat source side pressure reducing device 12 and the accumulator 18 are accommodated in the outdoor unit 100.
  • the load-side decompressor 14 and the load-side heat exchanger 16 are accommodated in the indoor unit 200.
  • the oil separator 4, the supercooling heat exchanger 10, and the accumulator 18 are not essential components and may not be provided depending on the application of the air conditioner 1. Further, FIG. 2 shows an example of mounting each unit, but each element does not necessarily have to be mounted as shown in FIG.
  • Compressor 2 compresses the sucked low-pressure refrigerant and discharges it as a high-pressure refrigerant.
  • the compressor 2 for example, a scroll compressor or a rotary compressor capable of capacity control (frequency control) by an inverter is used.
  • the oil separator 4 separates and removes refrigeration oil contained in the high-pressure refrigerant discharged from the compressor 2 to reduce the amount of refrigeration oil contained in the high-pressure refrigerant.
  • the separated and removed refrigeration oil is returned to the compressor 2 via an oil return pipe (not shown).
  • the first refrigerant flow switching device 6 is a device configured to switch the refrigerant flow channel inside the first refrigerant flow switching device 6.
  • the first refrigerant flow switching device 6 is controlled so as to supply cold heat from the outdoor unit 100 to the indoor unit 200 via the first communication pipe 300 during the cooling operation.
  • the first refrigerant flow switching device 6 is controlled so as to supply heat from the outdoor unit 100 to the indoor unit 200 via the second communication pipe 400 during the heating operation.
  • the second refrigerant flow switching device 7 is a device configured to switch the refrigerant flow path inside the second refrigerant flow switching device 7, similarly to the first refrigerant flow switching device 6.
  • the second refrigerant flow switching device 7 is controlled to supply cold heat from the outdoor unit 100 to the indoor unit 200 via the first communication pipe 300 during the cooling operation.
  • the second refrigerant flow switching device 7 is controlled so as to supply heat from the outdoor unit 100 to the indoor unit 200 via the second communication pipe 400 during the heating operation.
  • a four-way valve is used as the first refrigerant flow switching device 6 and the second refrigerant flow switching device 7.
  • a terminal member 7a for blocking the refrigerant flow path is connected to one end of the refrigerant flow path inside the second refrigerant flow switching device 7.
  • the “cooling operation” is an operation for supplying a low-temperature and low-pressure refrigerant to the load-side heat exchanger 16, and an operation for supplying air for cooling to the indoor space 700 in FIG.
  • the “heating operation” is an operation for supplying a high-temperature and high-pressure refrigerant to the load-side heat exchanger 16, and an operation for supplying heating air to the indoor space 700 of FIG.
  • a two-way valve or a three-way valve may be used as the first refrigerant flow switching device 6 and the second refrigerant flow switching device 7.
  • the heat source side heat exchanger 8 is a heat exchanger that functions as a radiator (condenser) during cooling operation and functions as an evaporator (cooler) during heating operation.
  • the heat source side heat exchanger 8 includes a refrigerant flowing inside the heat source side heat exchanger 8 and outside air (for example, outdoor air in the outdoor space 600 of FIG. 1) blown by a heat source side fan (not shown). It is configured to perform heat exchange.
  • a cross fin type fin-and-tube heat exchanger composed of a heat transfer tube and a plurality of fins is used.
  • the heat source side heat exchanger 8 is divided into two heat exchange regions, region A and region B.
  • One end of a heat transfer tube (not shown) in the region A of the heat source side heat exchanger 8 is connected to a plurality of first header branch tubes 82 branched from the first header main tube 81.
  • the other end of the heat transfer tube in the region A of the heat source side heat exchanger 8 is connected to a plurality of second header branch tubes 83 branched from the second header main tube 84.
  • the heat source side heat exchanger 8 is configured to be divided into two heat exchange regions, region A and region B, but may be configured to be divided into three or more heat exchange regions. .
  • one end of a heat transfer tube (not shown) of the heat source side heat exchanger 8 in the region B is connected to a plurality of third header branch tubes 86 branched from the third header main tube 85.
  • the other end portion of the heat transfer pipe of the heat source side heat exchanger 8 in the region B is connected to a plurality of fourth header branch pipes 87 branched from the fourth header main pipe 88.
  • the supercooling heat exchanger 10 is a heat exchanger that further cools the high-pressure refrigerant flowing from the heat source side heat exchanger 8 during the cooling operation.
  • the supercooling heat exchanger 10 is, for example, a double-tube heat exchanger having an inner pipe (not shown) and an outer pipe (not shown) arranged concentrically when viewed from the end of the inner pipe. It is possible to perform heat exchange between the high-pressure refrigerant flowing in the inner pipe and the decompressed refrigerant flowing in the outer pipe.
  • the supercooling heat exchanger 10 is a double-pipe heat exchanger, during the heating operation, the supercooling heat exchanger 10 functions as a part of the refrigerant pipe constituting the refrigeration cycle circuit.
  • a specific configuration of the refrigerant circuit when the supercooling heat exchanger 10 is a double-pipe heat exchanger will be described later.
  • the first heat source side decompression device 12 expands and decompresses the high-pressure refrigerant during the cooling operation, and flows into the first communication pipe 300 as a refrigerant having a pressure lower than the design pressure of the first communication pipe 300. It functions as a (squeezing device for liquid equalization between outdoor units). For example, when the first connecting pipe 300 is an existing pipe, the design pressure of the first connecting pipe 300 is set to the pressure resistance reference value of the first connecting pipe 300. Further, the first heat source side decompression device 12 functions as a throttle device that expands and decompresses the refrigerant flowing from the first communication pipe 300 and flows into the heat source side heat exchanger 8 during the heating operation. As the first heat source side pressure reducing device 12, an electronic expansion valve such as a linear electronic expansion valve (LEV) whose opening degree can be adjusted in multiple stages or continuously is used.
  • LEV linear electronic expansion valve
  • the load side decompression device 14 further expands and decompresses the refrigerant having a pressure lower than the design pressure of the first communication pipe 300 flowing from the first communication pipe 300 and flows into the load side heat exchanger 16. It functions as an expansion device (indoor expansion device). Further, the load-side decompression device 14 is a throttling device that expands and decompresses the high-pressure refrigerant during the heating operation, and flows into the first communication pipe 300 as a refrigerant having a pressure lower than the design pressure of the first communication pipe 300. Function.
  • the load side pressure reducing device 14 is configured as an electronic expansion valve such as a linear electronic expansion valve whose opening degree can be adjusted in multiple stages or continuously.
  • the load side heat exchanger 16 (use side heat exchanger) is a heat exchanger that functions as an evaporator (cooler) during cooling operation and as a radiator (condenser) during heating operation.
  • the load-side heat exchanger 16 is configured to exchange heat between, for example, a refrigerant flowing inside the load-side heat exchanger 16 and outside air (for example, indoor air in the indoor space 700 in FIG. 1).
  • a cross fin type fin-and-tube heat exchanger composed of a heat transfer tube and a plurality of fins is used.
  • the load side heat exchanger 16 can be comprised so that external air may be supplied by the ventilation from a load side ventilation fan (not shown).
  • the accumulator 18 is a storage container having a refrigerant storage function for storing excess refrigerant generated due to a difference in refrigerant amount during heating operation and cooling operation. Further, the accumulator 18 retains the liquid refrigerant that is temporarily generated when the operation state of the air conditioner 1 is changed, such as a transient operation change, so that a large amount of liquid refrigerant flows into the compressor 2. It is also a storage container having a gas-liquid separation function to prevent this.
  • a discharge pipe (not shown) of the compressor 2 and the inlet of the oil separator 4 are connected by a first heat source side refrigerant pipe 21.
  • the refrigerant outlet of the oil separator 4 and the first refrigerant flow switching device 6 are connected by a second heat source side refrigerant pipe 22.
  • a check valve 41 is disposed in the second heat source side refrigerant pipe 22 to prevent the high-pressure refrigerant from flowing back to the compressor 2.
  • coolant piping 22 located between the non-return valve 41 and the 1st refrigerant
  • the heat source side refrigerant pipe 25 is branched and connected.
  • the first refrigerant flow switching device 6 and the first header main pipe 81 are connected by a third heat source side refrigerant pipe 23.
  • the second refrigerant flow switching device 7 and the third header main pipe 85 are connected by a sixth heat source side refrigerant pipe 26.
  • One end of the fourth heat source side refrigerant pipe 24 is connected to the second header main pipe 84.
  • One end of the seventh heat source side refrigerant pipe 27 is connected to the fourth header main pipe 88.
  • the other one end of the fourth heat source side refrigerant pipe 24 and the seventh heat source side refrigerant pipe 27 joins the fourth heat source side refrigerant pipe 24 and the seventh heat source side refrigerant pipe 27 during the cooling operation.
  • It is connected to a connecting member 43 that functions as a merger.
  • the connecting member 43 is a member that functions as a distributor for diverting the refrigerant to the fourth heat source side refrigerant pipe 24 and the seventh heat source side refrigerant pipe 27 during the heating operation.
  • the connecting member 43 and the supercooling heat exchanger 10 are connected by an eighth heat source side refrigerant pipe 28.
  • the subcooling heat exchanger 10 and the first communication pipe 300 are connected by a ninth heat source side refrigerant pipe 29.
  • the first heat source side decompression device 12 is disposed in the ninth heat source side refrigerant pipe 29.
  • a first heat source side connection valve 47a is disposed at the end of the ninth heat source side refrigerant pipe 29 on the first communication pipe 300 side, and the first heat source side connection valve 47a has a first end.
  • a first joint portion 49a such as a flare joint is attached to the connecting pipe 300 side.
  • the ninth heat source side refrigerant pipe 29 is connected to the first communication pipe 300 at the first joint portion 49a.
  • the first heat source side connection valve 47a is constituted by, for example, a two-way valve such as a two-way electromagnetic valve that can be switched between open and closed. Further, in the ninth heat source side refrigerant pipe 29, a position between the first heat source side pressure reducing device 12 and the first heat source side connection valve 47a is used to scavenge dust, impurities, etc. contained in the refrigerant.
  • the 1st strainer 45a which is a filter is arrange
  • the first refrigerant flow switching device 6 and the second communication pipe 400 are connected by a tenth heat source side refrigerant pipe 30.
  • a second heat source side connection valve 47b is disposed at the end of the tenth heat source side refrigerant pipe 30 on the second communication pipe 400 side, and the second connection pipe of the second heat source side connection valve 47b.
  • a second joint portion 49b such as a flare joint is attached.
  • coolant piping 30 is connected with the 2nd connection piping 400 by the 2nd coupling part 49b.
  • the second heat source side connection valve 47b is configured by, for example, a two-way valve such as a two-way electromagnetic valve that can be switched between open and closed.
  • a position between the first refrigerant flow switching device 6 and the second heat source side connection valve 47b removes dust, impurities, and the like contained in the refrigerant.
  • the 2nd strainer 45b which is a filter of this is arrange
  • the first refrigerant flow switching device 6 and the first branch portion 32a of the twelfth heat source side refrigerant pipe 32 are connected by an eleventh heat source side refrigerant pipe 31.
  • the twelfth heat source side refrigerant pipe 32 is a refrigerant pipe that connects the second refrigerant flow switching device 7 and the inlet of the accumulator 18.
  • the inlet of the accumulator 18 and the suction pipe (not shown) of the compressor 2 are connected by a thirteenth heat source side refrigerant pipe 33.
  • the first communication pipe 300 and the load side heat exchanger 16 are connected by a first load side refrigerant pipe 35.
  • the load side decompression device 14 is disposed in the first load side refrigerant pipe 35.
  • a joint portion such as a flare joint is provided on the first communication pipe 300 side of the first load-side refrigerant pipe 35, and is connected to the first communication pipe 300 at the joint portion. Has been.
  • the load side heat exchanger 16 and the second communication pipe 400 are connected by a second load side refrigerant pipe 36.
  • a joint portion (not shown) such as a flare joint is provided on the second load-side refrigerant pipe 36 on the second communication pipe 400 side, and is connected to the second communication pipe 400 at the joint. Yes.
  • any kind of refrigerant can be selected as the refrigerant that circulates through the refrigerant pipe described above depending on the application of the air-conditioning apparatus 1.
  • a single refrigerant such as R22, R134a, R32, HFO1234yf, HFO1234ze, or HFO1123
  • a pseudo-azeotropic refrigerant mixture such as R410A or R404A
  • a non-azeotropic refrigerant mixture such as R407C
  • a refrigerant with a low global warming potential such as CF 3 CF ⁇ CH 2 containing a double bond in the chemical formula can be used.
  • the above-mentioned refrigerant may be used as a mixture in which two or more kinds are mixed.
  • it is possible to use natural refrigerant such as CO 2 or propane.
  • the supercooling heat exchanger 10 can be configured as a double-pipe heat exchanger.
  • the double-tube supercooling heat exchanger 10 has an inner tube (not shown) and an outer tube (not shown) arranged concentrically when viewed from the end of the inner tube. The heat exchange is performed between the high-pressure refrigerant flowing in the inner pipe and the decompressed refrigerant flowing in the outer pipe.
  • FIG. 1 The ninth heat source side refrigerant pipe 29 whose one end is connected to the first connecting pipe 300 has the other end connected to the other end of the inner pipe of the supercooling heat exchanger 10.
  • a first heat source side branch refrigerant pipe 51 is connected to the end on the side refrigerant pipe 29 side.
  • One end of the second heat source side branch refrigerant pipe 53 is connected to the end of the outer pipe of the supercooling heat exchanger 10 on the side of the eighth heat source side refrigerant pipe 28.
  • the other end of the second heat source side branch refrigerant pipe 53 is connected to the second branch part 32 b of the twelfth heat source side refrigerant pipe 32 connected to the inlet of the accumulator 18.
  • the second heat source side decompression device 13 is disposed in the first heat source side branch refrigerant pipe 51.
  • the second heat source-side decompression device 13 expands and decompresses the high-pressure refrigerant that flows from the branch portion 29a of the ninth heat source-side refrigerant pipe 29 to the first heat source-side branch refrigerant pipe 51 during cooling operation.
  • it functions as a throttle device (heat source side throttle device) that causes the decompressed refrigerant to flow into the outer tube of the supercooling heat exchanger 10.
  • the second heat source side pressure reducing device 13 is configured as an electronic expansion valve such as a linear electronic expansion valve (LEV) whose opening degree can be adjusted in multiple stages or continuously.
  • LEV linear electronic expansion valve
  • the seventh heat source side refrigerant pipe 27 is a refrigerant pipe connected between the fourth header main pipe 88 and the connecting member 43.
  • the fourth header main pipe 88 is a refrigerant pipe connected to a heat transfer pipe (not shown) of the heat source side heat exchanger 8 in the region B via a plurality of fourth header branch pipes 87.
  • one end of the second heat source side branch refrigerant pipe 53 is connected to the refrigerant outlet side end of the outer tube of the supercooling heat exchanger 10 and the other one end is the twelfth. It is the refrigerant
  • the twelfth heat source side refrigerant pipe 32 is a refrigerant pipe connected to the inflow port of the accumulator 18.
  • a flow path switching valve 55 is disposed in the seventh heat source side refrigerant pipe 27.
  • the flow path switching valve 55 and the branch portion 53 a of the second heat source side branch refrigerant pipe 53 are connected by a third heat source side branch refrigerant pipe 57.
  • the flow path switching valve 55 switches the refrigerant flow path inside the flow path switching valve 55 during the cooling operation, and connects the connection destination of the seventh heat source side refrigerant pipe 27 on the fourth header main pipe 88 side to the connecting member 43.
  • the second heat source side refrigerant pipe 27 or the second heat source side branch refrigerant pipe 53 is switched to two directions.
  • the flow path switching valve 55 is configured to connect the seventh heat source side refrigerant pipe 27 on the connecting member 43 side and the seventh heat source side refrigerant pipe 27 on the fourth header main pipe 88 side during the heating operation. Is done.
  • a three-way valve is used as the flow path switching valve 55.
  • FIG. 3 is a schematic diagram schematically showing the configuration and arrangement of the receiver 60 of the air-conditioning apparatus 1 according to Embodiment 1.
  • the flow direction of the refrigerant is indicated by white block arrows.
  • the receiver 60 includes a storage 60a that is a casing that stores liquid refrigerant, an inflow pipe 60b that is a refrigerant pipe that flows the refrigerant into the storage 60a, an outflow pipe 60c that is a refrigerant pipe that causes the refrigerant to flow out of the storage 60a, and a storage And a leg portion 60d which is a support member for supporting the bottom portion of 60a.
  • the receiver 60 is configured as a vertical-type surplus liquid refrigerant storage container.
  • the branch portion 28 a of the eighth heat source side refrigerant pipe 28 and the end portion on the inlet side of the inflow pipe 60 b of the receiver 60 are connected by a fourth heat source side branch refrigerant pipe 61. Yes.
  • the fifth heat source side branch is provided between the end portion on the outlet side of the outlet pipe 60 c of the receiver 60 and the third branch portion 32 c of the twelfth heat source side refrigerant pipe 32.
  • the refrigerant pipe 65 connects.
  • the eighth heat source side refrigerant pipe 28 is a refrigerant pipe connecting the connecting member 43 and the inner pipe of the supercooling heat exchanger 10, and the twelfth heat source side refrigerant pipe 32 is the accumulator 18. It is refrigerant piping connected to the inflow port.
  • the branching portion 28 a of the eighth heat source side refrigerant pipe 28 is arranged so as to be located above the end of the inlet of the inflow pipe 60 b of the receiver 60.
  • the fourth heat source side branch refrigerant pipe 61 is connected to the branch portion 28 a of the eighth heat source side refrigerant pipe 28 so as to be positioned below the eighth heat source side refrigerant pipe 28.
  • the inflow pipe 60b of the receiver 60 is arrange
  • the liquid refrigerant flowing into the fourth heat source side branch refrigerant pipe 61 from the branch portion 28a of the eighth heat source side refrigerant pipe 28 flows into the receiver 60 by its own weight.
  • the pipe 60b is surely introduced and stored in the storage 60a.
  • the outflow pipe 60c of the receiver 60 is disposed at the bottom of the storage 60a, and the end of the outflow pipe 60c on the inlet side communicates with the internal space below the storage 60a. Therefore, the receiver 60 according to the first embodiment can cause the liquid refrigerant stored at the bottom of the storage 60a to flow into the fifth heat source side branch refrigerant pipe 65 from the outflow pipe 60c.
  • an electromagnetic valve 63 is arranged in the fourth heat source side branch refrigerant pipe 61.
  • the solenoid valve 63 is a valve on the refrigerant inflow side to the receiver 60 that opens or closes the refrigerant flow path of the fourth heat source side branched refrigerant pipe 61 by supplying power or stopping power.
  • an electronic expansion valve such as a linear electronic expansion valve (LEV) whose opening degree can be adjusted in multiple steps or continuously may be used.
  • a flow rate adjustment valve 67 is arranged in the fifth heat source side branch refrigerant pipe 65.
  • the flow rate adjusting valve 67 is a valve that adjusts the amount of refrigerant returned to the refrigeration cycle circuit by storing the refrigerant in the accumulator 18 through the fifth heat source side branched refrigerant pipe 65.
  • an electronic expansion valve such as a linear electronic expansion valve (LEV) whose opening degree can be adjusted in multiple stages or continuously is used.
  • FIG. 3 shows a second temperature sensor 74 that is a liquid refrigerant temperature detection sensor. The second temperature sensor 74 will be described later.
  • the air conditioner 1 includes a first pressure sensor 70, a second pressure sensor 71, a first temperature sensor 73, a second temperature sensor 74, and a third temperature sensor. 75, a fourth temperature sensor 76, and a refrigerant leakage detection sensor 78.
  • the first pressure sensor 70 is disposed in the second heat source side refrigerant pipe 22.
  • the first pressure sensor 70 is a high-pressure sensor that detects the pressure of the high-temperature and high-pressure refrigerant that flows into the second heat source side refrigerant pipe 22 from the discharge pipe of the compressor 2 via the oil separator 4.
  • the second pressure sensor 71 is disposed in the twelfth heat source side refrigerant pipe 32.
  • the second pressure sensor 71 is a low-pressure sensor that detects the pressure of the low-pressure refrigerant flowing into the suction port of the compressor 2 from the twelfth heat source side refrigerant pipe 32 via the accumulator 18.
  • first pressure sensor 70 and the second pressure sensor 71 a crystal piezoelectric pressure sensor, a semiconductor sensor, a pressure transducer, or the like is used.
  • the first pressure sensor 70 and the second pressure sensor 71 may be the same type or different types.
  • the first temperature sensor 73 is disposed, for example, on the upstream side of a heat source side fan (not shown), and is sucked by the heat source side fan and is sent to the heat source side heat exchanger 8 (for example, outside air shown in FIG. 1).
  • This is an outdoor temperature sensor that detects the temperature of the outdoor air in the outdoor space 600.
  • the second temperature sensor 74 is disposed in the eighth heat source side refrigerant pipe 28.
  • the second temperature sensor 74 detects the temperature of the liquid refrigerant flowing from the heat source side heat exchanger 8 into the eighth heat source side refrigerant pipe 28 via the eighth heat source side refrigerant pipe 28 during the cooling operation. It is a temperature sensor (liquid refrigerant temperature detection sensor).
  • the second temperature sensor 74 is a temperature sensor that detects the temperature of the two-phase refrigerant decompressed by the first heat source side decompression device 12 via the eighth heat source side refrigerant pipe 28 during the heating operation. is there.
  • the third temperature sensor 75 is disposed in the first load side refrigerant pipe 35.
  • the third temperature sensor 75 is a temperature sensor (use side heat exchanger) that detects the temperature of the two-phase refrigerant decompressed by the load side decompression device 14 via the first load side refrigerant pipe 35 during the cooling operation. Liquid side sensor). Further, the third temperature sensor 75 detects the temperature of the liquid refrigerant flowing from the load-side heat exchanger 16 to the first load-side refrigerant pipe 35 via the first load-side refrigerant pipe 35 during the heating operation. It is a temperature sensor.
  • the fourth temperature sensor 76 is disposed in the second load side refrigerant pipe 36.
  • the third temperature sensor 75 detects the temperature of the low-pressure refrigerant flowing from the load-side heat exchanger 16 to the second load-side refrigerant pipe 36 through the second load-side refrigerant pipe 36 during the cooling operation.
  • Sensor use side heat exchanger gas side sensor.
  • the fourth temperature sensor 76 determines the temperature of the high-temperature and high-pressure refrigerant flowing into the second load-side refrigerant pipe 36 from the discharge pipe of the compressor 2 through the oil separator 4 during the heating operation. It is a temperature sensor detected via the load side refrigerant
  • Examples of materials for the first temperature sensor 73, the second temperature sensor 74, the third temperature sensor 75, and the fourth temperature sensor 76 include a semiconductor (for example, a thermistor) or a metal (for example, a resistance temperature detector). Is used.
  • the first temperature sensor 73, the second temperature sensor 74, the third temperature sensor 75, and the fourth temperature sensor 76 may be made of the same material or different materials. Good.
  • the refrigerant leakage detection sensor 78 is disposed in the indoor unit 200 and detects refrigerant leakage from the indoor unit 200.
  • the refrigerant leakage detection sensor 78 is disposed in the indoor space 700 of FIG. 1 in order to prevent, for example, refrigerant leakage into the indoor space 700 of FIG. 1 (for example, the living room of the building 500).
  • a gas sensor such as a semiconductor gas sensor or a hot wire semiconductor gas sensor is used.
  • Two or more refrigerant leakage detection sensors 78 may be arranged in the indoor space 700 in order to prevent refrigerant leakage into the indoor space 700. Further, for example, in a portion where the refrigerant leakage inside the indoor unit 200 is likely to occur, such as a connection portion between the first load side refrigerant pipe 35 or the second load side refrigerant pipe 36 and the load side heat exchanger 16. You may arrange.
  • control device 90 of the air-conditioning apparatus 1 according to Embodiment 1 will be described with reference to FIG.
  • the control device 90 controls the operation of the entire air conditioner 1 including driving or stopping of the outdoor unit 100. Further, as shown in FIG. 2, the control device 90 is also connected to an indoor unit control device 95 (indoor control device) that controls the operation of the indoor unit 200 via a transmission line 98. It is comprised so that it can communicate. In addition, you may comprise so that communication between the control apparatus 90 and the indoor unit control apparatus 95 can be performed by radio
  • the control device 90 and the indoor unit control device 95 have a microcomputer having a CPU that functions as a calculation unit, a memory (for example, ROM, RAM, etc.) that functions as a storage unit, an I / O port that functions as a communication unit, and the like. is doing.
  • the indoor unit controller 95 receives the electrical signal of the temperature information in the indoor unit 200 detected by the third temperature sensor 75 and the fourth temperature sensor 76 or the electrical signal of the refrigerant leak detected by the refrigerant leak detection sensor 78. , And configured to transmit to the control device 90 via the transmission line 98. Further, the indoor unit control device 95 is configured to transmit information related to the operating state of the indoor unit 200 to the control device 90 via the transmission line 98.
  • the information related to the operating state of the indoor unit 200 includes information on driving or stopping of the indoor unit 200, power consumption of the indoor unit 200, information on the operating capacity of the indoor unit 200, information on switching between cooling operation and heating operation, etc. It is included.
  • the control device 90 receives the electrical signal of the pressure information detected by the first pressure sensor 70 and the second pressure sensor 71 and the electrical signal of the temperature information detected by the first temperature sensor 73 and the second temperature sensor 74. Configured to receive. In addition, the control device 90 is configured to receive temperature information or an electric signal of refrigerant leakage transmitted from the indoor unit control device 95 via the transmission line 98 and information related to the operating state of the indoor unit 200. The control device 90 controls operations of various actuators of the air conditioning device 1 based on the received information.
  • the various actuators of the air conditioner 1 include, for example, the compressor 2, the first refrigerant flow switching device 6, the second refrigerant flow switching device 7, the first heat source side pressure reducing device 12, and the second heat source side.
  • the pressure reducing device 13, the load side pressure reducing device 14, the flow path switching valve 55, the electromagnetic valve 63, and the flow rate adjusting valve 67 are included.
  • the control device 90 and the first pressure sensor 70, the second pressure sensor 71, the first temperature sensor 73, and the second temperature sensor 74 are connected by a communication line (not shown). Can be configured. Similarly, the indoor unit control device 95, the third temperature sensor 75, the fourth temperature sensor 76, and the refrigerant leakage detection sensor 78 can be connected by a communication line (not shown). In addition to the memory such as ROM and RAM, the control device 90 may be configured to have a storage unit (not shown) that can store various data such as a standard outside air temperature range.
  • Normal cooling operation means, for example, a cooling operation under the cooling condition defined in the JIS standard (JIS B 8616) of the package air conditioner.
  • the “normal cooling operation” is referred to as a first cooling operation mode.
  • the outside air temperature is in the standard temperature range
  • the indoor unit 200 is in the standard operation capacity range
  • the air is discharged from the compressor 2 detected by the first pressure sensor 70.
  • This refers to a cooling operation performed by the air-conditioning apparatus 1 according to Embodiment 1 when the pressure of the high-temperature and high-pressure gas refrigerant is within the range of the standard high-pressure.
  • the standard temperature range of the outside air temperature is, for example, a temperature range of 25 ° C. to 43 ° C.
  • the lower limit value of the standard operating capacity range is, for example, 50% operating capacity when the total operating capacity of the indoor unit 200 in the air conditioner 1 is 100%.
  • the upper limit value of the standard high pressure range is, for example, 36 kg / cm 2 .
  • FIG. 4 is a schematic refrigerant circuit diagram showing a refrigerant flow in the first cooling operation mode (normal cooling operation) of the air-conditioning apparatus 1 according to Embodiment 1.
  • the flow direction of the refrigerant is indicated by solid line arrows.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the oil separator 4 via the first heat source side refrigerant pipe 21.
  • the oil separator 4 the components of the refrigerating machine oil are separated and removed from the high-temperature and high-pressure gas refrigerant discharged from the compressor 2.
  • a part of the high-temperature and high-pressure gas refrigerant from which the components of the refrigerating machine oil are separated and removed by the oil separator 4 includes the second heat source side refrigerant pipe 22, the first refrigerant flow switching device 6, and the third heat source side refrigerant pipe. 23, the first header main pipe 81, and the plurality of first header branch pipes 82 flow into the region A of the heat source side heat exchanger 8.
  • the remaining portion of the high-temperature and high-pressure gas refrigerant from which the components of the refrigeration oil are separated and removed by the oil separator 4 is the second heat source side refrigerant pipe 22, the fifth heat source side refrigerant pipe 25, and the second refrigerant flow. It flows into the region B of the heat source side heat exchanger 8 via the path switching device 7, the sixth heat source side refrigerant pipe 26, the third header main pipe 85, and the plurality of third header branch pipes 86. .
  • the high-temperature and high-pressure gas refrigerant that has flowed into the heat source side heat exchanger 8 is heat-exchanged by releasing heat to a low-temperature medium such as outdoor air in the outdoor space 600 in FIG. 1, and the high-temperature and high-pressure gas refrigerant is condensed and liquefied. And high pressure liquid refrigerant.
  • the high-pressure liquid refrigerant condensed and liquefied in the region A of the heat source side heat exchanger 8 passes through the plurality of second header branch pipes 83 and the second header main pipe 84 to form a fourth heat source side refrigerant pipe. 24.
  • the high-pressure liquid refrigerant condensed and liquefied in the region B of the heat source side heat exchanger 8 passes through the fourth header branch pipe 87 and the fourth header main pipe 88 to the seventh heat source side. It flows into the refrigerant pipe 27.
  • the high-pressure liquid refrigerant flowing through the fourth heat source side refrigerant pipe 24 and the seventh heat source side refrigerant pipe 27 is joined by the connecting member 43 and flows into the eighth heat source side refrigerant pipe 28.
  • the high-pressure liquid refrigerant flowing through the eighth heat source side refrigerant pipe 28 flows into the inner pipe of the supercooling heat exchanger 10 and is heat-exchanged with the refrigerant flowing through the outer pipe of the supercooling heat exchanger 10 to be supercooled.
  • the high-pressure liquid refrigerant becomes a supercooled high-pressure liquid refrigerant and flows into the ninth heat source side refrigerant pipe 29.
  • the refrigerant flowing through the outer pipe of the supercooling heat exchanger 10 is divided by the branch portion 29a of the ninth heat source side refrigerant pipe 29, and the first heat source side branched refrigerant.
  • the liquid refrigerant or the two-phase refrigerant flows into the pipe 51 and is expanded and depressurized by the second heat source side decompression device 13 (for example, medium pressure).
  • the liquid refrigerant or the two-phase refrigerant that has been expanded and depressurized by the second heat source side pressure reducing device 13 (for example, medium pressure) is connected to the inner pipe of the supercooling heat exchanger 10 by the outer pipe of the supercooling heat exchanger 10. Heat exchange with the flowing high-pressure liquid refrigerant results in a high-temperature gas refrigerant or a two-phase refrigerant with high dryness.
  • the high-temperature gas refrigerant or the two-phase refrigerant having a high dryness flowing from the outer pipe of the supercooling heat exchanger 10 into the second heat source side branch refrigerant pipe 53 passes through the twelfth heat source side refrigerant pipe 32 to be an accumulator. 18 is injected.
  • the high-pressure liquid refrigerant that was supercooled by the supercooling heat exchanger 10 and flowed into the ninth heat source side refrigerant pipe 29 was expanded and depressurized by the first heat source side decompression device 12 to be depressurized (for example, (Pressure) liquid refrigerant or two-phase refrigerant.
  • the decompressed liquid refrigerant or two-phase refrigerant flows out of the outdoor unit 100 and flows into the indoor unit 200 via the first connection pipe 300.
  • the liquid refrigerant or the two-phase refrigerant that has flowed into the indoor unit 200 flows into the load-side decompression device 14 via the first load-side refrigerant pipe 35.
  • the liquid refrigerant or two-phase refrigerant that has flowed into the load-side decompression device 14 is further expanded and decompressed by the load-side decompression device 14 to become a low-temperature and low-pressure two-phase refrigerant.
  • the low-temperature and low-pressure two-phase refrigerant flows into the load-side heat exchanger 16 and is heat-exchanged by absorbing heat from a high-temperature medium such as indoor air in the indoor space 700 of FIG.
  • the gas is evaporated and becomes a two-phase refrigerant or gas refrigerant having a low temperature and low pressure and high dryness, and flows into the second load side refrigerant pipe 36.
  • the low-temperature and low-pressure two-phase refrigerant or low-temperature and low-pressure gas refrigerant that has flowed into the second load-side refrigerant pipe 36 flows out of the indoor unit 200 and passes through the second connecting pipe 400 to the outdoor unit. 100 flows in.
  • the low-temperature and low-pressure two-phase refrigerant or gas refrigerant flowing into the outdoor unit 100 includes a tenth heat source side refrigerant pipe 30, a first refrigerant flow switching device 6, an eleventh heat source side refrigerant pipe 31, and It is injected into the accumulator 18 via the twelfth heat source side refrigerant pipe 32.
  • the liquid phase component of the refrigerant injected from the twelfth heat source side refrigerant pipe 32 is separated and stored, and the low-temperature and low-pressure gas refrigerant flows into the thirteenth heat source side refrigerant pipe 33 from the accumulator 18, and the compressor 2 is inhaled.
  • the refrigerant sucked into the compressor 2 is compressed to become a high-temperature and high-pressure gas refrigerant and is discharged from the compressor 2.
  • the above cycle is repeated.
  • control processing of the control device 90 of the air-conditioning apparatus 1 according to Embodiment 1 in the first cooling operation mode will be described.
  • the control device 90 causes the refrigerant to flow through the refrigerant flow path inside the first refrigerant flow switching device 6 from the second heat source side refrigerant pipe 22 to the third heat source side refrigerant pipe 23, and the tenth heat source side refrigerant.
  • the pipe 30 communicates with the eleventh heat source side refrigerant pipe 31 so that the refrigerant flows.
  • the control device 90 causes the refrigerant flow path inside the second refrigerant flow switching device 7 to communicate so that the refrigerant flows from the fifth heat source side refrigerant pipe 25 to the sixth heat source side refrigerant pipe 26.
  • control device 90 causes the refrigerant flow path inside the second refrigerant flow switching device 7 to which the termination member 7a is connected to communicate with the twelfth heat source side refrigerant pipe 32, and the twelfth heat source side refrigerant pipe 32.
  • the refrigerant is prevented from flowing backward in the direction opposite to the inlet direction of the accumulator 18.
  • the controller 90 connects the refrigerant flow path of the flow path switching valve 55 provided in the seventh heat source side refrigerant pipe 27 from the seventh heat source side refrigerant pipe 27 on the fourth header main pipe 88 side.
  • the refrigerant is communicated with the seventh heat source side refrigerant pipe 27 on the 43 side so that the refrigerant flows.
  • control device 90 performs control to close the electromagnetic valve 63 and block the flow of high-pressure liquid refrigerant from the fourth heat source side branch refrigerant pipe 61 to the receiver 60. Further, the control device 90 opens the flow rate adjustment valve 67 to a predetermined opening degree (for example, when the fully open state opening degree of the flow rate adjustment valve 67 is 1 and the opening degree of the closed state is 0, the opening degree is about 1/8. And the refrigerant stored in the storage 60 a of the receiver 60 passes through the fifth heat source side branch refrigerant pipe 65 and the twelfth heat source side refrigerant pipe 32 due to the pressure difference generated by the flow rate adjustment valve 67. , Control to flow to the accumulator 18.
  • the cooling load is high and the amount of refrigerant used in the refrigeration cycle circuit is increased. Control is performed to return the refrigerant stored in the receiver 60 to the refrigeration cycle circuit.
  • the control device 90 calculates the saturation temperature (evaporation temperature) in the load-side heat exchanger 16 from the refrigerant suction pressure detected by the second pressure sensor 71.
  • the control device 90 subtracts the refrigerant temperature detected by the fourth temperature sensor 76 from the calculated evaporation temperature, calculates the degree of superheat in the refrigeration cycle circuit of the air conditioner 1, and the degree of superheat is a predetermined temperature range (for example, 5 ° C.), the opening degree of the load side decompression device 14 is controlled. Further, the control device 90 controls the operation frequency of the compressor 2 so that the evaporation temperature becomes the target temperature.
  • the target value of the evaporation temperature may be a fixed value (for example, ⁇ 30 ° C.), or an indoor temperature sensor (not shown) is arranged in the indoor space 700 of FIG. 1, and the temperature detected by the indoor temperature sensor and the user
  • the control device 90 may be configured to change the target temperature by calculating the maximum value of the set temperature difference set by the control device 90.
  • the “second cooling operation mode” means that the outside air temperature is less than the lower limit (for example, less than 25 ° C.) of the standard temperature range of the outside air temperature in the first cooling operation mode, and the indoor unit In the case where 200 operating capacity is less than the lower limit value of the standard operating capacity range (for example, operating capacity less than 50% of the total operating capacity) (in the cooling intermediate load condition), the first embodiment is used. The cooling operation performed with the air conditioning apparatus 1 which concerns is said.
  • FIG. 5 is a schematic refrigerant circuit diagram showing a refrigerant flow in the second cooling operation mode of the air-conditioning apparatus 1 according to Embodiment 1.
  • the flow direction of the refrigerant is indicated by solid arrows.
  • the air conditioner 1 is discharged from the compressor 2, passes through the oil separator 4, and the high-temperature high-pressure gas refrigerant flowing into the second heat source side refrigerant pipe 22 is the first Only the region A of the heat source side heat exchanger 8 passes through the refrigerant flow switching device 6, the third heat source side refrigerant pipe 23, the first header main pipe 81, and the plurality of first header branch pipes 82. Configured to flow into. That is, in the second cooling operation mode, the refrigerant flow inside the second refrigerant flow switching device 7 that communicates with the fifth heat source side refrigerant pipe 25 branched from the branch portion 22a of the second heat source side refrigerant pipe 22.
  • control processing of the control device 90 of the air-conditioning apparatus 1 according to Embodiment 1 in the second cooling operation mode will be described.
  • the control device 90 changes the refrigerant flow path in the first refrigerant flow switching device 6 from the second heat source side refrigerant pipe 22 to the third heat source side refrigerant pipe 23.
  • the refrigerant flows and communicates so that the refrigerant flows from the tenth heat source side refrigerant pipe 30 to the eleventh heat source side refrigerant pipe 31.
  • the control device 90 causes the refrigerant flow path inside the second refrigerant flow switching device 7 to which the termination member 7a is connected to communicate with the fifth heat source side refrigerant pipe 25 so that the high temperature and high pressure Control is performed so that the gas refrigerant does not flow into the region B of the heat source side heat exchanger 8.
  • control device 90 moves the refrigerant flow path of the flow path switching valve 55 provided in the seventh heat source side refrigerant pipe 27 from the seventh heat source side refrigerant pipe 27 to the third header main pipe 88 side.
  • the heat source side branch refrigerant pipe 57 is communicated so that the refrigerant flows.
  • the refrigerant that stays (sleeps) in the region B of the heat source side heat exchanger 8 is changed to the second heat source side branch refrigerant pipe 53, the third heat source side branch refrigerant pipe 57, And it can return to the accumulator 18 via the 12th heat source side refrigerant
  • the second cooling operation mode it is possible to prevent an increase in high pressure due to the refrigerant staying in the region B of the heat source side heat exchanger 8 (high stopping), and the compressor is reduced by reducing the high pressure. Therefore, the energy consumption of the air conditioner 1 can be reduced.
  • control of the operation frequency of the compressor 2 and the control of the opening degree of the load side pressure reducing device 14 in the control device 90 are the same as the control processing in the first cooling operation mode.
  • FIG. 6 is a flowchart illustrating an example of a control process in the second cooling operation mode in the control device 90 of the air-conditioning apparatus 1 according to Embodiment 1. It is assumed that the cooling operation in the first cooling operation mode is performed in the air conditioner 1 at the start of control processing of the electromagnetic valve 63 and the flow rate adjustment valve 67.
  • step S11 whether or not the outside air temperature T detected by the first temperature sensor 73 is less than the lower limit value T0 of the standard temperature range of the outside air temperature, or the operating capacity V of the indoor unit 200 is standard. It is determined in control device 90 whether or not the lower limit value V0 of the range of the correct operating capacity.
  • the lower limit value T0 of the standard temperature range of the outside air temperature is set to 25 ° C.
  • the lower limit value V0 of the standard operating capacity range is set to 50% of the total operating capacity.
  • the operation in the first cooling operation mode is continued, The determination process is performed regularly (for example, once an hour).
  • the outside temperature T detected by the first temperature sensor 73 is less than the lower limit value T0 of the standard temperature range of the outside temperature, or the operating capacity V of the indoor unit 200 is the lower limit of the standard operating capacity range.
  • the control device 90 opens the electromagnetic valve 63 and opens the flow rate adjustment valve 67 at a predetermined opening.
  • the predetermined opening is an opening at which the amount of refrigerant flowing out from the receiver 60 is smaller than the amount of refrigerant flowing into the receiver 60.
  • the refrigerant flows out from the outflow pipe 60c, the refrigerant is stored in the storage 60a of the receiver 60. The amount can be prevented from decreasing.
  • the opening degree of the flow rate adjusting valve 67 can be set to about 1/8 when the opening degree of the flow rate adjusting valve 67 is 1 and the opening degree of the closed state is 0.
  • the refrigerant temperature detected by the second temperature sensor 74 is subtracted from the saturation temperature (condensation temperature) calculated from the pressure detected by the first pressure sensor 70, thereby causing an excess in the heat source side heat exchanger 8.
  • the degree of cooling ⁇ T is calculated, and the opening degree of the flow rate adjusting valve 67 is controlled so that the degree of supercooling ⁇ T becomes a predetermined temperature width ⁇ T0 (for example, 3 ° C.).
  • step S ⁇ b> 12 the refrigerant can be stored in the storage 60 a of the receiver 60 by the dead weight of the refrigerant by opening the electromagnetic valve 63 and the pressure difference generated in the flow rate adjustment valve 67 by opening the flow rate adjustment valve 67.
  • step S13 the control device 90 subtracts the refrigerant temperature detected by the second temperature sensor 74 from the saturation temperature (condensation temperature) calculated from the pressure detected by the first pressure sensor 70.
  • the degree of supercooling ⁇ T in the heat source side heat exchanger 8 is calculated.
  • the control device 90 determines whether or not the degree of supercooling ⁇ T in the heat source side heat exchanger 8 is less than a predetermined temperature range ⁇ T0 (for example, 3 ° C.). That is, the control device 90 determines how much the refrigerant in the region A of the heat source side heat exchanger 8 becomes liquid refrigerant and exists in the refrigerant circuit as a surplus, based on the degree of supercooling ⁇ T in the heat source side heat exchanger 8. To do.
  • a predetermined temperature range ⁇ T0 for example, 3 ° C.
  • the predetermined temperature range ⁇ T0 may not be a fixed value.
  • the predetermined temperature range ⁇ T0 may be decreased as the value of the outside air temperature T detected by the first temperature sensor 73 decreases. Further, the predetermined temperature range ⁇ T0 may be decreased as the operating capacity of the indoor unit 200 decreases.
  • step S15 whether or not the outside air temperature T detected by the first temperature sensor 73 is less than the lower limit value T0 of the standard temperature range of the outside air temperature, or the operating capacity V of the indoor unit 200 is standard. It is determined in the control device 90 whether or not the lower limit value V0 of the operating capacity range.
  • the outside temperature T detected by the first temperature sensor 73 is less than the lower limit value T0 of the standard temperature range of the outside temperature, or the operating capacity V of the indoor unit 200 is the lower limit of the standard operating capacity range.
  • the control device 90 performs the determination process in step S13 again.
  • the outside temperature T detected by the first temperature sensor 73 is not less than the lower limit value T0 of the standard temperature range of the outside temperature, or the operating capacity V of the indoor unit 200 is the lower limit of the standard operating capacity range. If it is determined that the value is equal to or greater than V0, in step S17, the control device 90 closes the electromagnetic valve 63, opens the flow rate adjustment valve 67 at a predetermined opening degree, and the cooling operation is performed in the first cooling mode. Thus, the control process ends.
  • step S13 When it is determined in step S13 that the degree of supercooling ⁇ T is less than the predetermined temperature range ⁇ T0, the controller 90 closes the electromagnetic valve 63, closes the flow rate adjustment valve 67, and closes the receiver 60 in step S14.
  • the refrigerant is confined in the storage 60a.
  • the amount of refrigerant flowing through the area A of the heat source side heat exchanger 8 is an appropriate amount.
  • step S16 whether or not the outside air temperature T detected by the first temperature sensor 73 is less than the lower limit value T0 of the standard temperature range of the outside air temperature, or the operating capacity V of the indoor unit 200 is standard. It is determined in the control device 90 whether or not the lower limit value V0 of the operating capacity range.
  • the outside temperature T detected by the first temperature sensor 73 is less than the lower limit value T0 of the standard temperature range of the outside temperature, or the operating capacity V of the indoor unit 200 is the lower limit of the standard operating capacity range.
  • the control device 90 closes the electromagnetic valve 63 and maintains the flow rate adjustment valve 67, and the determination process of step S16 is performed again.
  • the outside temperature T detected by the first temperature sensor 73 is not less than the lower limit value T0 of the standard temperature range of the outside temperature, or the operating capacity V of the indoor unit 200 is the lower limit of the standard operating capacity range. If it is determined that the value is equal to or greater than V0, in step S17, the control device 90 closes the electromagnetic valve 63, opens the flow rate adjustment valve 67 at a predetermined opening degree, and the cooling operation is performed in the first cooling mode. Thus, the control process ends.
  • the air conditioner 1 includes a compressor 2 that compresses a refrigerant, and heat source side heat that is divided into a plurality of regions (for example, a region A and a region B) that perform heat exchange between the refrigerant and outside air.
  • Exchanger 8 a refrigerant flow switching device (first refrigerant flow switching) that changes the flow direction of refrigerant passing through the heat source side heat exchanger 8 divided into a plurality of regions (for example, region A and region B).
  • Device 6 second refrigerant flow switching device 7
  • a decompression device first heat source side decompression device 12, load side decompression device 14 for decompressing the refrigerant, and heat exchange between the refrigerant and the indoor space 700.
  • coolant piping 65) and the heat source side heat exchanger 8 and the load side heat exchanger 16 is provided.
  • a first valve for example, an electromagnetic valve 63
  • a refrigerant pipe fourth heat source side branch refrigerant pipe 61
  • a second valve for example, a flow rate adjusting valve 67
  • a refrigerant pipe for example, a refrigerant pipe 65
  • the cooling load of the heat exchanger 16 is smaller than a predetermined value, only the lower heat source side heat exchanger (part of the region A of the heat source side heat exchanger 8) of the heat source side heat exchanger 8 is used.
  • the receiver 60 includes a control device 90 that performs control for storing the refrigerant.
  • the control device 90 determines that the cooling load is small from the outside air temperature and the capacity of the indoor unit 200, and also determines that the amount of refrigerant in the heat source side heat exchanger 8 is large.
  • the refrigerant can be stored in the storage 60 a of the receiver 60 by opening the electromagnetic valve 63 and setting the flow rate adjustment valve 67 to a predetermined opening degree.
  • the air conditioner 1 of the first embodiment by storing the refrigerant in the storage 60a of the receiver 60, the refrigerant amount of the heat source side heat exchanger 8 is made appropriate, the high pressure is reduced, and the operating load of the compressor 2 ( Input) can be reduced.
  • the air conditioner 1 can be operated efficiently, and the air conditioner 1 that can reduce the energy consumption of the air conditioner 1 can be provided. Further, when the cooling load of the load side heat exchanger 16 is smaller than a predetermined value, the volume of the heat source side heat exchanger 8 through which the refrigerant flows can be reduced by using only the area A of the heat source side heat exchanger 8. Can be reduced.
  • the control device 90 sets the first valve (for example, the electromagnetic valve 63) when the cooling load of the load-side heat exchanger 16 is smaller than a predetermined value.
  • the second valve for example, the flow rate adjusting valve 67
  • the liquid refrigerant flowing from the heat source side heat exchanger 8 can be stored in the receiver 60 due to the weight of the refrigerant and the pressure difference between the receiver 60 and the suction side of the compressor 2.
  • FIG. 2 In the second embodiment of the present invention, a third cooling operation mode that is a modification of the cooling operation mode in the air-conditioning apparatus 1 according to the above-described first embodiment will be described.
  • the configuration of the air conditioner 1 and the operation of the refrigeration cycle circuit according to Embodiment 2 of the present invention are the same as those in the first cooling operation mode of Embodiment 1 described above.
  • the outside air temperature exceeds the upper limit (for example, 43 ° C.) of the standard temperature range of the outside air temperature in the first cooling operation mode, and the high pressure is standard.
  • a control process of the control device 90 of the air-conditioning apparatus 1 according to Embodiment 2 in the third cooling operation mode will be described.
  • the control device 90 the first refrigerant flow switching device 6, the second refrigerant flow switching device 7, the flow switching valve 55, the operating frequency of the compressor 2, and the opening degree of the load side pressure reducing device 14 are set.
  • the control is the same as the control process in the first cooling operation mode.
  • FIG. 7 is a flowchart illustrating an example of a control process in the third cooling operation mode in the control device 90 of the air-conditioning apparatus 1 according to Embodiment 2. It is assumed that the cooling operation in the first cooling operation mode is performed in the air conditioner 1 when the control process by the control device 90 is started.
  • step S21 whether or not the outside air temperature T detected by the first temperature sensor 73 exceeds the upper limit value T1 of the standard temperature range of the outside air temperature, and the high pressure detected by the first pressure sensor 70.
  • the controller 90 determines whether or not the pressure P exceeds the upper limit value P1 of the standard high pressure range.
  • the upper limit value T1 of the standard temperature range of the outside air temperature is set to 43 ° C.
  • the upper limit value P1 of the standard high pressure range is set to 36 kg / cm 2 .
  • the outside temperature T detected by the first temperature sensor 73 exceeds the upper limit value T1 of the standard temperature range of the outside temperature, and the high pressure P detected by the first pressure sensor 70 is the standard high pressure. If it is determined that the upper limit value P1 of the pressure range is exceeded, in step S22, the control device 90 opens the electromagnetic valve 63 and opens the flow rate adjustment valve 67 at a predetermined opening.
  • the predetermined opening is an opening at which the amount of refrigerant flowing out from the receiver 60 is smaller than the amount of refrigerant flowing into the receiver 60.
  • the refrigerant flows out from the outflow pipe 60c, the refrigerant is stored in the storage 60a of the receiver 60. Prevent the amount from decreasing.
  • the opening degree of the flow rate adjusting valve 67 can be set to about 1/8 when the opening degree of the flow rate adjusting valve 67 is 1 and the opening degree of the closed state is 0. Further, the opening degree of the flow rate adjustment valve 67 can be adjusted so that the value of the high pressure detected by the first pressure sensor 70 is reduced to the upper limit value P1 or less.
  • the refrigerant can be stored in the storage 60 a of the receiver 60 by the dead weight of the refrigerant by opening the electromagnetic valve 63 and the pressure difference generated in the flow rate adjustment valve 67 by opening the flow rate adjustment valve 67.
  • step S23 the controller 90 determines whether or not the high pressure P detected by the first pressure sensor 70 is equal to or lower than the upper limit value P1 of the standard high pressure range. When it is determined that the high pressure P detected by the first pressure sensor 70 exceeds the upper limit value P1 of the standard high pressure range, the control device 90 periodically performs the determination process in step S23.
  • step S24 the control device 90 closes the electromagnetic valve 63.
  • the flow regulating valve 67 is closed and the refrigerant is confined in the storage 60 a of the receiver 60.
  • step S25 the controller 90 determines whether or not the high pressure P detected by the first pressure sensor 70 is equal to or lower than the upper limit value P1 of the standard high pressure range.
  • the control device 90 performs the control process of step S22 and sets the electromagnetic valve 63.
  • the flow control valve 67 is opened at a predetermined opening.
  • step S25 determines whether or not the outside temperature T detected by the first temperature sensor 73 exceeds the upper limit value T1 of the standard temperature range of the outside temperature in step S26. Is determined by the control device 90. When it is determined that the outside air temperature T detected by the first temperature sensor 73 exceeds the upper limit value T1 of the standard temperature range of the outside air temperature, the control device 90 closes the electromagnetic valve 63 and the flow rate adjusting valve. 67 is kept closed, and the determination process in step S25 is periodically performed.
  • step S27 the control device 90 causes the electromagnetic valve 63 to Is closed, the flow rate adjustment valve 67 is opened at a predetermined opening, the cooling operation is in the first cooling mode, and the control process is terminated.
  • the control device 90 in the air-conditioning apparatus 1 has the cooling load on the load side heat exchanger 16 and the receiver 60 receives the air temperature when the outside air temperature is higher than a predetermined value. It controls to store the refrigerant.
  • the control device 90 determines that suppression of the high pressure is necessary based on the information on the outside air temperature by the first temperature sensor 73 and the information on the high pressure by the first pressure sensor 70.
  • the refrigerant can be stored in the storage 60 a of the receiver 60 by opening the electromagnetic valve 63 and setting the flow rate adjustment valve 67 to a predetermined opening.
  • the amount of refrigerant in the heat source side heat exchanger 8 is reduced, an increase in high pressure is suppressed, and air conditioning is caused by a high pressure abnormality (for example, a pressure of 38.5 kg / cm 2 or more).
  • the apparatus 1 can be prevented from abnormally stopping.
  • FIG. 8 is a schematic refrigerant circuit diagram illustrating a refrigerant flow in the heating operation mode of the air-conditioning apparatus 1 according to Embodiment 3.
  • the flow direction of the refrigerant is indicated by solid line arrows.
  • Compressor 2 sucks and compresses low-temperature and low-pressure refrigerant and discharges high-temperature and high-pressure gas refrigerant.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows from the outdoor unit 100 into the indoor unit 200 through the first refrigerant flow switching device 6.
  • the refrigerant flowing into the indoor unit 200 is condensed and liquefied while dissipating heat to the indoor space 700, and becomes a high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant is decompressed and expanded when passing through the load-side decompression device 14, and becomes a low-temperature and low-pressure (gas-liquid) two-phase refrigerant.
  • the two-phase refrigerant flows from the indoor unit 200 to the outdoor unit 100.
  • the refrigerant that has flowed into the outdoor unit 100 flows into the heat source side heat exchanger 8 (including both the region A and the region B) that functions as an evaporator.
  • the refrigerant that has flowed into the heat source side heat exchanger 8 absorbs heat from the outside air in the heat source side heat exchanger 8, and becomes a low-temperature and low-pressure gas refrigerant.
  • the low-temperature and low-pressure gas refrigerant that has flowed out of the heat source side heat exchanger 8 is again sucked into the compressor 2 via the first refrigerant flow switching device 6, the second refrigerant flow switching device 7, and the accumulator 18. .
  • control processing of the control device 90 of the air-conditioning apparatus 1 according to Embodiment 3 in the heating operation mode will be described.
  • the control device 90 causes the refrigerant to flow through the refrigerant flow path inside the first refrigerant flow switching device 6 from the second heat source side refrigerant pipe 22 to the tenth heat source side refrigerant pipe 30, and thereby the third heat source side refrigerant.
  • the pipe 23 is connected to the eleventh heat source side refrigerant pipe 31 so that the refrigerant flows.
  • the control device 90 causes the refrigerant flow path inside the second refrigerant flow switching device 7 to communicate so that the refrigerant flows from the sixth heat source side refrigerant pipe 26 to the twelfth heat source side refrigerant pipe 32.
  • the controller 90 connects the refrigerant flow path of the flow path switching valve 55 provided in the seventh heat source side refrigerant pipe 27 from the seventh heat source side refrigerant pipe 27 on the fourth header main pipe 88 side.
  • the refrigerant is communicated with the seventh heat source side refrigerant pipe 27 on the 43 side so that the refrigerant flows.
  • the control device 90 causes the refrigerant flow path inside the second refrigerant flow switching device 7 to which the termination member 7a is connected to communicate with the fifth heat source side refrigerant pipe 25 to thereby provide a fifth heat source side refrigerant pipe 25. The refrigerant flow is blocked.
  • control device 90 opens the electromagnetic valve 63 and fully opens the flow rate adjustment valve 67, thereby passing the inflow pipe 60 b of the receiver 60, the storage 60 a of the receiver 60, and the outflow pipe 60 c of the receiver 60 to the accumulator 18.
  • a refrigerant flow path for returning the refrigerant is formed. That is, the control device 90 opens the electromagnetic valve 63 and fully opens the flow rate adjustment valve 67, so that a part of the refrigerant that leaves the load side heat exchanger 16 and goes to the heat source side heat exchanger 8 is heated to the heat source side heat. Control is performed to return the refrigerant to the accumulator 18 without going through the exchanger 8.
  • the control device 90 calculates a saturation temperature (condensation temperature) in the load-side heat exchanger 16 from the pressure detected by the first pressure sensor 70.
  • the controller 90 subtracts the refrigerant temperature detected by the third temperature sensor 75 from the calculated condensation temperature, calculates the degree of supercooling in the refrigeration cycle circuit of the air conditioner 1, and the degree of supercooling is a predetermined temperature range. (For example, 5 degreeC)
  • the opening degree of the load side decompression device 14 is controlled. Further, the control device 90 controls the operating frequency of the compressor 2 so that the condensation temperature becomes the target temperature.
  • the target value of the condensation temperature may be a fixed value (for example, 30 ° C.), or an indoor temperature sensor (not shown) is arranged in the indoor space 700 of FIG.
  • the controller 90 may be configured to change the target temperature by calculating the maximum value of the set temperature difference to be set by the controller 90.
  • the 2nd heat-source side decompression device 13 may be open
  • the control device 90 is a part of the refrigerant that has come out of the load-side heat exchanger 16. Is returned to the compressor 2 via the receiver 60 without passing through the heat source side heat exchanger 8.
  • the pressure loss due to passing through the heat source side heat exchanger 8 can be reduced, so that the low pressure reduction can be suppressed, frost formation due to the low pressure reduction and the circulation amount discharged from the compressor 2 can be suppressed. Reduction can be suppressed.
  • Embodiment 4 FIG.
  • the refrigerant recovery mode when the refrigerant leaks into the indoor space 700 in the air-conditioning apparatus 1 according to the first embodiment described above will be described.
  • the configuration of the air-conditioning apparatus 1 and the operation of the refrigeration cycle circuit according to Embodiment 4 of the present invention are the same as those in the first cooling operation mode of Embodiment 1 described above.
  • a refrigerant leak signal is transmitted to the control device 90 via the transmission line 98.
  • the control device 90 passes through the first refrigerant flow switching device 6 and the second refrigerant flow switching device 7 of the outdoor unit 100 so that the refrigerant discharged from the compressor 2 flows into the heat source side heat exchanger 8. Switch to the same refrigerant flow path as in the first cooling operation mode.
  • the control device 90 moves the refrigerant flow path of the flow path switching valve 55 provided in the seventh heat source side refrigerant pipe 27 from the seventh heat source side refrigerant pipe 27 on the fourth header main pipe 88 side to the connection member 43.
  • the refrigerant is communicated with the seventh heat source side refrigerant pipe 27 so that the refrigerant flows.
  • the control device 90 opens the electromagnetic valve 63, and the flow rate adjustment valve 67 has a predetermined opening degree (for example, when the opening degree of the flow adjustment valve 67 is 1 and the opening degree of the closed state is 0, 1 / 8). Further, the control device 90 determines the flow rate adjustment valve based on the difference in the refrigerant temperature detected by the second temperature sensor 74 from the saturation temperature (condensation temperature) calculated from the pressure detected by the first pressure sensor 70. The opening degree of 67 can be changed. The first heat source side decompression device 12 is closed. The load side decompression device 14 is fully opened.
  • the compressor 2 sucks low-temperature and low-pressure refrigerant and discharges high-temperature and high-pressure gas refrigerant.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the heat source side heat exchanger 8 via the first refrigerant flow switching device 6 and the second refrigerant flow switching device 7. Since the first heat source side decompression device 12 is closed, the refrigerant is stored in the heat source side heat exchanger 8. Since there is no refrigerant flowing into the indoor unit 200, the refrigerant in the indoor unit 200 is collected by the outdoor unit 100. Further, the refrigerant collected in the outdoor unit 100 is also stored in the storage 60 a of the receiver 60 via the electromagnetic valve 63 and the inflow pipe 60 b of the receiver 60.
  • the control device 90 when the control device 90 detects that the refrigerant is leaking in the indoor space 700, the heat source side heat exchanger 8 and the receiver 60 Both are controlled to store the refrigerant.
  • the control device 90 when the indoor unit control device 95 detects refrigerant leakage from the refrigerant leakage detection sensor 78, the control device 90 supplies the refrigerant to the receiver 60 in addition to the heat source side heat exchanger 8. Can be stored. Therefore, according to the configuration of the fourth embodiment, in the refrigerant recovery mode, it is possible to recover a large amount of refrigerant in the outdoor unit 100 and reduce the refrigerant flowing out into the indoor space 700.
  • the installation position of the control device 90 is not particularly limited.
  • the outdoor unit 100 or the indoor unit 200 may be used.
  • the air conditioning apparatus 1 of the above-described embodiment may include two or more control devices 90.
  • the control device 90 closes the electromagnetic valve 63 in step S17 in the first cooling operation mode, the second cooling operation mode, or step S27 in the third cooling operation mode.
  • the electromagnetic valve 63 may be opened for a certain period.
  • the pressure difference generated by the flow rate adjustment valve 67 increases, so that the refrigerant stored in the storage 60 a of the receiver 60 is transferred to the fifth heat source side branch refrigerant pipe 65 and the twelfth heat source side refrigerant pipe 32. It is possible to increase the flow rate of the refrigerant flowing through the accumulator 18 via.

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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)
  • Air Conditioning Control Device (AREA)

Abstract

L'invention concerne un climatiseur comprenant : un circuit de cycle de réfrigération destiné à faire circuler un fluide frigorigène à travers des conduites reliant un compresseur, un échangeur de chaleur côté source de chaleur divisé en une pluralité de régions pour réaliser un échange de chaleur entre le fluide frigorigène et l'air extérieur, un dispositif de commutation de trajet d'écoulement de fluide frigorigène destiné à modifier la direction dans laquelle le fluide frigorigène s'écoule à travers l'échangeur de chaleur côté source de chaleur divisé en la pluralité de régions, un décompresseur et un échangeur de chaleur côté charge ; un récepteur destiné à stocker le fluide frigorigène, le récepteur se ramifiant depuis la conduite de fluide frigorigène entre l'échangeur de chaleur côté source de chaleur et l'échangeur de chaleur côté charge et étant prévu partiellement le long de la conduite de fluide frigorigène reliée au côté d'admission du compresseur ; une première soupape se ramifiant depuis la conduite de fluide frigorigène entre l'échangeur de chaleur côté source de chaleur et l'échangeur de chaleur côté charge, la première soupape étant prévue sur la conduite de fluide frigorigène reliée au côté d'écoulement d'entrée du récepteur ; une seconde soupape reliée au côté d'écoulement de sortie du récepteur, la seconde soupape étant prévue sur la conduite de fluide frigorigène reliée au côté d'écoulement d'entrée du compresseur ; et un dispositif de commande destiné à utiliser uniquement une partie de l'échangeur de chaleur côté source de chaleur lorsque la charge de refroidissement d'air de l'échangeur de chaleur côté charge est inférieure à une valeur prédéfinie, puis à commander le stockage du fluide frigorigène dans le récepteur.
PCT/JP2015/070441 2015-07-16 2015-07-16 Climatiseur WO2017010007A1 (fr)

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JP2017040464A (ja) * 2014-09-03 2017-02-23 三星電子株式会社Ｓａｍｓｕｎｇ Ｅｌｅｃｔｒｏｎｉｃｓ Ｃｏ．，Ｌｔｄ． 冷媒量検知装置
JP2019207088A (ja) * 2018-05-30 2019-12-05 株式会社前川製作所 ヒートポンプシステム
CN114110739A (zh) * 2020-08-28 2022-03-01 Lg电子株式会社 一拖多制冷制热空调机
CN114251719A (zh) * 2020-09-23 2022-03-29 Lg电子株式会社 制冷制热用一拖多空调机

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JP2008051425A (ja) * 2006-08-25 2008-03-06 Samsung Electronics Co Ltd 空気調和装置
JP2010127531A (ja) * 2008-11-27 2010-06-10 Mitsubishi Electric Corp 冷凍空調装置
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JPS6338865A (ja) * 1986-08-04 1988-02-19 三菱電機株式会社 冷凍サイクル装置
JPH02140574A (ja) * 1988-11-18 1990-05-30 Sanyo Electric Co Ltd 空気調和装置
JPH0350466A (ja) * 1989-07-14 1991-03-05 Sanyo Electric Co Ltd 冷暖房装置
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JP2017040464A (ja) * 2014-09-03 2017-02-23 三星電子株式会社Ｓａｍｓｕｎｇ Ｅｌｅｃｔｒｏｎｉｃｓ Ｃｏ．，Ｌｔｄ． 冷媒量検知装置
JP2019207088A (ja) * 2018-05-30 2019-12-05 株式会社前川製作所 ヒートポンプシステム
CN114110739A (zh) * 2020-08-28 2022-03-01 Lg电子株式会社 一拖多制冷制热空调机
US11892209B2 (en) 2020-08-28 2024-02-06 Lg Electronics Inc. Multi-air conditioner for heating and cooling including a shut-off valve between indoor and outdoor units and control method thereof
CN114110739B (zh) * 2020-08-28 2024-02-13 Lg电子株式会社 一拖多制冷制热空调机
CN114251719A (zh) * 2020-09-23 2022-03-29 Lg电子株式会社 制冷制热用一拖多空调机
US11898782B2 (en) 2020-09-23 2024-02-13 Lg Electronics Inc. Multi-air conditioner for heating and cooling operations

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