WO2021014520A1 - Air-conditioning device - Google Patents

Air-conditioning device Download PDF

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Publication number
WO2021014520A1
WO2021014520A1 PCT/JP2019/028595 JP2019028595W WO2021014520A1 WO 2021014520 A1 WO2021014520 A1 WO 2021014520A1 JP 2019028595 W JP2019028595 W JP 2019028595W WO 2021014520 A1 WO2021014520 A1 WO 2021014520A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
source side
heat source
side heat
refrigerant
Prior art date
Application number
PCT/JP2019/028595
Other languages
French (fr)
Japanese (ja)
Inventor
淳平 濱口
裕之 森本
隆直 木村
Original Assignee
三菱電機株式会社
Priority date (The priority date 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 date listed.)
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 CN201980098517.XA priority Critical patent/CN114127493B/en
Priority to PCT/JP2019/028595 priority patent/WO2021014520A1/en
Publication of WO2021014520A1 publication Critical patent/WO2021014520A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/41—Defrosting; Preventing freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/41—Defrosting; Preventing freezing
    • F24F11/42—Defrosting; Preventing freezing of outdoor units
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles

Definitions

  • the present invention relates to an air conditioner having three heat source side heat exchangers and capable of switching the refrigerant flow path of these three heat source side heat exchangers.
  • an air conditioner such as a multi air conditioner for a building
  • a pipe is provided between an outdoor unit (outdoor unit) which is a heat source unit arranged outside the building and an indoor unit (indoor unit) arranged inside the building.
  • outdoor unit outdoor unit
  • indoor unit indoor unit
  • the refrigerant circulates in the refrigerant circuit, and the indoor air is heated or cooled by utilizing the heat radiation or heat absorption of the refrigerant, so that the air-conditioned space is heated or cooled.
  • the plurality of heat exchangers are connected in parallel and the refrigerant flows. As a result, the pressure loss of the evaporator can be reduced, the performance of the evaporator is improved, and the heating performance is improved.
  • the heat exchanger is operated as a condenser when the defrosting operation is performed in order to prevent the evaporator from being frosted and the performance of the evaporator being deteriorated. At that time, since each heat exchanger is connected in series, the heat exchanger on the wake side may have insufficient defrosting ability.
  • the present invention has been made in view of the above circumstances, and an object of the present invention is to provide an air conditioner having improved defrosting ability when carrying out a defrosting operation.
  • the compressor, the refrigerant flow path switching device, the load side heat exchanger, the load side drawing device, the first heat source side heat exchanger, the second heat source side heat exchanger and the third heat source The main circuit in which the side heat exchangers are connected by pipes to circulate the refrigerant and the refrigerant flow paths of the first heat source side heat exchanger, the second heat source side heat exchanger, and the third heat source side heat exchanger are switched.
  • a heat exchanger flow path switching device for the purpose and a control device for controlling the heat exchanger flow path switching device are provided, and the control device includes the first heat source side heat exchanger and the second heat source side heat exchange.
  • the refrigerant flow of the first heat source side heat exchanger, the second heat source side heat exchanger and the third heat source side heat exchanger The heat exchanger flow path switching device is controlled so as to switch the path to the parallel refrigerant flow path, and the parallel refrigerant flow path is the first heat source side heat exchanger, the second heat source side heat exchanger, and the third.
  • the first heat source side heat exchanger, the second heat source side heat exchanger, and the third heat source side heat exchanger are connected in parallel to each other in a parallel refrigerant flow path. Since it is switched, it is possible to provide an air conditioner with improved defrosting ability.
  • FIG. It is a schematic circuit block diagram which shows an example of the circuit structure of the air conditioner 100 which concerns on Embodiment 1.
  • FIG. It is a refrigerant circuit diagram which shows the flow of the refrigerant in the cooling operation mode of the air conditioner 100 which concerns on Embodiment 1.
  • FIG. It is a refrigerant circuit diagram which shows the flow of the refrigerant in the heating operation mode of the air conditioner 100 which concerns on Embodiment 1.
  • FIG. It is a refrigerant circuit diagram which shows the flow of the refrigerant in the defrost operation mode of the air conditioner 100 which concerns on Embodiment 1.
  • FIG. It is a flowchart for demonstrating operation of the control device of the air conditioner 100 which concerns on Embodiment 1.
  • FIG. 1 is a schematic circuit configuration diagram showing an example of the circuit configuration of the air conditioner 100 according to the first embodiment.
  • the air conditioner 100 shown in FIG. 1 has a configuration in which an outdoor unit 1 and an indoor unit 2 are connected by a first main pipe 4a and a second main pipe 4b.
  • FIG. 1 shows an example in which one indoor unit 2 is connected to the outdoor unit 1 via the first main pipe 4a and the second main pipe 4b.
  • the number of indoor units 2 connected to the outdoor unit 1 is not limited to one, and a plurality of indoor units may be connected.
  • the outdoor unit 1 includes a compressor 10, a first four-way valve 11, a second four-way valve 12, a first heat source side heat exchanger 13a, and a second heat source side heat exchanger 13b as components of the main circuit. , And a third heat source side heat exchanger 13c.
  • the first four-way valve 11 and the second four-way valve 12 correspond to the refrigerant flow path switching device.
  • the main circuits are the compressor 10, the first four-way valve 11, the second four-way valve 12, the load side heat exchanger 21, the load side throttle device 22, the first heat source side heat exchanger 13a, and the second heat source side heat exchanger 13b.
  • the third heat source side heat exchanger 13c are sequentially connected by the refrigerant pipe 3, and the refrigerant circulates.
  • the refrigerant pipe 3 is a general term for pipes for circulating the refrigerant used in the air conditioner 100.
  • the refrigerant pipe 3 includes, for example, a first main pipe 4a, a second main pipe 4b, a first main pipe 5a, a second main pipe 5b, a series parallel switching pipe 6, a series outlet pipe 7, a parallel inlet / outlet pipe 8, and a first inlet / outlet pipe 9a.
  • heat source side heat exchanger other heat source side heat exchangers may be provided in addition to the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c. ..
  • the first main pipe 4a and the second main pipe 4b connect the outdoor unit 1 and the indoor unit 2.
  • the first main pipe 5a connects the first four-way valve 11 and the first header 14a.
  • the second main pipe 5b connects the second four-way valve 12 and the second header 14b.
  • the series-parallel switching pipe 6 joins the fourth header 14d and the second header 14b and connects to the second four-way valve 12 via the second main pipe 5b. That is, the series-parallel switching pipe 6 connects the second header 14b and the fourth header 14d.
  • the parallel inlet / outlet pipe 8 is connected to the first inlet / outlet pipe 9a, the second inlet / outlet pipe 9b, and the third inlet / outlet pipe 9c, respectively, and connects to the second main pipe 4b leading to the load side throttle device 22.
  • the series outlet pipe 7 connects the connection portion in which the series / parallel switching pipe 6 and the fourth header 14d are connected and the second main pipe 4b leading to the load side throttle device 22.
  • the outdoor unit 1 has a first switchgear 31, a second switchgear 32, a first opening / closing device 33 capable of adjusting a Cv value, and a second opening / closing device 33 as heat exchanger flow path switching devices. It has an adjusting device 34 and.
  • the outdoor unit 1 is equipped with a fan 16 which is a blower.
  • the fan 16 includes a top flow type or first heat source side heat exchanger 13a located above the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c.
  • a side flow method or the like located on the side of the two heat source side heat exchangers 13b and the third heat source side heat exchanger 13c is adopted.
  • the compressor 10 sucks in the refrigerant and compresses it into a high temperature and high pressure state.
  • the compressor 10 is composed of, for example, an inverter compressor whose capacity can be controlled.
  • the compressor 10 uses, for example, a low-pressure shell structure having a compression chamber in a closed container, the inside of the closed container having a low-pressure refrigerant pressure atmosphere, and sucking and compressing the low-pressure refrigerant in the closed container.
  • the first four-way valve 11 and the second four-way valve 12 switch between the refrigerant flow path in the cooling operation mode and the defrosting operation mode and the refrigerant flow path in the heating operation mode.
  • the cooling operation mode is a case where at least one of the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c is used as a condenser or a gas cooler.
  • the first embodiment has a cooling operation mode and a heating operation mode.
  • the heating operation mode is a case where the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as the evaporator.
  • the first four-way valve 11 supplies or shuts off the refrigerant discharged from the compressor 10 to the first heat source side heat exchanger 13a.
  • the second four-way valve 12 supplies the refrigerant discharged from the compressor 10 to either the second heat source side heat exchanger 13b, the third heat source side heat exchanger 13c, or the load side heat exchanger 21.
  • the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c include a plurality of heat transfer tubes which are heat exchanger components and a plurality of heat exchanger components. It has fins and.
  • Multiple heat transfer tubes are flat tubes or circular tubes, respectively.
  • the plurality of heat transfer tubes extend in the horizontal direction.
  • the plurality of heat transfer tubes form a plurality of refrigerant flow paths in the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c.
  • the plurality of fins are plate-shaped and are stacked at predetermined intervals.
  • the plurality of fins extend in the vertical direction which is orthogonal to the extending direction of the heat transfer tube, and the plurality of heat transfer tubes are inserted therethrough.
  • the first heat source side heat exchanger 13a is arranged independently of the second heat source side heat exchanger 13b and the third heat source side heat exchanger 13c.
  • the second heat source side heat exchanger 13b is arranged above the third heat source side heat exchanger 13c on the vertical line.
  • the first heat source side heat exchanger 13a is provided with one first header 14a and one first distributor 15a.
  • the second heat source side heat exchanger 13b is arranged above the vertical line of the third heat source side heat exchanger 13c.
  • a part of the second heat source side heat exchanger 13b is integrally formed with the third heat source side heat exchanger 13c by sharing fins which are heat exchanger components. That is, a part of the second heat source side heat exchanger 13b and a part of the third heat source side heat exchanger 13c have their heat transfer tubes inserted into the same fins.
  • the remaining part other than a part of the second heat source side heat exchanger 13b is configured independently of the third heat source side heat exchanger 13c. That is, the heat transfer tubes are inserted into different fins except for a part of the second heat source side heat exchanger 13b and a part of the third heat source side heat exchanger 13c.
  • the second heat source side heat exchanger 13b is provided with one second header 14b and one second distributor 15b.
  • the third heat source side heat exchanger 13c is provided with one third header 14c and one fourth header 14d.
  • the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c function as a condenser in the cooling operation mode and the defrosting operation mode, and an evaporator in the heating operation mode. It functions as.
  • the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c exchange heat between the air supplied from the fan 16 and the refrigerant flowing through the plurality of heat transfer tubes. I do.
  • In the cooling operation mode depending on the various modes, only all or a part of the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c function as a condenser.
  • the total heat transfer area of the heat transfer area of the first heat source side heat exchanger 13a and the heat transfer area of the second heat source side heat exchanger 13b is calculated from the heat transfer area of the third heat source side heat exchanger 13c. Is also formed to be large. Therefore, the number of sums of the number of heat transfer tubes of the first heat source side heat exchanger 13a and the second heat source side heat exchanger 13b is larger than the number of heat transfer tubes of the third heat source side heat exchanger 13c.
  • the first header 14a is a refrigerant flow path on the inlet side of the first heat source side heat exchanger 13a when the first heat source side heat exchanger 13a is used as a condenser in the cooling operation mode and the defrosting operation mode. It is provided at the position where
  • the first header 14a has a plurality of branch pipes, which are thin pipes connected to the heat transfer pipes of the first heat source side heat exchanger 13a, and a main pipe to which the plurality of branch pipes are connected.
  • the main pipe is connected to the first main pipe 5a which is connected to the first four-way valve 11.
  • the upper part of the main pipe is connected to the first main pipe 5a.
  • the first header 14a contains a plurality of refrigerants that have flowed into the main pipe from the first main pipe 5a when the first heat source side heat exchanger 13a is used as a condenser in the cooling operation mode and the defrosting operation mode. It flows into the first heat source side heat exchanger 13a through the branch pipe.
  • the first header 14a allows the refrigerant flowing out from the first heat source side heat exchanger 13a to a plurality of branch pipes to flow through the main pipe to the first main pipe 5a. To leak to.
  • the second header 14b is a refrigerant flow path on the inlet side of the second heat source side heat exchanger 13b when the second heat source side heat exchanger 13b is used as a condenser in the cooling operation mode and the defrosting operation mode. It is provided at the position where The second header 14b has a plurality of branch pipes, which are thin pipes connected to the heat transfer pipes of the second heat source side heat exchanger 13b, and a main pipe to which the plurality of branch pipes are connected.
  • the main pipe is connected to the second main pipe 5b which is connected to the second four-way valve 12.
  • the lower part of the main pipe is connected to the second main pipe 5b.
  • the second header 14b contains a plurality of refrigerants that have flowed into the main pipe from the second main pipe 5b when the second heat source side heat exchanger 13b is used as a condenser in the cooling operation mode and the defrosting operation mode. It flows into the second heat source side heat exchanger 13b through the branch pipe.
  • the second header 14b allows the refrigerant flowing out from the second heat source side heat exchanger 13b to a plurality of branch pipes to flow through the main pipe to the second main pipe 5b. To leak to.
  • the third header 14c is located at a position that serves as a refrigerant flow path on the inlet side of the third heat source side heat exchanger 13c when the third heat source side heat exchanger 13c is used as a condenser or an evaporator in the cooling operation mode. It is provided.
  • the third header 14c has a plurality of branch pipes, which are thin pipes connected to the heat transfer pipes of the third heat source side heat exchanger 13c, and a main pipe to which the plurality of branch pipes are connected.
  • the main pipe is connected to the parallel entrance / exit pipe 8.
  • the lower part of the main pipe is connected to the parallel inlet / outlet pipe 8.
  • the third header 14c is a third heat source through a plurality of branch pipes, when the third heat source side heat exchanger 13c is used as a condenser or an evaporator in the cooling mode, the refrigerant flowing into the main pipe from the parallel inlet / outlet pipe 8 is used. It flows into the side heat exchanger 13c.
  • the third header 14c allows the refrigerant flowing out from the third heat source side heat exchanger 13c to the plurality of branch pipes through the main pipe when the third heat source side heat exchanger 13c is used as a condenser in the defrosting operation mode. It flows out to the parallel entrance / exit pipe 8.
  • the fourth header 14d is provided at a position that serves as a refrigerant flow path on the inlet side of the third heat source side heat exchanger 13c when the third heat source side heat exchanger 13c is used as a condenser in the defrosting operation mode. ing.
  • the fourth header 14d has a plurality of branch pipes, which are thin pipes connected to the heat transfer pipes of the third heat source side heat exchanger 13c, and a main pipe to which the plurality of branch pipes are connected.
  • the main pipe is connected to the series-parallel switching pipe 6 and the series outlet pipe 7.
  • the lower part of the main pipe is connected to the series-parallel switching pipe 6 and the series outlet pipe 7.
  • the fourth header 14d receives the refrigerant flowing out from the third heat source side heat exchanger 13c into a plurality of branch pipes when the third heat source side heat exchanger 13c is used as a condenser and an evaporator in the cooling operation mode. It flows out to the series-parallel switching pipe 6 through the main pipe.
  • the first distributor 15a is provided at a position that serves as a refrigerant flow path on the inlet side of the first heat source side heat exchanger 13a when the first heat source side heat exchanger 13a is used as an evaporator.
  • the first distributor 15a has a plurality of thin pipes connected to the heat transfer tubes of the first heat source side heat exchanger 13a, and a main body which is a confluence portion in which the plurality of thin pipes are merged into one. ing.
  • the main body is connected to the first entrance / exit pipe 9a connected to the parallel entrance / exit pipe.
  • the first distributor 15a allows the refrigerant flowing out from the first heat source side heat exchanger 13a to a plurality of thin pipes to flow through the main body to the first inlet / outlet pipe 9a. Leak to.
  • the first distributor 15a allows the refrigerant flowing into the main body from the first inlet / outlet pipe 9a to pass through a plurality of thin pipes to the first heat source side heat exchanger 13a. Inflow to.
  • the second distributor 15b is provided at a position that serves as a refrigerant flow path on the inlet side of the second heat source side heat exchanger 13b when the second heat source side heat exchanger 13b is used as an evaporator.
  • the second distributor 15b has a plurality of thin pipes connected to the heat transfer tubes of the second heat source side heat exchanger 13b, and a main body which is a confluence portion in which the plurality of thin pipes are merged into one. ing.
  • the main body is connected to a second entrance / exit pipe 9b connected to a parallel entrance / exit pipe.
  • the second distributor 15b allows the refrigerant flowing out from the second heat source side heat exchanger 13b to a plurality of thin pipes to flow through the main body to the second inlet / outlet pipe 9b. Leak to.
  • the second distributor 15b allows the refrigerant flowing into the main body from the second inlet / outlet pipe 9b to pass through the plurality of thin pipes to the second heat source side heat exchanger 13b. Inflow to.
  • the series-parallel switching pipe 6 connects the fourth header 14d, the second header 14b, and the second main pipe 5b.
  • the series-parallel switching pipe 6 sends the refrigerant flowing out from the fourth header 14d to the outlet of the second header 14b via the first opening degree adjusting device 33. Let the refrigerant flow out.
  • the series-parallel switching pipe 6 is provided with a first opening degree adjusting device 33.
  • the first entrance / exit pipe 9a connects the first distributor 15a and the parallel entrance / exit pipe 8.
  • the first inlet / outlet pipe 9a is in a two-phase state with low dryness when the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as evaporators.
  • the liquid low-pressure refrigerant flows into the first heat source side heat exchanger 13a via the first distributor 15a.
  • the second entrance / exit pipe 9b connects the second distributor 15b and the parallel entrance / exit pipe 8.
  • the second inlet / outlet pipe 9b is in a two-phase state with low dryness when the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as evaporators.
  • the liquid low-pressure refrigerant flows into the second heat source side heat exchanger 13b via the second opening degree adjusting device 34 and the second distributor 15b.
  • a second opening degree adjusting device 34 is provided in the second entrance / exit pipe 9b.
  • the third entrance / exit pipe 9c connects the third header 14c and the parallel entrance / exit pipe 8.
  • the third inlet / outlet pipe 9c is in a two-phase state with low dryness when the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as evaporators.
  • the liquid low-pressure refrigerant flows into the third heat source side heat exchanger 13c via the third header 14c.
  • the parallel inlet / outlet pipe 8 connects the first inlet / outlet pipe 9a, the second inlet / outlet pipe 9b, and the third inlet / outlet pipe 9c to the second main pipe 4b.
  • the parallel inlet / outlet pipe 8 is in a two-phase state or liquid with low dryness when the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as evaporators.
  • the low-pressure refrigerant in the state is branched into the first inlet / outlet pipe 9a, the second inlet / outlet pipe 9b, and the third inlet / outlet pipe 9c via the first opening / closing device 31.
  • the parallel entrance / exit pipe 8 is provided with a first switchgear 31.
  • the series outlet pipe 7 connects the fourth header 14d and the second main pipe 4b via the second switchgear 32.
  • the series outlet pipe 7 is a second opening / closing device when the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as a condenser in the cooling operation mode.
  • a high-pressure liquid refrigerant flows into the second main pipe 4b via the 32.
  • the series outlet pipe 7 is provided with a second switchgear 32.
  • the first switchgear 31 is arranged in the parallel inlet / outlet pipe 8 and passes or shuts off the refrigerant flowing from the second main pipe 4b into the parallel inlet / outlet pipe 8. That is, the first opening / closing device 31 is closed so that the refrigerant flowing out from the first heat source side heat exchanger 13a and the second heat source side heat exchanger 13b does not flow into the second main pipe 4b in the cooling operation mode. Further, in the heating operation mode, the refrigerant flowing out from the second main pipe 4b is opened so as to flow into the parallel inlet / outlet pipe 8.
  • the refrigerant flowing out from the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c is opened so as to flow into the second main pipe 4b.
  • the first switchgear 31 is an on-off valve, and is configured to open and close the flow path of the refrigerant such as a two-way valve, a solenoid valve, and an electronic expansion valve.
  • the second switchgear 32 is arranged in the series outlet pipe 7 and passes or shuts off the refrigerant flowing through the series outlet pipe 7. That is, the second switchgear 32 is opened so that the refrigerant flowing out of the fourth header 14d flows into the second main pipe in the cooling operation mode. Further, in the heating operation mode, the refrigerant flowing out from the second main pipe does not pass through the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c to the second main pipe 5b. It is closed so that it does not flow in. Further, in the defrosting operation mode, the refrigerant flowing out from the second main pipe is closed so as not to flow out to the second main pipe without passing through the second heat source side heat exchanger 13b and the third heat source side heat exchanger 13c.
  • the second switchgear 32 is an on-off valve, and is configured to open and close the flow path of the refrigerant such as a two-way valve, a solenoid valve, and an electronic expansion valve.
  • the first opening degree adjusting device 33 is arranged in the series-parallel switching pipe 6 and passes or shuts off the refrigerant flowing through the series-parallel switching pipe 6. That is, the first opening degree adjusting device 33 is closed so that the high temperature and high pressure refrigerant does not flow into the third heat source side heat exchanger 13c in the cooling operation mode. Further, in the heating operation mode, the Cv value is adjusted in order to adjust the amount of the refrigerant flowing into the third heat source side heat exchanger 13c from the parallel inlet / outlet pipe. Further, in the defrosting operation mode, the high-temperature and high-pressure refrigerant is opened so as to flow into the third heat source side heat exchanger 13c.
  • the first opening degree adjusting device 33 is composed of a throttle device capable of adjusting the flow rate of the refrigerant by changing the opening degree of, for example, an electronic expansion valve.
  • the second opening / closing adjusting device 34 is arranged in the second inlet / outlet pipe 9b, and passes or shuts off the refrigerant flowing through the second inlet / outlet pipe 9b. That is, the second opening degree adjusting device 34 is opened so that the refrigerant flowing out from the second heat source side heat exchanger 13b flows into the parallel inlet / outlet pipe 8 in the cooling operation mode. Further, in the heating operation mode, the Cv value is adjusted in order to adjust the amount of the refrigerant flowing into the second heat source side heat exchanger 13b from the parallel inlet / outlet pipe. Further, in the defrosting operation mode, the refrigerant flowing out from the second heat source side heat exchanger 13b is opened so as to flow into the parallel inlet / outlet pipe 8.
  • the second opening degree adjusting device 34 is composed of a throttle device capable of adjusting the flow rate of the refrigerant by changing the opening degree of, for example, an electronic expansion valve.
  • the indoor unit 2 has a load-side heat exchanger 21 and a load-side throttle device 22 as components of the main circuit.
  • the load side heat exchanger 21 is connected to the outdoor unit 1 via the first main pipe 4a and the second main pipe 4b.
  • the load-side heat exchanger 21 exchanges heat between the air leading to the indoor space and the refrigerant flowing through the first main pipe 4a or the second main pipe 4b, and supplies heating air or cooling to the indoor space. Generates air for use. Indoor air is blown to the load side heat exchanger 21 from a blower such as a fan (not shown).
  • the load-side throttle device 22 is composed of, for example, an electronic expansion valve whose opening degree is mutably controlled, has a function as a pressure reducing valve or an expansion valve, and decompresses and expands the refrigerant. ..
  • the load-side throttle device 22 is provided on the upstream side of the load-side heat exchanger 21 in the cooling operation mode and the defrosting operation mode.
  • the control device 60 is composed of a microcomputer or the like and is provided in the outdoor unit 1, and controls various devices of the air conditioner 100 based on the detection information detected by various sensors and the instruction from the remote controller.
  • the objects controlled by the control device 60 are the drive frequency of the compressor 10, the rotation speed including ON or OFF of the fan 16, the switching of the first four-way valve 11, the switching of the second four-way valve 12, and the opening and closing of the first switchgear 31. , Opening / closing of the second opening / closing device 32, opening / closing / opening / closing of the first opening / closing device 33, opening / closing / opening / closing of the second opening / closing device 34, opening / closing of the load side throttle device 22 and the like. By controlling various devices in this way, the control device 60 executes each operation mode described later.
  • the control device 60 is composed of dedicated hardware or a CPU (also referred to as a central processing unit, a processing unit, an arithmetic unit, a microprocessor, a microprocessor, or a processor) that executes a program stored in a memory. ..
  • a CPU also referred to as a central processing unit, a processing unit, an arithmetic unit, a microprocessor, a microprocessor, or a processor
  • the control device 60 corresponds to, for example, a single circuit, a composite circuit, an ASIC (Application Specific Integrated Circuit), an FPGA (Field Programmable Gate Array), or a combination thereof.
  • ASIC Application Specific Integrated Circuit
  • FPGA Field Programmable Gate Array
  • each function executed by the control device 60 is realized by software, firmware, or a combination of software and firmware.
  • Software and firmware are written as programs and stored in memory.
  • the CPU realizes each function of the control device 60 by reading and executing a program stored in the memory.
  • the memory is a non-volatile or volatile semiconductor memory such as a RAM, a ROM, a flash memory, an EPROM, or an EEPROM. It should be noted that a part of the functions of the control device 60 may be realized by dedicated hardware, and a part may be realized by software or firmware.
  • control device 60 is provided in the outdoor unit 1 .
  • control device may be provided for each unit or may be provided in the indoor unit 2.
  • each operation mode executed by the air conditioner 100 performs a cooling operation mode or a heating operation mode based on an instruction from the indoor unit 2, and a defrosting operation mode based on an instruction from the control device 60.
  • the operation modes executed by the air conditioner 100 shown in FIG. 1 include three cooling operation modes in which the driving indoor unit 2 executes the cooling operation, and the driving indoor unit 2 executes the heating operation. There is a heating operation mode and a defrosting operation mode in which the driving air conditioner 100 executes a defrosting operation.
  • FIG. 2 is a refrigerant circuit diagram showing the flow of the refrigerant in the cooling operation mode of the air conditioner 100 according to the first embodiment.
  • FIG. 2 the flow of the refrigerant in the heavy load cooling operation mode will be described by taking the case where a large cooling heat load is generated in the load side heat exchanger 21 as an example.
  • the flow direction of the refrigerant is indicated by a solid arrow.
  • the low-temperature and low-pressure refrigerant is compressed by the compressor 10 and discharged as a high-temperature and high-pressure gas refrigerant.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 branches into the first four-way valve 11 and the second four-way valve 12 and flows in. Then, the refrigerant that has flowed into the first four-way valve 11 flows into the first heat source side heat exchanger 13a through the first main pipe 5a.
  • the refrigerant flowing into the second four-way valve 12 flows into the second heat source side heat exchanger 13b through the second main pipe 5b.
  • the first opening degree adjusting device 33 is switched to the closed state. Therefore, the high-temperature and high-pressure gas refrigerant flowing through the second main pipe 5b does not flow into the third heat source side heat exchanger 13c via the series-parallel switching pipe 6.
  • the gas refrigerant flowing into the first heat source side heat exchanger 13a becomes a high-pressure two-phase or liquid refrigerant while radiating heat to the outdoor air supplied from the fan 16 by the first heat source side heat exchanger 13a. Further, the gas refrigerant flowing into the second heat source side heat exchanger 13b becomes a high-pressure two-phase or liquid refrigerant while radiating heat to the outdoor air supplied from the fan 16 by the second heat source side heat exchanger 13b.
  • the high-pressure two-phase or liquid refrigerant flowing out of the first heat source side heat exchanger 13a flows into the parallel inlet / outlet pipe 8 through the first inlet / outlet pipe 9a. Further, the high-pressure two-phase or liquid refrigerant flowing out from the second heat source side heat exchanger 13b flows into the parallel inlet / outlet pipe 8 through the second inlet / outlet pipe 9b. As a result, the high-pressure two-phase or liquid refrigerant flowing out of the first heat source side heat exchanger 13a and the high-pressure two-phase or liquid refrigerant flowing out of the second heat source side heat exchanger 13b merge at the parallel inlet / outlet pipe 8. To do. At this time, the first switchgear 31 is switched to the closed state. Therefore, the high-pressure two-phase or liquid refrigerant flowing out of the first heat source side heat exchanger 13a or the second heat source side heat exchanger 13b does not flow into the second main pipe 4b via the parallel inlet / outlet pipe 8.
  • the combined high-pressure two-phase or liquid refrigerant flows into the third heat source side heat exchanger 13c. Then, the inflowing high-pressure two-phase or liquid refrigerant becomes a high-pressure liquid refrigerant while radiating heat to the outdoor air supplied from the fan 16 by the third heat source side heat exchanger 13c.
  • This high-pressure liquid refrigerant flows out from the outdoor unit 1 through the series outlet pipe 7 in which the second switchgear 32 switched to the open state is arranged, passes through the second main pipe 4b, and flows into the indoor unit 2.
  • the first heat source side heat exchanger 13a and the second heat source side heat exchanger 13b are parallel to each other on the upstream side, and the first heat source side heat is on the downstream side.
  • the third heat source side heat exchanger 13c is connected in series to the exchanger 13a and the second heat source side heat exchanger 13b.
  • the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as condensers, and the first four-way valve 11 is used from the compressor 10.
  • the discharged refrigerant is supplied to the first heat source side heat exchanger 13a, the refrigerant discharged from the compressor 10 by the second four-way valve 12 is supplied to the second heat source side heat exchanger 13b, and the first opening / closing device 31 is operated.
  • the second opening / closing device 32 is opened, the first opening / closing adjusting device 33 is closed, and the second opening / closing adjusting device 34 is opened.
  • the high-pressure liquid refrigerant is expanded by the load-side throttle device 22 to become a low-temperature low-pressure gas-liquid two-phase state refrigerant.
  • the gas-liquid two-phase state refrigerant flows into the load side heat exchanger 21 used as an evaporator and absorbs heat from the indoor air to become a low-temperature low-pressure gas refrigerant while cooling the indoor air.
  • the opening degree of the load side throttle device 22 is controlled by the control device 60 so that the degree of superheat becomes constant.
  • the gas refrigerant flowing out of the load side heat exchanger 21 flows into the outdoor unit 1 again through the first main pipe 4a.
  • the gas refrigerant that has flowed into the outdoor unit 1 is sucked into the compressor 10 again through the second four-way valve 12.
  • the third heat source side heat exchanger 13c is connected to the first heat source side heat exchanger 13a and the second heat source side heat exchanger 13b as a series refrigerant flow path.
  • the flow velocity of the refrigerant increases, and the performance of the condenser can be improved.
  • the flow velocity of the refrigerant is slow, it is possible to prevent the refrigerant from accumulating as a liquid refrigerant in the third heat source side heat exchanger 13c on the downstream side.
  • first heat source side heat exchanger 13a is independently arranged without division, and is provided with one first header 14a and one first distributor 15a.
  • second heat source side heat exchanger 13b and the third heat source side heat exchanger 13c are partially integrally configured.
  • the second heat source side heat exchanger 13b is provided with one second header 14b and one second distributor 15b.
  • the third heat source side heat exchanger 13c is provided with one third header 14c and one fourth header 14d. Therefore, the cost can be suppressed and the installation space can be narrowed as compared with the configuration in which two or more headers and distributors are provided in one heat source side heat exchanger.
  • the volume ratio between the upstream side and the downstream side is such that the inflow refrigerant of the third heat source side heat exchanger 13c on the downstream side becomes a refrigerant with low dryness. This is to adjust.
  • FIG. 3 is a refrigerant circuit diagram showing the flow of the refrigerant in the heating operation mode of the air conditioner 100 according to the first embodiment.
  • FIG. 3 the flow of the refrigerant in the heating operation mode will be described by taking as an example a case where a thermal load is generated in the load side heat exchanger 21.
  • the flow direction of the refrigerant is indicated by a solid arrow.
  • the low-temperature and low-pressure refrigerant is compressed by the compressor 10 and discharged as a high-temperature and high-pressure gas refrigerant.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 passes through the second four-way valve 12 and flows out from the outdoor unit 1.
  • the high-temperature and high-pressure gas refrigerant flowing out of the outdoor unit 1 passes through the first main pipe 4a and is dissipated to the indoor air by the load side heat exchanger 21 to become a liquid refrigerant while heating the indoor space.
  • the opening degree of the load side throttle device 22 is controlled by the control device 60 so that the degree of supercooling becomes constant.
  • the liquid refrigerant flowing out from the load side heat exchanger 21 is expanded by the load side throttle device 22 to become a gas-liquid two-phase state refrigerant at medium temperature and medium pressure, and passes through the second main pipe 4b to the outdoor unit 1 again. Inflow.
  • the medium-temperature, medium-pressure, gas-liquid, two-phase refrigerant that has flowed into the outdoor unit 1 passes through the first switchgear 31 that has been switched to the open state, and flows into the parallel inlet / outlet pipe 8.
  • the refrigerant flowing into the parallel inlet / outlet pipe 8 flows into the first inlet / outlet pipe 9a, the second inlet / outlet pipe 9b, and the third inlet / outlet pipe 9c in parallel, and flows into the first heat source side heat exchanger 13a and the second heat source side heat exchanger, respectively. It flows into 13b and the third heat source side heat exchanger 13c.
  • the second switchgear 32 is switched to the closed state. Therefore, the refrigerant flowing through the second main pipe 4b does not flow into the series-parallel switching pipe 6.
  • the first opening degree adjusting device 33 adjusts the amount of refrigerant flowing into the third heat source side heat exchanger 13c by changing the opening degree so that each heat exchanger has an optimum refrigerant circulation amount in the heating operation mode.
  • the second opening degree adjusting device 34 adjusts the amount of refrigerant flowing into the second heat source side heat exchanger 13b by changing the opening degree so that each heat exchanger has an optimum refrigerant circulation amount in the heating operation mode. ..
  • the refrigerant that has flowed into the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c is the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and The heat exchanger 13c on the third heat source side absorbs heat from the outdoor air and becomes a low-temperature low-pressure gas refrigerant.
  • the refrigerant flowing out of the first heat source side heat exchanger 13a flows into the suction side of the compressor 10 through the first four-way valve 11. Further, the refrigerant flowing out from the third heat source side heat exchanger 13c passes through the series-parallel switching pipe 6 in which the second opening degree adjusting device 34 that has been switched to the open state is arranged.
  • the refrigerant that flows out of the third heat source side heat exchanger 13c and passes through the series-parallel switching pipe 6 in which the second opening degree adjusting device 34 is arranged is in the second main pipe 5b in the second heat source side heat exchanger 13b. It merges with the refrigerant flowing out from the compressor, passes through the second four-way valve 12, and flows into the suction side of the compressor 10.
  • the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as the heating operation mode, the first heat source side heat exchanger 13a and the second heat source
  • the side heat exchanger 13b and the third heat source side heat exchanger 13c are connected in parallel with each other by a parallel refrigerant flow path.
  • the first four-way valve 11 shuts off the refrigerant discharged from the compressor 10
  • the second four-way valve 12 supplies the refrigerant discharged from the compressor 10 to the load side heat exchanger 21. 1
  • the opening / closing device 31 is opened, the second opening / closing device 32 is closed, the first opening / closing device 33 is opened, and the second opening / closing device 34 is open.
  • the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are connected in parallel.
  • the pressure loss of the refrigerant flowing through the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c is reduced, and the performance of the evaporator can be improved.
  • FIG. 4 is a refrigerant circuit diagram showing the flow of the refrigerant in the defrosting operation mode of the air conditioner 100 according to the first embodiment.
  • the low-temperature and low-pressure refrigerant is compressed by the compressor 10 and discharged as a high-temperature and high-pressure gas refrigerant.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 branches into the first four-way valve 11 and the second four-way valve 12 and flows in. Then, the refrigerant that has flowed into the first four-way valve 11 flows into the first heat source side heat exchanger 13a through the first main pipe 5a.
  • the refrigerant flowing into the second four-way valve 12 flows into the second heat source side heat exchanger 13b through the second main pipe 5b.
  • the first opening degree adjusting device 33 is switched to the open state. Therefore, the high-temperature and high-pressure gas refrigerant flowing through the second main pipe 5b flows into the third heat source side heat exchanger 13c via the series-parallel switching pipe 6.
  • the second switchgear 32 is switched to the closed state. Therefore, the high-temperature and high-pressure gas refrigerant flowing through the series-parallel switching pipe 6 does not flow into the second main pipe 4b via the series outlet pipe 7.
  • the gas refrigerant flowing into the first heat source side heat exchanger 13a becomes a high-pressure two-phase or liquid refrigerant while melting the frost frosted on the heat exchanger at the first heat source side heat exchanger 13a.
  • the gas refrigerant flowing into the second heat source side heat exchanger 13b becomes a high-pressure two-phase or liquid refrigerant while melting the frost frosted on the heat exchanger at the second heat source side heat exchanger 13b.
  • the gas refrigerant flowing into the third heat source side heat exchanger 13c becomes a high-pressure two-phase or liquid refrigerant while melting the frost frosted on the heat exchanger by the third heat source side heat exchanger 13c.
  • the high-pressure two-phase or liquid refrigerant flowing out of the first heat source side heat exchanger 13a flows into the parallel inlet / outlet pipe 8 through the first inlet / outlet pipe 9a. Further, the high-pressure two-phase or liquid refrigerant flowing out from the second heat source side heat exchanger 13b flows into the parallel inlet / outlet pipe 8 through the second inlet / outlet pipe 9b. Further, the high-pressure two-phase or liquid refrigerant flowing out from the third heat source side heat exchanger 13c flows into the parallel inlet / outlet pipe 8 through the third inlet / outlet pipe 9c.
  • the high-pressure two-phase or liquid refrigerant flowing out of the first heat source side heat exchanger 13a, the high-pressure two-phase or liquid refrigerant flowing out of the second heat source side heat exchanger 13b, and the third heat source side heat exchanger merges at the parallel inlet / outlet pipe 8.
  • the first opening / closing device 31 is switched to the open state. Therefore, the high-pressure two-phase or liquid refrigerant flowing out of the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c passes through the parallel inlet / outlet pipe 8. 2 Passes through the main pipe 4b and flows into the indoor unit 2.
  • the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are connected in parallel in the defrosting operation mode.
  • the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as condensers, and the compressor 10 is used by the first four-way valve 11.
  • the refrigerant discharged from the compressor 10 is supplied to the first heat source side heat exchanger 13a, and the refrigerant discharged from the compressor 10 is supplied to the second heat source side heat exchanger 13b by the second four-way valve 12, and the first switching device 31
  • the second opening / closing device 32 is closed, the first opening / closing adjusting device 33 is opened, and the second opening / closing adjusting device 34 is opened.
  • the high-pressure liquid refrigerant is expanded by the load-side throttle device 22 to become a low-temperature low-pressure gas-liquid two-phase state refrigerant.
  • the gas-liquid two-phase state refrigerant flows into the load side heat exchanger 21 used as an evaporator and absorbs heat from the indoor air to become a low-temperature low-pressure gas refrigerant while cooling the indoor air.
  • the opening degree of the load side throttle device 22 is controlled by the control device 60 so that the opening degree is fully opened.
  • the gas refrigerant flowing out of the load side heat exchanger 21 flows into the outdoor unit 1 again through the first main pipe 4a.
  • the gas refrigerant that has flowed into the outdoor unit 1 is sucked into the compressor 10 again through the second four-way valve 12.
  • the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c operate as a condenser, but as a parallel refrigerant flow path. Connect.
  • the high-temperature and high-pressure refrigerant flows in parallel to the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c, and the maximum defrosting ability is obtained.
  • FIG. 5 is a flowchart for explaining the operation of the control device 60 of the air conditioner 100 according to the first embodiment.
  • the control device 60 determines whether or not the control device 60 is in the cooling operation mode (S11).
  • the heat exchanger flow path switching device includes the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the second. 3 An instruction is given to switch the refrigerant flow path of the heat source side heat exchanger 13c to the series refrigerant flow path (S12).
  • the control device 60 uses the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c as a condenser, and compresses with the first four-way valve 11.
  • the refrigerant discharged from the machine 10 is supplied to the first heat source side heat exchanger 13a, and the refrigerant discharged from the compressor 10 is supplied to the second heat source side heat exchanger 13b by the second four-way valve 12, and the first opening / closing is performed.
  • Control is performed so that the device 31 is opened, the second opening / closing device 32 is opened, the first opening / closing device 33 is closed, and the second opening / closing device 34 is opened.
  • step S11 when it is determined that the control device 60 is not in the cooling operation mode (NO in S11), and after the processing in step S12, it is determined whether or not the control device 60 is in the heating operation mode (S13).
  • step S13 When it is determined in step S13 that the control device 60 is in the heating operation mode (YES in S13), the control device 60 connects the heat exchanger flow path switching device to the first heat source side heat exchanger 13a and the second heat source side heat exchange. An instruction is given to switch the refrigerant flow path of the device 13b and the third heat source side heat exchanger 13c to the parallel refrigerant flow path (S14).
  • the control device 60 shuts off the refrigerant discharged from the compressor 10 by the first four-way valve 11, and sends the refrigerant discharged from the compressor 10 by the second four-way valve 12 to the load side heat exchanger 21.
  • the first opening / closing device 31 is opened, the second opening / closing device 32 is closed, the first opening / closing device 33 is opened, and the second opening / closing device 34 is opened.
  • step S13 when it is determined that the control device 60 is not in the heating operation mode (NO in S13), and after the processing in step S14, it is determined whether or not the control device 60 is in the defrosting operation mode (S15).
  • step S15 When it is determined in step S15 that the control device 60 is in the defrosting operation mode (YES in S15), the control device 60 is connected to the heat exchanger flow path switching device with the first heat source side heat exchanger 13a and the second heat source side heat. An instruction is given to switch the refrigerant flow paths of the exchanger 13b and the third heat source side heat exchanger 13c to parallel refrigerant flow paths (S16).
  • control device 60 supplies the refrigerant discharged from the compressor 10 by the first four-way valve 11 to the first heat source side heat exchanger 13a, and discharges the refrigerant from the compressor 10 by the second four-way valve 12.
  • the refrigerant is supplied to the second heat source side heat exchanger 13b, the first opening / closing device 31 is opened, the second opening / closing device 32 is closed, the first opening / closing device 33 is opened, and the second opening / closing device 34 is opened. Is controlled so as to open.
  • step S15 If it is determined in step S15 that the control device 60 is not in the defrosting operation mode (NO in S15), and after the processing in step S16, the process returns to step S11.
  • the air conditioner 100 includes the compressor 10, the first four-way valve 11, the second four-way valve 12, the load side heat exchanger 21, the load side throttle device 22, and at least the first heat source.
  • the side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are connected by a refrigerant pipe 3 to include a main circuit in which the refrigerant circulates.
  • the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as the cooling operation mode
  • the first heat source side heat exchanger 13a and the first heat exchanger 13a are on the upstream side.
  • the two heat source side heat exchangers 13b are in parallel with each other
  • the third heat source side heat exchanger 13c is in series with the first heat source side heat exchanger 13a and the second heat source side heat exchanger 13b on the downstream side. It is connected by a series refrigerant flow path.
  • the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as the heating operation mode, the first heat source side heat exchanger 13a and the second heat source side heat The exchanger 13b and the third heat source side heat exchanger 13c are connected in parallel with each other by a parallel refrigerant flow path.
  • the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as the defrosting operation mode, the first heat source side heat exchanger 13a and the second heat source side
  • the heat exchanger 13b and the third heat source side heat exchanger 13c are connected in parallel with each other by a parallel refrigerant flow path.
  • the air conditioner 100 switches to the series refrigerant flow path when the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as the cooling operation mode, and the first When the heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as the heating operation mode, they are switched to the parallel refrigerant flow path, and the first heat source side heat exchanger 13a, the first It has a heat exchanger flow path switching device that switches to a parallel refrigerant flow path when the two heat source side heat exchangers 13b and the third heat source side heat exchanger 13c are used as the defrost rainy weather mode.
  • the heat exchanger flow path switching device is a first switchgear 31, a second switchgear 32, a first opening / closing device 33, and a second opening / closing device 34.
  • the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as the cooling operation mode, they are switched to the series refrigerant flow path and the first It has a heat exchanger flow path switching device that switches to a parallel refrigerant flow path when the heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as the heating operation mode. There is.
  • the flow paths of the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c can be switched in series or in parallel between the cooling operation and the heating operation.
  • the series refrigerant flow path is first on the upstream side when the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as the cooling operation mode.
  • the heat source side heat exchanger 13a and the second heat source side heat exchanger 13b are in parallel with each other, and the third heat source is relative to the first heat source side heat exchanger 13a and the second heat source side heat exchanger 13b on the downstream side.
  • Side heat exchangers 13c are connected in series.
  • the third heat source side heat exchanger 13c is arranged on the downstream side of the condenser, the volume on the downstream side of the evaporator is small, and evaporation occurs.
  • the liquid refrigerant accumulates on the downstream side of the vessel.
  • the first heat source side heat exchanger 13a is provided with one first header 14a and one first distributor 15a.
  • the second heat source side heat exchanger 13b is provided with one second header 14b and one second distributor 15b.
  • the third heat source side heat exchanger 13c is provided with a single third header 14c and a single fourth header 14d.
  • each of the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c is provided with a total of two headers or distributors.
  • the cost can be suppressed and the installation space can be narrowed as compared with the conventional configuration in which two or more headers and distributors are provided in one heat source side heat exchanger.
  • the first opening degree adjusting device 33 and the second opening degree adjusting device 34 are throttle devices capable of adjusting the flow rate by changing the opening degree.
  • the heat exchanger flow path switching device changes the opening degree of each of the first opening degree adjusting device 33 and the second opening degree adjusting device 34 to the first heat source side. The amount of refrigerant flowing into each of the heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c is adjusted.
  • the first heat source side heat exchanger 13a when the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as the heating operation mode, the first heat source side heat exchanger 13a
  • the amount of refrigerant can be optimally distributed to the second heat source side heat exchanger 13b and the third heat source side heat exchanger 13c.
  • the total heat transfer area of the heat transfer area of the first heat source side heat exchanger 13a and the heat transfer area of the second heat source side heat exchanger 13b is the third heat source side heat exchanger 13c. It is formed so as to be larger than the heat transfer area of.
  • the third heat source side heat exchanger 13c is arranged on the downstream side of the evaporator, and the volume on the downstream side of the evaporator is large. It is small, and the refrigerant that collects liquid refrigerant on the downstream side of the evaporator can be suppressed from falling asleep, and the refrigerant can be circulated well.
  • the first heat source side heat exchanger 13a is arranged independently.
  • a part of the second heat source side heat exchanger 13b is integrally formed with the third heat source side heat exchanger 13c by sharing fins which are heat exchanger components.
  • the remaining part other than a part of the second heat source side heat exchanger 13b is configured independently of the third heat source side heat exchanger 13c.
  • the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger are used as opposed to the case where the independent first heat source side heat exchanger 13a also shares the fins.
  • the connection pipe which is the refrigerant pipe 3 can be simplified, and the air conditioner 100 can be miniaturized.
  • the heat transfer tube which is a component of the heat exchanger is a flat tube. ..
  • the compressor 10 of the first embodiment has been described by taking the case of using a low-pressure shell type compressor as an example. However, for example, the same effect can be obtained by using a high-pressure shell type compressor.
  • the heat source side heat exchanger and the load side heat exchanger are often equipped with a blower such as a fan that promotes the condensation or evaporation of the refrigerant by blowing air, but the present invention is not limited to this. ..
  • a blower such as a fan that promotes the condensation or evaporation of the refrigerant by blowing air
  • the present invention is not limited to this. ..
  • a panel heater using radiation can also be used.
  • a water-cooled type heat exchanger that exchanges heat with a liquid such as water or antifreeze can be used. Any heat exchanger can be used as long as it can dissipate heat or absorb heat from the refrigerant.
  • a water-cooled type heat exchanger for example, a water-refrigerant heat exchanger such as a plate heat exchanger or a double-tube heat exchanger may be installed and used.
  • the embodiment is presented as an example and is not intended to limit the scope of the embodiment.
  • the embodiment can be implemented in various other forms, and various omissions, replacements, and changes can be made without departing from the gist of the embodiment. These embodiments and variations thereof are included in the scope and gist of the embodiments.

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Abstract

An air-conditioning device according to the present invention is provided with: a main circuit in which a compressor, a refrigerant channel switching device, a load-side heat exchanger, a load-side throttle device, a first heat-source-side heat exchanger, a second heat-source-side heat exchanger, and a third heat-source-side heat exchanger are connected by piping and in which a refrigerant circulates; a heat exchanger channel switching device for switching a refrigerant channel of the first, second, and third heat-source-side heat exchangers; and a control device for controlling the heat exchanger channel switching device. The control device controls the heat exchanger channel switching device to switch the refrigerant channel of the first, second, and third heat-source-side heat exchangers to a parallel refrigerant channel when the first, second, and third heat-source-side heat exchangers are used as a defrost operation mode. The parallel refrigerant channel is a refrigerant channel in which the first, second, and third heat-source-side heat exchangers are connected in parallel to each other.

Description

空気調和装置Air conditioner
　本発明は、３つの熱源側熱交換器有し、これら３つの熱源側熱交換器の冷媒流路を切り替えることができる空気調和装置に関する。 The present invention relates to an air conditioner having three heat source side heat exchangers and capable of switching the refrigerant flow path of these three heat source side heat exchangers.
　従来、たとえばビル用マルチエアコンなどの空気調和装置は、建物外に配置した熱源機である室外機（室外ユニット）と、建物内に配置した室内機（室内ユニット）と、の間を、配管を介して接続した冷媒回路を備えるものが知られている。そして、冷媒回路において冷媒が循環し、冷媒の放熱又は吸熱を利用して室内空気が加熱又は冷却されることにより、空調対象空間の暖房又は冷房が行われている。
　並列に接続された複数の熱交換器において、室外熱交換器のように暖房運転時に蒸発器として使用する場合に、複数の熱交換器を並列に接続して冷媒が流れる。これにより、蒸発器の圧力損失が低減でき、蒸発器の性能が向上し、暖房性能が向上する。 Conventionally, in an air conditioner such as a multi air conditioner for a building, a pipe is provided between an outdoor unit (outdoor unit) which is a heat source unit arranged outside the building and an indoor unit (indoor unit) arranged inside the building. Those provided with a refrigerant circuit connected via a pipe are known. Then, the refrigerant circulates in the refrigerant circuit, and the indoor air is heated or cooled by utilizing the heat radiation or heat absorption of the refrigerant, so that the air-conditioned space is heated or cooled.
In a plurality of heat exchangers connected in parallel, when used as an evaporator during a heating operation like an outdoor heat exchanger, the plurality of heat exchangers are connected in parallel and the refrigerant flows. As a result, the pressure loss of the evaporator can be reduced, the performance of the evaporator is improved, and the heating performance is improved.
　しかし、冷房運転時に凝縮器として使用する場合に、複数の熱交換器を並列に接続して冷媒が流れることにより、各伝熱管を流れる冷媒の流速が低下する。これにより、管内熱伝達率が低下し、凝縮器の性能が低下し、冷房性能が低下する。 However, when used as a condenser during cooling operation, the flow velocity of the refrigerant flowing through each heat transfer tube decreases due to the flow of the refrigerant by connecting multiple heat exchangers in parallel. As a result, the heat transfer coefficient in the pipe is lowered, the performance of the condenser is lowered, and the cooling performance is lowered.
　そこで、凝縮器としても蒸発器としても性能が向上するように、複数の流路切替弁を使用して流路を切り替える技術がある。この技術では、凝縮器として使用する場合に、複数の熱交換器を直列に接続して冷媒が流れるように流路が切り替わる。これにより、冷媒の流速が上昇することにより、凝縮器の性能が向上する。また、蒸発器として使用する場合に、複数の熱交換器を並列に接続して冷媒が流れるように流路が切り替わる。これにより、圧力損失が低減することにより、蒸発器の性能が向上する。このような冷房運転時及び暖房運転時の性能向上手法が提案されている。 Therefore, there is a technology to switch the flow path by using a plurality of flow path switching valves so that the performance of both the condenser and the evaporator is improved. In this technique, when used as a condenser, a plurality of heat exchangers are connected in series and the flow path is switched so that the refrigerant flows. As a result, the flow velocity of the refrigerant increases, which improves the performance of the condenser. Further, when used as an evaporator, a plurality of heat exchangers are connected in parallel and the flow path is switched so that the refrigerant flows. This reduces the pressure loss and improves the performance of the evaporator. A method for improving performance during such cooling operation and heating operation has been proposed.
特開２００３－１２１０１９号公報Japanese Unexamined Patent Publication No. 2003-121019
　従来の空気調和装置では、蒸発器に霜が付き蒸発器の性能が低下することを防ぐために除霜運転を実施する際に熱交換器を凝縮器として運転する。その際に各熱交換器が直列となってしまうため、後流側の熱交換器で除霜能力が不足することがあった。 In the conventional air conditioner, the heat exchanger is operated as a condenser when the defrosting operation is performed in order to prevent the evaporator from being frosted and the performance of the evaporator being deteriorated. At that time, since each heat exchanger is connected in series, the heat exchanger on the wake side may have insufficient defrosting ability.
　本発明は、上記実情に鑑みてなされたものであり、除霜運転を実施する際に除霜能力が向上した空気調和装置を提供することを目的とする。 The present invention has been made in view of the above circumstances, and an object of the present invention is to provide an air conditioner having improved defrosting ability when carrying out a defrosting operation.
　本発明に係る空気調和装置によれば、圧縮機、冷媒流路切替装置、負荷側熱交換器、負荷側絞り装置、第１熱源側熱交換器、第２熱源側熱交換器及び第３熱源側熱交換器が配管で接続されて冷媒が循環する主回路と、前記第１熱源側熱交換器、前記第２熱源側熱交換器及び前記第３熱源側熱交換器の冷媒流路を切り替えるための熱交換器流路切替装置と、前記熱交換器流路切替装置を制御する制御装置とを具備し、前記制御装置は、前記第１熱源側熱交換器、前記第２熱源側熱交換器及び前記第３熱源側熱交換器を除霜運転モードとして使用する際に、前記第１熱源側熱交換器、前記第２熱源側熱交換器及び前記第３熱源側熱交換器の冷媒流路を並列冷媒流路に切り替えるように前記熱交換器流路切替装置を制御し、前記並列冷媒流路は、前記第１熱源側熱交換器、前記第２熱源側熱交換器及び前記第３熱源側熱交換器が互いに並列に接続される冷媒流路である。 According to the air conditioner according to the present invention, the compressor, the refrigerant flow path switching device, the load side heat exchanger, the load side drawing device, the first heat source side heat exchanger, the second heat source side heat exchanger and the third heat source The main circuit in which the side heat exchangers are connected by pipes to circulate the refrigerant and the refrigerant flow paths of the first heat source side heat exchanger, the second heat source side heat exchanger, and the third heat source side heat exchanger are switched. A heat exchanger flow path switching device for the purpose and a control device for controlling the heat exchanger flow path switching device are provided, and the control device includes the first heat source side heat exchanger and the second heat source side heat exchange. When the device and the third heat source side heat exchanger are used as the defrosting operation mode, the refrigerant flow of the first heat source side heat exchanger, the second heat source side heat exchanger and the third heat source side heat exchanger The heat exchanger flow path switching device is controlled so as to switch the path to the parallel refrigerant flow path, and the parallel refrigerant flow path is the first heat source side heat exchanger, the second heat source side heat exchanger, and the third. A refrigerant flow path in which heat source side heat exchangers are connected in parallel with each other.
　本発明によれば、除霜運転を実施する際に第１熱源側熱交換器と第２熱源側熱交換器と第３熱源側熱交換器とが互いに並列に接続された並列冷媒流路に切り替わるので、除霜能力が向上した空気調和装置を提供できる。 According to the present invention, when the defrosting operation is performed, the first heat source side heat exchanger, the second heat source side heat exchanger, and the third heat source side heat exchanger are connected in parallel to each other in a parallel refrigerant flow path. Since it is switched, it is possible to provide an air conditioner with improved defrosting ability.
実施の形態１に係る空気調和装置１００の回路構成の一例を示す概略回路構成図である。It is a schematic circuit block diagram which shows an example of the circuit structure of the air conditioner 100 which concerns on Embodiment 1. FIG. 実施の形態１に係る空気調和装置１００の冷房運転モード時における冷媒の流れを示す冷媒回路図である。It is a refrigerant circuit diagram which shows the flow of the refrigerant in the cooling operation mode of the air conditioner 100 which concerns on Embodiment 1. FIG. 実施の形態１に係る空気調和装置１００の暖房運転モード時における冷媒の流れを示す冷媒回路図である。It is a refrigerant circuit diagram which shows the flow of the refrigerant in the heating operation mode of the air conditioner 100 which concerns on Embodiment 1. FIG. 実施の形態１に係る空気調和装置１００の除霜運転モード時における冷媒の流れを示す冷媒回路図である。It is a refrigerant circuit diagram which shows the flow of the refrigerant in the defrost operation mode of the air conditioner 100 which concerns on Embodiment 1. FIG. 実施の形態１に係る空気調和装置１００の制御装置の動作を説明するためのフローチャートである。It is a flowchart for demonstrating operation of the control device of the air conditioner 100 which concerns on Embodiment 1. FIG.
　以下、図面を参照して、実施の形態に係る空気調和装置について説明する。なお、図面において、同一の構成要素には同一符号を付して説明し、重複説明は必要な場合にのみ行なう。さらに、明細書全文に示されている構成要素の形態は、あくまで例示であってこれらの記載に限定されるものではない。 Hereinafter, the air conditioner according to the embodiment will be described with reference to the drawings. In the drawings, the same components will be described with the same reference numerals, and duplicate explanations will be given only when necessary. Furthermore, the forms of the components shown in the full text of the specification are merely examples and are not limited to these descriptions.
実施の形態１．
１－１．構成
　図１は、実施の形態１に係る空気調和装置１００の回路構成の一例を示す概略回路構成図である。
　図１に示す空気調和装置１００は、室外機１と室内機２とが第１主管４ａ及び第２主管４ｂで接続された構成である。
　なお、図１では、１台の室内機２が第１主管４ａ及び第２主管４ｂを介して室外機１に接続されている場合を例に示している。しかし、室外機１に接続される室内機２の接続台数を１台に限定するものではなく、複数台接続してもよい。 Embodiment 1.
1-1. Configuration FIG. 1 is a schematic circuit configuration diagram showing an example of the circuit configuration of the air conditioner 100 according to the first embodiment.
The air conditioner 100 shown in FIG. 1 has a configuration in which an outdoor unit 1 and an indoor unit 2 are connected by a first main pipe 4a and a second main pipe 4b.
Note that FIG. 1 shows an example in which one indoor unit 2 is connected to the outdoor unit 1 via the first main pipe 4a and the second main pipe 4b. However, the number of indoor units 2 connected to the outdoor unit 1 is not limited to one, and a plurality of indoor units may be connected.
［室外機１］
　室外機１は、主回路の構成要素として、圧縮機１０と、第１四方弁１１と、第２四方弁１２と、第１熱源側熱交換器１３ａと、第２熱源側熱交換器１３ｂと、第３熱源側熱交換器１３ｃと、を有している。 [Outdoor unit 1]
The outdoor unit 1 includes a compressor 10, a first four-way valve 11, a second four-way valve 12, a first heat source side heat exchanger 13a, and a second heat source side heat exchanger 13b as components of the main circuit. , And a third heat source side heat exchanger 13c.
　なお、第１四方弁１１及び第２四方弁１２は、冷媒流路切替装置に相当する。 The first four-way valve 11 and the second four-way valve 12 correspond to the refrigerant flow path switching device.
　主回路は、圧縮機１０、第１四方弁１１、第２四方弁１２、負荷側熱交換器２１、負荷側絞り装置２２、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃが冷媒配管３で順次接続されて冷媒が循環する。 The main circuits are the compressor 10, the first four-way valve 11, the second four-way valve 12, the load side heat exchanger 21, the load side throttle device 22, the first heat source side heat exchanger 13a, and the second heat source side heat exchanger 13b. And the third heat source side heat exchanger 13c are sequentially connected by the refrigerant pipe 3, and the refrigerant circulates.
　なお、冷媒配管３は、空気調和装置１００に用いられる冷媒を流通させる配管の総称である。冷媒配管３は、たとえば、第１主管４ａ、第２主管４ｂ、第１本管５ａ、第２本管５ｂ、直列並列切り替え配管６、直列出口配管７、並列出入口配管８、第１出入口配管９ａ、第２出入口配管９ｂ、第３出入口配管９ｃ、第１ヘッダー１４ａ、第２ヘッダー１４ｂ、第３ヘッダー１４ｃ、第４ヘッダー１４ｄ、第１分配器１５ａ及び第２分配器１５ｂなどを含んで構成される。 The refrigerant pipe 3 is a general term for pipes for circulating the refrigerant used in the air conditioner 100. The refrigerant pipe 3 includes, for example, a first main pipe 4a, a second main pipe 4b, a first main pipe 5a, a second main pipe 5b, a series parallel switching pipe 6, a series outlet pipe 7, a parallel inlet / outlet pipe 8, and a first inlet / outlet pipe 9a. , 2nd entrance / exit pipe 9b, 3rd entrance / exit pipe 9c, 1st header 14a, 2nd header 14b, 3rd header 14c, 4th header 14d, 1st distributor 15a, 2nd distributor 15b and the like. To.
　また、熱源側熱交換器としては、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃ以外に他の熱源側熱交換器も備えてもよい。 Further, as the heat source side heat exchanger, other heat source side heat exchangers may be provided in addition to the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c. ..
　第１主管４ａ及び第２主管４ｂは、室外機１と室内機２とを繋ぐ。第１本管５ａは、第１四方弁１１と第１ヘッダー１４ａとを繋ぐ。第２本管５ｂは、第２四方弁１２と第２ヘッダー１４ｂとを繋ぐ。 The first main pipe 4a and the second main pipe 4b connect the outdoor unit 1 and the indoor unit 2. The first main pipe 5a connects the first four-way valve 11 and the first header 14a. The second main pipe 5b connects the second four-way valve 12 and the second header 14b.
　直列並列切り替え配管６は第４ヘッダー１４ｄと第２ヘッダー１４ｂとを合流させ第２本管５ｂを介して第２四方弁１２に繋ぐ。すなわち直列並列切り替え配管６は第２ヘッダー１４ｂと、第４ヘッダー１４ｄと、を繋ぐ。 The series-parallel switching pipe 6 joins the fourth header 14d and the second header 14b and connects to the second four-way valve 12 via the second main pipe 5b. That is, the series-parallel switching pipe 6 connects the second header 14b and the fourth header 14d.
　並列出入口配管８は第１出入口配管９ａと第２出入口配管９ｂと第３出入口配管９ｃとがそれぞれ接続され、負荷側絞り装置２２に至る第２主管４ｂと、を繋ぐ。 The parallel inlet / outlet pipe 8 is connected to the first inlet / outlet pipe 9a, the second inlet / outlet pipe 9b, and the third inlet / outlet pipe 9c, respectively, and connects to the second main pipe 4b leading to the load side throttle device 22.
　直列出口配管７は直列並列切り替え配管６と第４ヘッダー１４ｄとが接続された接続部と、負荷側絞り装置２２に至る第２主管４ｂと、を繋ぐ。 The series outlet pipe 7 connects the connection portion in which the series / parallel switching pipe 6 and the fourth header 14d are connected and the second main pipe 4b leading to the load side throttle device 22.
　室外機１は、熱交換器流路切替装置として、第１開閉装置３１と、第２開閉装置３２と、Ｃｖ値を調整することが可能な第１開度調整装置３３と、第２開度調整装置３４と、を有している。 The outdoor unit 1 has a first switchgear 31, a second switchgear 32, a first opening / closing device 33 capable of adjusting a Cv value, and a second opening / closing device 33 as heat exchanger flow path switching devices. It has an adjusting device 34 and.
　また、室外機１には、送風機であるファン１６が搭載されている。ファン１６には、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃの上方に位置するトップフロー方式又は第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃの側方に位置するサイドフロー方式などが採用される。
　圧縮機１０は、冷媒を吸入して圧縮して高温高圧の状態にする。圧縮機１０は、たとえば容量制御可能なインバータ圧縮機などで構成されている。圧縮機１０は、たとえば、密閉容器内に圧縮室を有し、密閉容器内が低圧の冷媒圧雰囲気になり、密閉容器内の低圧冷媒を吸入して圧縮する低圧シェル構造のものを使用する。
　第１四方弁１１及び第２四方弁１２は、冷房運転モード及び除霜運転モード時における冷媒流路と、暖房運転モード時における冷媒流路と、を切り替えるものである。 Further, the outdoor unit 1 is equipped with a fan 16 which is a blower. The fan 16 includes a top flow type or first heat source side heat exchanger 13a located above the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c. A side flow method or the like located on the side of the two heat source side heat exchangers 13b and the third heat source side heat exchanger 13c is adopted.
The compressor 10 sucks in the refrigerant and compresses it into a high temperature and high pressure state. The compressor 10 is composed of, for example, an inverter compressor whose capacity can be controlled. The compressor 10 uses, for example, a low-pressure shell structure having a compression chamber in a closed container, the inside of the closed container having a low-pressure refrigerant pressure atmosphere, and sucking and compressing the low-pressure refrigerant in the closed container.
The first four-way valve 11 and the second four-way valve 12 switch between the refrigerant flow path in the cooling operation mode and the defrosting operation mode and the refrigerant flow path in the heating operation mode.
　なお、冷房運転モードとは、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃの少なくとも１つが凝縮器もしくはガスクーラとして使用される場合である。実施の形態１では、冷房運転モードと、暖房運転モードと、を有する。暖房運転モードとは、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃが蒸発器として使用される場合である。 The cooling operation mode is a case where at least one of the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c is used as a condenser or a gas cooler. The first embodiment has a cooling operation mode and a heating operation mode. The heating operation mode is a case where the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as the evaporator.
　第１四方弁１１は、圧縮機１０から吐出された冷媒を第１熱源側熱交換器１３ａに供給又は遮断を行う。 The first four-way valve 11 supplies or shuts off the refrigerant discharged from the compressor 10 to the first heat source side heat exchanger 13a.
　第２四方弁１２は、圧縮機１０から吐出された冷媒を第２熱源側熱交換器１３ｂ、第３熱源側熱交換器１３ｃ又は負荷側熱交換器２１のどちらかに供給する。 The second four-way valve 12 supplies the refrigerant discharged from the compressor 10 to either the second heat source side heat exchanger 13b, the third heat source side heat exchanger 13c, or the load side heat exchanger 21.
　第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃは、熱交換器構成要素である複数の伝熱管と、熱交換器構成要素である複数のフィンと、を有している。 The first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c include a plurality of heat transfer tubes which are heat exchanger components and a plurality of heat exchanger components. It has fins and.
　複数の伝熱管は、それぞれ扁平管もしくは円管である。複数の伝熱管は、水平方向に延びている。複数の伝熱管は、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃ内に複数の冷媒流路を構成する。 Multiple heat transfer tubes are flat tubes or circular tubes, respectively. The plurality of heat transfer tubes extend in the horizontal direction. The plurality of heat transfer tubes form a plurality of refrigerant flow paths in the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c.
　複数のフィンは、板状であり、所定間隔を空けて重ねられている。複数のフィンは、伝熱管の延伸方向と直交方向である鉛直方向に延びて複数の伝熱管が挿通されている。 The plurality of fins are plate-shaped and are stacked at predetermined intervals. The plurality of fins extend in the vertical direction which is orthogonal to the extending direction of the heat transfer tube, and the plurality of heat transfer tubes are inserted therethrough.
　第１熱源側熱交換器１３ａは、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃとは離れて独立して配置されている。第２熱源側熱交換器１３ｂは、第３熱源側熱交換器１３ｃの鉛直線上の上方に配置されている。 The first heat source side heat exchanger 13a is arranged independently of the second heat source side heat exchanger 13b and the third heat source side heat exchanger 13c. The second heat source side heat exchanger 13b is arranged above the third heat source side heat exchanger 13c on the vertical line.
　第１熱源側熱交換器１３ａには、１つの第１ヘッダー１４ａ及び１つの第１分配器１５ａが設けられている。 The first heat source side heat exchanger 13a is provided with one first header 14a and one first distributor 15a.
　第２熱源側熱交換器１３ｂは、第３熱源側熱交換器１３ｃの鉛直線上の上方に配置されている。第２熱源側熱交換器１３ｂの一部分は、第３熱源側熱交換器１３ｃと熱交換器構成要素であるフィンを共有して一体に構成されている。つまり、第２熱源側熱交換器１３ｂの一部分と第３熱源側熱交換器１３ｃの一部分とは、同じフィンに互いの伝熱管を挿通している。 The second heat source side heat exchanger 13b is arranged above the vertical line of the third heat source side heat exchanger 13c. A part of the second heat source side heat exchanger 13b is integrally formed with the third heat source side heat exchanger 13c by sharing fins which are heat exchanger components. That is, a part of the second heat source side heat exchanger 13b and a part of the third heat source side heat exchanger 13c have their heat transfer tubes inserted into the same fins.
　第２熱源側熱交換器１３ｂの一部分以外の残りの部分は、第３熱源側熱交換器１３ｃとは独立して構成されている。つまり、第２熱源側熱交換器１３ｂの一部分以外と第３熱源側熱交換器１３ｃの一部分以外とは、異なるフィンにそれぞれの伝熱管を挿通している。 The remaining part other than a part of the second heat source side heat exchanger 13b is configured independently of the third heat source side heat exchanger 13c. That is, the heat transfer tubes are inserted into different fins except for a part of the second heat source side heat exchanger 13b and a part of the third heat source side heat exchanger 13c.
　第２熱源側熱交換器１３ｂには、１つの第２ヘッダー１４ｂ及び１つの第２分配器１５ｂが設けられている。 The second heat source side heat exchanger 13b is provided with one second header 14b and one second distributor 15b.
　第３熱源側熱交換器１３ｃには、１つの第３ヘッダー１４ｃ及び１つの第４ヘッダー１４ｄが設けられている。 The third heat source side heat exchanger 13c is provided with one third header 14c and one fourth header 14d.
　第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃは、冷房運転モード時、除霜運転モード時には凝縮器として機能し、暖房運転モード時には蒸発器として機能するものである。第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃは、ファン１６から供給される空気と複数の伝熱管を流通する冷媒との間で熱交換を行う。なお、冷房運転モード時には、各種モードによって、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃの全部又は一部のみが凝縮器として機能する。 The first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c function as a condenser in the cooling operation mode and the defrosting operation mode, and an evaporator in the heating operation mode. It functions as. The first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c exchange heat between the air supplied from the fan 16 and the refrigerant flowing through the plurality of heat transfer tubes. I do. In the cooling operation mode, depending on the various modes, only all or a part of the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c function as a condenser.
　ここで、第１熱源側熱交換器１３ａの伝熱面積と第２熱源側熱交換器１３ｂの伝熱面積との和の伝熱面積は、第３熱源側熱交換器１３ｃの伝熱面積よりも大きくなるように形成されている。このため、第１熱源側熱交換器１３ａ及び第２熱源側熱交換器１３ｂの伝熱管数の和の数は、第３熱源側熱交換器１３ｃの伝熱管数よりも多く設けられている。 Here, the total heat transfer area of the heat transfer area of the first heat source side heat exchanger 13a and the heat transfer area of the second heat source side heat exchanger 13b is calculated from the heat transfer area of the third heat source side heat exchanger 13c. Is also formed to be large. Therefore, the number of sums of the number of heat transfer tubes of the first heat source side heat exchanger 13a and the second heat source side heat exchanger 13b is larger than the number of heat transfer tubes of the third heat source side heat exchanger 13c.
　第１ヘッダー１４ａは、第１熱源側熱交換器１３ａを冷房運転モード時、及び除霜運転モード時の凝縮器として使用する際に、第１熱源側熱交換器１３ａの入口側の冷媒流路となる位置に設けられている。 The first header 14a is a refrigerant flow path on the inlet side of the first heat source side heat exchanger 13a when the first heat source side heat exchanger 13a is used as a condenser in the cooling operation mode and the defrosting operation mode. It is provided at the position where
　第１ヘッダー１４ａは、第１熱源側熱交換器１３ａの伝熱管にそれぞれ接続される細い配管である複数の枝管と、複数の枝管が接続された主配管と、を有している。主配管は、第１四方弁１１と繋がれている第１本管５ａに接続されている。主配管の上部が、第１本管５ａに接続されている。第１ヘッダー１４ａは、第１熱源側熱交換器１３ａを冷房運転モード時、及び除霜運転モード時の凝縮器として使用する際に、第１本管５ａから主配管に流入した冷媒を複数の枝管を通じて第１熱源側熱交換器１３ａに流入させる。第１ヘッダー１４ａは、第１熱源側熱交換器１３ａを蒸発器として使用する際に、第１熱源側熱交換器１３ａから複数の枝管に流出した冷媒を、主配管を通じて第１本管５ａに流出させる。 The first header 14a has a plurality of branch pipes, which are thin pipes connected to the heat transfer pipes of the first heat source side heat exchanger 13a, and a main pipe to which the plurality of branch pipes are connected. The main pipe is connected to the first main pipe 5a which is connected to the first four-way valve 11. The upper part of the main pipe is connected to the first main pipe 5a. The first header 14a contains a plurality of refrigerants that have flowed into the main pipe from the first main pipe 5a when the first heat source side heat exchanger 13a is used as a condenser in the cooling operation mode and the defrosting operation mode. It flows into the first heat source side heat exchanger 13a through the branch pipe. When the first heat source side heat exchanger 13a is used as an evaporator, the first header 14a allows the refrigerant flowing out from the first heat source side heat exchanger 13a to a plurality of branch pipes to flow through the main pipe to the first main pipe 5a. To leak to.
　第２ヘッダー１４ｂは、第２熱源側熱交換器１３ｂを冷房運転モード時、及び除霜運転モード時の凝縮器として使用する際に、第２熱源側熱交換器１３ｂの入口側の冷媒流路となる位置に設けられている。
　第２ヘッダー１４ｂは、第２熱源側熱交換器１３ｂの伝熱管にそれぞれ接続される細い配管である複数の枝管と、複数の枝管が接続された主配管と、を有している。主配管は、第２四方弁１２と繋がれている第２本管５ｂに接続されている。主配管の下部が、第２本管５ｂに接続されている。第２ヘッダー１４ｂは、第２熱源側熱交換器１３ｂを冷房運転モード時、及び除霜運転モード時の凝縮器として使用する際に、第２本管５ｂから主配管に流入した冷媒を複数の枝管を通じて第２熱源側熱交換器１３ｂに流入させる。第２ヘッダー１４ｂは、第２熱源側熱交換器１３ｂを蒸発器として使用する際に、第２熱源側熱交換器１３ｂから複数の枝管に流出した冷媒を、主配管を通じて第２本管５ｂに流出させる。 The second header 14b is a refrigerant flow path on the inlet side of the second heat source side heat exchanger 13b when the second heat source side heat exchanger 13b is used as a condenser in the cooling operation mode and the defrosting operation mode. It is provided at the position where
The second header 14b has a plurality of branch pipes, which are thin pipes connected to the heat transfer pipes of the second heat source side heat exchanger 13b, and a main pipe to which the plurality of branch pipes are connected. The main pipe is connected to the second main pipe 5b which is connected to the second four-way valve 12. The lower part of the main pipe is connected to the second main pipe 5b. The second header 14b contains a plurality of refrigerants that have flowed into the main pipe from the second main pipe 5b when the second heat source side heat exchanger 13b is used as a condenser in the cooling operation mode and the defrosting operation mode. It flows into the second heat source side heat exchanger 13b through the branch pipe. When the second heat source side heat exchanger 13b is used as an evaporator, the second header 14b allows the refrigerant flowing out from the second heat source side heat exchanger 13b to a plurality of branch pipes to flow through the main pipe to the second main pipe 5b. To leak to.
　第３ヘッダー１４ｃは、第３熱源側熱交換器１３ｃを冷房運転モード時の凝縮器もしくは蒸発器として使用する際に、第３熱源側熱交換器１３ｃの入口側の冷媒流路となる位置に設けられている。
　第３ヘッダー１４ｃは、第３熱源側熱交換器１３ｃの伝熱管にそれぞれ接続される細い配管である複数の枝管と、複数の枝管が接続された主配管と、を有している。主配管は、並列出入口配管８に接続されている。主配管の下部が、並列出入口配管８に接続されている。第３ヘッダー１４ｃは、第３熱源側熱交換器１３ｃを冷房モード時の凝縮器もしくは蒸発器として使用する際に、並列出入口配管８から主配管に流入した冷媒を複数の枝管を通じて第３熱源側熱交換器１３ｃに流入させる。第３ヘッダー１４ｃは、第３熱源側熱交換器１３ｃを除霜運転モード時の凝縮器として使用する際に、第３熱源側熱交換器１３ｃから複数の枝管に流出した冷媒を主配管を通じて並列出入口配管８に流出させる。 The third header 14c is located at a position that serves as a refrigerant flow path on the inlet side of the third heat source side heat exchanger 13c when the third heat source side heat exchanger 13c is used as a condenser or an evaporator in the cooling operation mode. It is provided.
The third header 14c has a plurality of branch pipes, which are thin pipes connected to the heat transfer pipes of the third heat source side heat exchanger 13c, and a main pipe to which the plurality of branch pipes are connected. The main pipe is connected to the parallel entrance / exit pipe 8. The lower part of the main pipe is connected to the parallel inlet / outlet pipe 8. The third header 14c is a third heat source through a plurality of branch pipes, when the third heat source side heat exchanger 13c is used as a condenser or an evaporator in the cooling mode, the refrigerant flowing into the main pipe from the parallel inlet / outlet pipe 8 is used. It flows into the side heat exchanger 13c. The third header 14c allows the refrigerant flowing out from the third heat source side heat exchanger 13c to the plurality of branch pipes through the main pipe when the third heat source side heat exchanger 13c is used as a condenser in the defrosting operation mode. It flows out to the parallel entrance / exit pipe 8.
　第４ヘッダー１４ｄは、第３熱源側熱交換器１３ｃを除霜運転モード時の凝縮器として使用する際に、第３熱源側熱交換器１３ｃの入口側の冷媒流路となる位置に設けられている。 The fourth header 14d is provided at a position that serves as a refrigerant flow path on the inlet side of the third heat source side heat exchanger 13c when the third heat source side heat exchanger 13c is used as a condenser in the defrosting operation mode. ing.
　第４ヘッダー１４ｄは、第３熱源側熱交換器１３ｃの伝熱管にそれぞれ接続される細い配管である複数の枝管と、複数の枝管が接続された主配管と、を有している。主配管は、直列並列切り替え配管６及び直列出口配管７に接続されている。主配管の下部が、直列並列切り替え配管６及び直列出口配管７に接続されている。第４ヘッダー１４ｄは、第３熱源側熱交換器１３ｃを除霜運転モード凝縮器として使用する際に、直列並列切り替え配管６から主配管に流入した冷媒を複数の枝管を通じて第３熱源側熱交換器１３ｃに流入させる。第４ヘッダー１４ｄは、第３熱源側熱交換器１３ｃを冷房運転モード時の凝縮器及び蒸発器として使用する際に、第３熱源側熱交換器１３ｃから複数の枝管に流出した冷媒を、主配管を通じて直列並列切り替え配管６に流出させる。 The fourth header 14d has a plurality of branch pipes, which are thin pipes connected to the heat transfer pipes of the third heat source side heat exchanger 13c, and a main pipe to which the plurality of branch pipes are connected. The main pipe is connected to the series-parallel switching pipe 6 and the series outlet pipe 7. The lower part of the main pipe is connected to the series-parallel switching pipe 6 and the series outlet pipe 7. When the third heat source side heat exchanger 13c is used as the defrosting operation mode condenser, the fourth header 14d allows the refrigerant flowing into the main pipe from the series-parallel switching pipe 6 to heat the third heat source side through a plurality of branch pipes. It flows into the exchanger 13c. The fourth header 14d receives the refrigerant flowing out from the third heat source side heat exchanger 13c into a plurality of branch pipes when the third heat source side heat exchanger 13c is used as a condenser and an evaporator in the cooling operation mode. It flows out to the series-parallel switching pipe 6 through the main pipe.
　第１分配器１５ａは、第１熱源側熱交換器１３ａを蒸発器として使用する際に、第１熱源側熱交換器１３ａの入口側の冷媒流路となる位置に設けられている。 The first distributor 15a is provided at a position that serves as a refrigerant flow path on the inlet side of the first heat source side heat exchanger 13a when the first heat source side heat exchanger 13a is used as an evaporator.
　第１分配器１５ａは、第１熱源側熱交換器１３ａの伝熱管にそれぞれ接続される複数の細い配管と、複数の細い配管を一つに合流させた合流部である本体と、を有している。本体は、並列出入口配管につながれている第１出入口配管９ａに接続されている。第１分配器１５ａは、第１熱源側熱交換器１３ａを凝縮器として使用する際に、第１熱源側熱交換器１３ａから複数の細い配管に流出した冷媒を、本体を通じて第１出入口配管９ａに流出させる。第１分配器１５ａは、第１熱源側熱交換器１３ａを蒸発器として使用する際に、第１出入口配管９ａから本体に流入した冷媒を、複数の細い配管を通じて第１熱源側熱交換器１３ａに流入させる。 The first distributor 15a has a plurality of thin pipes connected to the heat transfer tubes of the first heat source side heat exchanger 13a, and a main body which is a confluence portion in which the plurality of thin pipes are merged into one. ing. The main body is connected to the first entrance / exit pipe 9a connected to the parallel entrance / exit pipe. When the first heat source side heat exchanger 13a is used as a condenser, the first distributor 15a allows the refrigerant flowing out from the first heat source side heat exchanger 13a to a plurality of thin pipes to flow through the main body to the first inlet / outlet pipe 9a. Leak to. When the first heat source side heat exchanger 13a is used as an evaporator, the first distributor 15a allows the refrigerant flowing into the main body from the first inlet / outlet pipe 9a to pass through a plurality of thin pipes to the first heat source side heat exchanger 13a. Inflow to.
　第２分配器１５ｂは、第２熱源側熱交換器１３ｂを蒸発器として使用する際に、第２熱源側熱交換器１３ｂの入口側の冷媒流路となる位置に設けられている。 The second distributor 15b is provided at a position that serves as a refrigerant flow path on the inlet side of the second heat source side heat exchanger 13b when the second heat source side heat exchanger 13b is used as an evaporator.
　第２分配器１５ｂは、第２熱源側熱交換器１３ｂの伝熱管にそれぞれ接続される複数の細い配管と、複数の細い配管を一つに合流させた合流部である本体と、を有している。本体は、並列出入口配管につながれている第２出入口配管９ｂに接続されている。第２分配器１５ｂは、第２熱源側熱交換器１３ｂを凝縮器として使用する際に、第２熱源側熱交換器１３ｂから複数の細い配管に流出した冷媒を、本体を通じて第２出入口配管９ｂに流出させる。第２分配器１５ｂは、第２熱源側熱交換器１３ｂを蒸発器として使用する際に、第２出入口配管９ｂから本体に流入した冷媒を、複数の細い配管を通じて第２熱源側熱交換器１３ｂに流入させる。 The second distributor 15b has a plurality of thin pipes connected to the heat transfer tubes of the second heat source side heat exchanger 13b, and a main body which is a confluence portion in which the plurality of thin pipes are merged into one. ing. The main body is connected to a second entrance / exit pipe 9b connected to a parallel entrance / exit pipe. When the second heat source side heat exchanger 13b is used as a condenser, the second distributor 15b allows the refrigerant flowing out from the second heat source side heat exchanger 13b to a plurality of thin pipes to flow through the main body to the second inlet / outlet pipe 9b. Leak to. When the second heat source side heat exchanger 13b is used as an evaporator, the second distributor 15b allows the refrigerant flowing into the main body from the second inlet / outlet pipe 9b to pass through the plurality of thin pipes to the second heat source side heat exchanger 13b. Inflow to.
　直列並列切り替え配管６は、第４ヘッダー１４ｄと第２ヘッダー１４ｂと、第２本管５ｂを繋いでいる。直列並列切り替え配管６は第３熱源側熱交換器１３ｃを蒸発器として使用する際に、第４ヘッダー１４ｄから流出した冷媒を第１開度調整装置３３を介して、第２ヘッダー１４ｂの出口に冷媒を流出させる。 The series-parallel switching pipe 6 connects the fourth header 14d, the second header 14b, and the second main pipe 5b. When the third heat source side heat exchanger 13c is used as an evaporator, the series-parallel switching pipe 6 sends the refrigerant flowing out from the fourth header 14d to the outlet of the second header 14b via the first opening degree adjusting device 33. Let the refrigerant flow out.
　直列並列切り替え配管６には、第１開度調整装置３３が設けられている。 The series-parallel switching pipe 6 is provided with a first opening degree adjusting device 33.
　第１出入口配管９ａは、第１分配器１５ａと並列出入口配管８とを繋いでいる。第１出入口配管９ａは、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃを蒸発器として使用する際に、低乾き度の二相状態もしくは液状態の低圧冷媒を、第１分配器１５ａを介して、第１熱源側熱交換器１３ａに流入させる。 The first entrance / exit pipe 9a connects the first distributor 15a and the parallel entrance / exit pipe 8. The first inlet / outlet pipe 9a is in a two-phase state with low dryness when the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as evaporators. The liquid low-pressure refrigerant flows into the first heat source side heat exchanger 13a via the first distributor 15a.
　第２出入口配管９ｂは、第２分配器１５ｂと並列出入口配管８とを繋いでいる。第２出入口配管９ｂは、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃを蒸発器として使用する際に、低乾き度の二相状態もしくは液状態の低圧冷媒を、第２開度調整装置３４及び第２分配器１５ｂを介して、第２熱源側熱交換器１３ｂに流入させる。 The second entrance / exit pipe 9b connects the second distributor 15b and the parallel entrance / exit pipe 8. The second inlet / outlet pipe 9b is in a two-phase state with low dryness when the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as evaporators. The liquid low-pressure refrigerant flows into the second heat source side heat exchanger 13b via the second opening degree adjusting device 34 and the second distributor 15b.
　第２出入口配管９ｂには、第２開度調整装置３４が設けられている。 A second opening degree adjusting device 34 is provided in the second entrance / exit pipe 9b.
　第３出入口配管９ｃは、第３ヘッダー１４ｃと並列出入口配管８とを繋いでいる。第３出入口配管９ｃは、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃを蒸発器として使用する際に、低乾き度の二相状態もしくは液状態の低圧冷媒を、第３ヘッダー１４ｃを介して、第３熱源側熱交換器１３ｃに流入させる。 The third entrance / exit pipe 9c connects the third header 14c and the parallel entrance / exit pipe 8. The third inlet / outlet pipe 9c is in a two-phase state with low dryness when the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as evaporators. The liquid low-pressure refrigerant flows into the third heat source side heat exchanger 13c via the third header 14c.
　並列出入口配管８は第１出入口配管９ａと、第２出入口配管９ｂと、第３出入口配管９ｃが合流して第２主管４ｂと、を繋いでいる。並列出入口配管８は、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃを蒸発器として使用する際に、低乾き度の二相状態もしくは液状態の低圧冷媒を、第１開閉装置３１を介して第１出入口配管９ａ、第２出入口配管９ｂ及び第３出入口配管９ｃに分岐させて流入させる。並列出入口配管８には、第１開閉装置３１が設けられている。 The parallel inlet / outlet pipe 8 connects the first inlet / outlet pipe 9a, the second inlet / outlet pipe 9b, and the third inlet / outlet pipe 9c to the second main pipe 4b. The parallel inlet / outlet pipe 8 is in a two-phase state or liquid with low dryness when the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as evaporators. The low-pressure refrigerant in the state is branched into the first inlet / outlet pipe 9a, the second inlet / outlet pipe 9b, and the third inlet / outlet pipe 9c via the first opening / closing device 31. The parallel entrance / exit pipe 8 is provided with a first switchgear 31.
　直列出口配管７は、第４ヘッダー１４ｄと、第２主管４ｂと、を第２開閉装置３２を介して繋いでいる。直列出口配管７は、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃを冷房運転モード時の凝縮器として使用する際に、第２開閉装置３２を介して高圧の液冷媒を第２主管４ｂに流入させる。 The series outlet pipe 7 connects the fourth header 14d and the second main pipe 4b via the second switchgear 32. The series outlet pipe 7 is a second opening / closing device when the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as a condenser in the cooling operation mode. A high-pressure liquid refrigerant flows into the second main pipe 4b via the 32.
　直列出口配管７には、第２開閉装置３２が設けられている。 The series outlet pipe 7 is provided with a second switchgear 32.
　第１開閉装置３１は、並列出入口配管８に配置され、第２主管４ｂから並列出入口配管８へと流入する冷媒の通過又は遮断を行う。すなわち第１開閉装置３１は、冷房運転モード時に第１熱源側熱交換器１３ａ及び第２熱源側熱交換器１３ｂから流出した冷媒が第２主管４ｂに流入させないように閉となる。また暖房運転モード時には第２主管４ｂから流出した冷媒が並列出入口配管８へと流入させるように開となる。さらに除霜運転モード時には第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃから流出した冷媒が第２主管４ｂに流入させるように開となる。 The first switchgear 31 is arranged in the parallel inlet / outlet pipe 8 and passes or shuts off the refrigerant flowing from the second main pipe 4b into the parallel inlet / outlet pipe 8. That is, the first opening / closing device 31 is closed so that the refrigerant flowing out from the first heat source side heat exchanger 13a and the second heat source side heat exchanger 13b does not flow into the second main pipe 4b in the cooling operation mode. Further, in the heating operation mode, the refrigerant flowing out from the second main pipe 4b is opened so as to flow into the parallel inlet / outlet pipe 8. Further, in the defrosting operation mode, the refrigerant flowing out from the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c is opened so as to flow into the second main pipe 4b.
　第１開閉装置３１は、開閉弁であり、たとえば二方弁、電磁弁、電子式膨張弁などの冷媒の流路を開閉できるもので構成される。 The first switchgear 31 is an on-off valve, and is configured to open and close the flow path of the refrigerant such as a two-way valve, a solenoid valve, and an electronic expansion valve.
　第２開閉装置３２は、直列出口配管７に配置され、直列出口配管７を流通する冷媒の通過又は遮断を行う。すなわち、第２開閉装置３２は、冷房運転モード時に第４ヘッダー１４ｄを流出した冷媒を第２主管へと流入させるように開となる。また暖房運転モード時には第２主管から流出した冷媒が第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃを通過せずに第２本管５ｂへと流入させないように閉となる。さらに除霜運転モード時には第２本管から流出した冷媒が第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃを通過せずに第２主管へと流出させないように閉となる。 The second switchgear 32 is arranged in the series outlet pipe 7 and passes or shuts off the refrigerant flowing through the series outlet pipe 7. That is, the second switchgear 32 is opened so that the refrigerant flowing out of the fourth header 14d flows into the second main pipe in the cooling operation mode. Further, in the heating operation mode, the refrigerant flowing out from the second main pipe does not pass through the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c to the second main pipe 5b. It is closed so that it does not flow in. Further, in the defrosting operation mode, the refrigerant flowing out from the second main pipe is closed so as not to flow out to the second main pipe without passing through the second heat source side heat exchanger 13b and the third heat source side heat exchanger 13c.
　第２開閉装置３２は、開閉弁であり、たとえば二方弁、電磁弁、電子式膨張弁などの冷媒の流路を開閉できるもので構成される。 The second switchgear 32 is an on-off valve, and is configured to open and close the flow path of the refrigerant such as a two-way valve, a solenoid valve, and an electronic expansion valve.
　第１開度調整装置３３は、直列並列切り替え配管６に配置され、直列並列切り替え配管６を流通する冷媒の通過又は遮断を行う。すなわち第１開度調整装置３３は、冷房運転モード時に高温高圧の冷媒を第３熱源側熱交換器１３ｃに流入させないように閉となる。また暖房運転モード時には並列出入口配管から第３熱源側熱交換器１３ｃに流入する冷媒の量を調整するためにそのＣｖ値を調整するように動作させる。さらに除霜運転モード時には高温高圧の冷媒を第３熱源側熱交換器１３ｃに流入させるように開となる。 The first opening degree adjusting device 33 is arranged in the series-parallel switching pipe 6 and passes or shuts off the refrigerant flowing through the series-parallel switching pipe 6. That is, the first opening degree adjusting device 33 is closed so that the high temperature and high pressure refrigerant does not flow into the third heat source side heat exchanger 13c in the cooling operation mode. Further, in the heating operation mode, the Cv value is adjusted in order to adjust the amount of the refrigerant flowing into the third heat source side heat exchanger 13c from the parallel inlet / outlet pipe. Further, in the defrosting operation mode, the high-temperature and high-pressure refrigerant is opened so as to flow into the third heat source side heat exchanger 13c.
　第１開度調整装置３３は、たとえば電子式膨張弁などの開度変化により冷媒の流量を調整できる絞り装置で構成される。 The first opening degree adjusting device 33 is composed of a throttle device capable of adjusting the flow rate of the refrigerant by changing the opening degree of, for example, an electronic expansion valve.
　第２開度調整装置３４は、第２出入口配管９ｂに配置され、第２出入口配管９ｂを流通する冷媒の通過又は遮断を行う。すなわち第２開度調整装置３４は冷房運転モード時に第２熱源側熱交換器１３ｂから流出した冷媒を並列出入口配管８に流入させるように開となる。また暖房運転モード時には、並列出入口配管から第２熱源側熱交換器１３ｂに流入する冷媒の量を調整するためにそのＣｖ値を調整するように動作させる。さらに除霜運転モード時には第２熱源側熱交換器１３ｂから流出した冷媒を並列出入口配管８に流入させるように開となる。 The second opening / closing adjusting device 34 is arranged in the second inlet / outlet pipe 9b, and passes or shuts off the refrigerant flowing through the second inlet / outlet pipe 9b. That is, the second opening degree adjusting device 34 is opened so that the refrigerant flowing out from the second heat source side heat exchanger 13b flows into the parallel inlet / outlet pipe 8 in the cooling operation mode. Further, in the heating operation mode, the Cv value is adjusted in order to adjust the amount of the refrigerant flowing into the second heat source side heat exchanger 13b from the parallel inlet / outlet pipe. Further, in the defrosting operation mode, the refrigerant flowing out from the second heat source side heat exchanger 13b is opened so as to flow into the parallel inlet / outlet pipe 8.
　第２開度調整装置３４は、たとえば電子式膨張弁などの開度変化により冷媒の流量を調整できる絞り装置で構成される。 The second opening degree adjusting device 34 is composed of a throttle device capable of adjusting the flow rate of the refrigerant by changing the opening degree of, for example, an electronic expansion valve.
［室内機２］
　室内機２は、主回路の構成要素として、負荷側熱交換器２１と、負荷側絞り装置２２と、を有している。 [Indoor unit 2]
The indoor unit 2 has a load-side heat exchanger 21 and a load-side throttle device 22 as components of the main circuit.
　負荷側熱交換器２１は、第１主管４ａ及び第２主管４ｂを介して室外機１に接続されている。負荷側熱交換器２１は、室内空間に通じる空気と第１主管４ａ又は第２主管４ｂを流通して来る冷媒との間で熱交換を行い、室内空間に供給するための暖房用空気あるいは冷房用空気を生成する。なお、負荷側熱交換器２１には、図示しないファンなどの送風機から室内空気が送風される。 The load side heat exchanger 21 is connected to the outdoor unit 1 via the first main pipe 4a and the second main pipe 4b. The load-side heat exchanger 21 exchanges heat between the air leading to the indoor space and the refrigerant flowing through the first main pipe 4a or the second main pipe 4b, and supplies heating air or cooling to the indoor space. Generates air for use. Indoor air is blown to the load side heat exchanger 21 from a blower such as a fan (not shown).
　負荷側絞り装置２２は、たとえば電子式膨張弁などの開度が変更可能に制御されるもので構成され、減圧弁あるいは膨張弁としての機能を有して冷媒を減圧して膨張させるものである。負荷側絞り装置２２は、冷房運転モード時及び除霜運転モード時において負荷側熱交換器２１の上流側に設けられている。 The load-side throttle device 22 is composed of, for example, an electronic expansion valve whose opening degree is mutably controlled, has a function as a pressure reducing valve or an expansion valve, and decompresses and expands the refrigerant. .. The load-side throttle device 22 is provided on the upstream side of the load-side heat exchanger 21 in the cooling operation mode and the defrosting operation mode.
　制御装置６０は、マイコンなどで構成されて室外機１に設けられており、各種センサーにて検出された検出情報及びリモコンからの指示に基づいて、空気調和装置１００の各種機器を制御する。制御装置６０が制御する対象は、圧縮機１０の駆動周波数、ファン１６のＯＮ又はＯＦＦを含む回転数、第１四方弁１１の切り替え、第２四方弁１２の切り替え、第１開閉装置３１の開閉、第２開閉装置３２の開閉、第１開度調整装置３３の開度もしくは開閉、第２開度調整装置３４の開度もしくは開閉、負荷側絞り装置２２の開度などである。このように制御装置６０が各種機器を制御することにより、後述する各運転モードを実行する。 The control device 60 is composed of a microcomputer or the like and is provided in the outdoor unit 1, and controls various devices of the air conditioner 100 based on the detection information detected by various sensors and the instruction from the remote controller. The objects controlled by the control device 60 are the drive frequency of the compressor 10, the rotation speed including ON or OFF of the fan 16, the switching of the first four-way valve 11, the switching of the second four-way valve 12, and the opening and closing of the first switchgear 31. , Opening / closing of the second opening / closing device 32, opening / closing / opening / closing of the first opening / closing device 33, opening / closing / opening / closing of the second opening / closing device 34, opening / closing of the load side throttle device 22 and the like. By controlling various devices in this way, the control device 60 executes each operation mode described later.
　制御装置６０は、専用のハードウェア、又はメモリに格納されるプログラムを実行するＣＰＵ（Ｃｅｎｔｒａｌ　Ｐｒｏｃｅｓｓｉｎｇ　Ｕｎｉｔ、中央処理装置、処理装置、演算装置、マイクロプロセッサ、マイクロコンピュータ、プロセッサともいう）で構成される。
　制御装置６０が専用のハードウェアである場合、制御装置６０は、例えば、単一回路、複合回路、ＡＳＩＣ（Ａｐｐｌｉｃａｔｉｏｎ　Ｓｐｅｃｉｆｉｃ　Ｉｎｔｅｇｒａｔｅｄ　Ｃｉｒｃｕｉｔ）、ＦＰＧＡ（Ｆｉｅｌｄ　Ｐｒｏｇｒａｍｍａｂｌｅ　Ｇａｔｅ　Ａｒｒａｙ）、又はこれらを組み合わせたものが該当する。制御装置６０が実現する各機能部のそれぞれを、個別のハードウェアで実現してもよいし、各機能部を一つのハードウェアで実現してもよい。 The control device 60 is composed of dedicated hardware or a CPU (also referred to as a central processing unit, a processing unit, an arithmetic unit, a microprocessor, a microprocessor, or a processor) that executes a program stored in a memory. ..
When the control device 60 is dedicated hardware, the control device 60 corresponds to, for example, a single circuit, a composite circuit, an ASIC (Application Specific Integrated Circuit), an FPGA (Field Programmable Gate Array), or a combination thereof. To do. Each of the functional units realized by the control device 60 may be realized by individual hardware, or each functional unit may be realized by one hardware.
　制御装置６０がＣＰＵの場合、制御装置６０が実行する各機能は、ソフトウェア、ファームウェア、又はソフトウェアとファームウェアとの組み合わせにより実現される。ソフトウェア及びファームウェアはプログラムとして記述され、メモリに格納される。ＣＰＵは、メモリに格納されたプログラムを読み出して実行することにより、制御装置６０の各機能を実現する。ここで、メモリは、例えば、ＲＡＭ、ＲＯＭ、フラッシュメモリ、ＥＰＲＯＭ、ＥＥＰＲＯＭ等の、不揮発性又は揮発性の半導体メモリである。
　なお、制御装置６０の機能の一部を専用のハードウェアで実現し、一部をソフトウェア又はファームウェアで実現するようにしてもよい。 When the control device 60 is a CPU, each function executed by the control device 60 is realized by software, firmware, or a combination of software and firmware. Software and firmware are written as programs and stored in memory. The CPU realizes each function of the control device 60 by reading and executing a program stored in the memory. Here, the memory is a non-volatile or volatile semiconductor memory such as a RAM, a ROM, a flash memory, an EPROM, or an EEPROM.
It should be noted that a part of the functions of the control device 60 may be realized by dedicated hardware, and a part may be realized by software or firmware.
　なお、制御装置６０は、室外機１に設けられている場合について例示している。しかし、制御装置は、ユニット毎に設けてもよいし、室内機２に設けてもよい。 The case where the control device 60 is provided in the outdoor unit 1 is illustrated. However, the control device may be provided for each unit or may be provided in the indoor unit 2.
１－２．動作
　次に、空気調和装置１００が実行する各運転モードについて説明する。空気調和装置１００は、室内機２からの指示に基づいて、冷房運転モード又は暖房運転モード、また制御装置６０からの指示に基づいて除霜運転モードを行う。
　なお、図１に示す空気調和装置１００が実行する運転モードには、駆動している室内機２が冷房運転を実行する３つの冷房運転モード、駆動している室内機２が暖房運転を実行する暖房運転モード、駆動している空気調和装置１００が除霜運転を実行する除霜運転モードがある。 1-2. Operation Next, each operation mode executed by the air conditioner 100 will be described. The air conditioner 100 performs a cooling operation mode or a heating operation mode based on an instruction from the indoor unit 2, and a defrosting operation mode based on an instruction from the control device 60.
The operation modes executed by the air conditioner 100 shown in FIG. 1 include three cooling operation modes in which the driving indoor unit 2 executes the cooling operation, and the driving indoor unit 2 executes the heating operation. There is a heating operation mode and a defrosting operation mode in which the driving air conditioner 100 executes a defrosting operation.
　以下に、各運転モードについて、冷媒の流れと共に説明する。 Below, each operation mode will be described together with the flow of the refrigerant.
［冷房運転モード］
　図２は、実施の形態１に係る空気調和装置１００の冷房運転モード時における冷媒の流れを示す冷媒回路図である。 [Cooling operation mode]
FIG. 2 is a refrigerant circuit diagram showing the flow of the refrigerant in the cooling operation mode of the air conditioner 100 according to the first embodiment.
　図２では、負荷側熱交換器２１で冷熱大負荷が発生している場合を例に大負荷冷房運転モードの冷媒の流れについて説明する。なお、図２では、冷媒の流れ方向を実線矢印で示している。 In FIG. 2, the flow of the refrigerant in the heavy load cooling operation mode will be described by taking the case where a large cooling heat load is generated in the load side heat exchanger 21 as an example. In FIG. 2, the flow direction of the refrigerant is indicated by a solid arrow.
　図２に示すように、低温低圧の冷媒が圧縮機１０によって圧縮され、高温高圧のガス冷媒になって吐出される。圧縮機１０から吐出された高温高圧のガス冷媒は、第１四方弁１１と第２四方弁１２とに分岐して流入する。そして、第１四方弁１１に流入した冷媒は、第１本管５ａを通じて、第１熱源側熱交換器１３ａに流入する。 As shown in FIG. 2, the low-temperature and low-pressure refrigerant is compressed by the compressor 10 and discharged as a high-temperature and high-pressure gas refrigerant. The high-temperature and high-pressure gas refrigerant discharged from the compressor 10 branches into the first four-way valve 11 and the second four-way valve 12 and flows in. Then, the refrigerant that has flowed into the first four-way valve 11 flows into the first heat source side heat exchanger 13a through the first main pipe 5a.
　また、第２四方弁１２に流入した冷媒は、第２本管５ｂを通じて、第２熱源側熱交換器１３ｂに流入する。このとき、第１開度調整装置３３は、閉状態に切り替えられている。よって、第２本管５ｂを流通する高温高圧のガス冷媒は、直列並列切り替え配管６を介して第３熱源側熱交換器１３ｃに流入しない。 Further, the refrigerant flowing into the second four-way valve 12 flows into the second heat source side heat exchanger 13b through the second main pipe 5b. At this time, the first opening degree adjusting device 33 is switched to the closed state. Therefore, the high-temperature and high-pressure gas refrigerant flowing through the second main pipe 5b does not flow into the third heat source side heat exchanger 13c via the series-parallel switching pipe 6.
　第１熱源側熱交換器１３ａに流入したガス冷媒は、第１熱源側熱交換器１３ａにてファン１６から供給される室外空気に放熱しながら高圧の二相もしくは液冷媒になる。また、第２熱源側熱交換器１３ｂに流入したガス冷媒は、第２熱源側熱交換器１３ｂにてファン１６から供給される室外空気に放熱しながら高圧の二相もしくは液冷媒になる。 The gas refrigerant flowing into the first heat source side heat exchanger 13a becomes a high-pressure two-phase or liquid refrigerant while radiating heat to the outdoor air supplied from the fan 16 by the first heat source side heat exchanger 13a. Further, the gas refrigerant flowing into the second heat source side heat exchanger 13b becomes a high-pressure two-phase or liquid refrigerant while radiating heat to the outdoor air supplied from the fan 16 by the second heat source side heat exchanger 13b.
　第１熱源側熱交換器１３ａから流出した高圧の二相もしくは液冷媒は、第１出入口配管９ａを通って並列出入口配管８に流入する。また、第２熱源側熱交換器１３ｂから流出した高圧の二相もしくは液冷媒は、第２出入口配管９ｂを通って並列出入口配管８に流入する。これにより、第１熱源側熱交換器１３ａから流出した高圧の二相もしくは液冷媒と、第２熱源側熱交換器１３ｂから流出した高圧の二相もしくは液冷媒と、が並列出入口配管８で合流する。このとき、第１開閉装置３１は、閉状態に切り替えられている。よって、第１熱源側熱交換器１３ａ又は第２熱源側熱交換器１３ｂから流出した高圧の二相もしくは液冷媒は、並列出入口配管８を介して第２主管４ｂに流入しない。 The high-pressure two-phase or liquid refrigerant flowing out of the first heat source side heat exchanger 13a flows into the parallel inlet / outlet pipe 8 through the first inlet / outlet pipe 9a. Further, the high-pressure two-phase or liquid refrigerant flowing out from the second heat source side heat exchanger 13b flows into the parallel inlet / outlet pipe 8 through the second inlet / outlet pipe 9b. As a result, the high-pressure two-phase or liquid refrigerant flowing out of the first heat source side heat exchanger 13a and the high-pressure two-phase or liquid refrigerant flowing out of the second heat source side heat exchanger 13b merge at the parallel inlet / outlet pipe 8. To do. At this time, the first switchgear 31 is switched to the closed state. Therefore, the high-pressure two-phase or liquid refrigerant flowing out of the first heat source side heat exchanger 13a or the second heat source side heat exchanger 13b does not flow into the second main pipe 4b via the parallel inlet / outlet pipe 8.
　合流した高圧の二相もしくは液冷媒は、第３熱源側熱交換器１３ｃに流入する。そして、流入する高圧の二相もしくは液冷媒は、第３熱源側熱交換器１３ｃにてファン１６から供給される室外空気に放熱しながら高圧液冷媒になる。この高圧液冷媒は、開状態に切り替えられている第２開閉装置３２が配置された直列出口配管７を通って室外機１から流出し、第２主管４ｂを通り、室内機２へ流入する。
　すなわち、室外機１では、冷房運転モード時に、上流側にて第１熱源側熱交換器１３ａと第２熱源側熱交換器１３ｂとが互いに並列に、かつ、下流側にて第１熱源側熱交換器１３ａ及び第２熱源側熱交換器１３ｂに対して第３熱源側熱交換器１３ｃが直列に接続される。 The combined high-pressure two-phase or liquid refrigerant flows into the third heat source side heat exchanger 13c. Then, the inflowing high-pressure two-phase or liquid refrigerant becomes a high-pressure liquid refrigerant while radiating heat to the outdoor air supplied from the fan 16 by the third heat source side heat exchanger 13c. This high-pressure liquid refrigerant flows out from the outdoor unit 1 through the series outlet pipe 7 in which the second switchgear 32 switched to the open state is arranged, passes through the second main pipe 4b, and flows into the indoor unit 2.
That is, in the outdoor unit 1, in the cooling operation mode, the first heat source side heat exchanger 13a and the second heat source side heat exchanger 13b are parallel to each other on the upstream side, and the first heat source side heat is on the downstream side. The third heat source side heat exchanger 13c is connected in series to the exchanger 13a and the second heat source side heat exchanger 13b.
　冷房運転モード時においては、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃを凝縮器として使用し、第１四方弁１１で圧縮機１０から吐出された冷媒を第１熱源側熱交換器１３ａに供給し、第２四方弁１２で圧縮機１０から吐出された冷媒を第２熱源側熱交換器１３ｂに供給し、第１開閉装置３１を開とし、第２開閉装置３２を開とし、第１開度調整装置３３を閉とし、第２開度調整装置３４を開として構成される。 In the cooling operation mode, the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as condensers, and the first four-way valve 11 is used from the compressor 10. The discharged refrigerant is supplied to the first heat source side heat exchanger 13a, the refrigerant discharged from the compressor 10 by the second four-way valve 12 is supplied to the second heat source side heat exchanger 13b, and the first opening / closing device 31 is operated. The second opening / closing device 32 is opened, the first opening / closing adjusting device 33 is closed, and the second opening / closing adjusting device 34 is opened.
　室内機２では、高圧液冷媒は、負荷側絞り装置２２で膨張させられて、低温低圧の気液二相状態の冷媒になる。気液二相状態の冷媒は、蒸発器として使用する負荷側熱交換器２１に流入し、室内空気から吸熱することにより、室内空気を冷却しながら低温低圧のガス冷媒になる。この際、負荷側絞り装置２２の開度は、過熱度が一定になるように制御装置６０により制御される。負荷側熱交換器２１から流出したガス冷媒は、第１主管４ａを通って再び室外機１へ流入する。室外機１に流入したガス冷媒は、第２四方弁１２を通って圧縮機１０へ再度吸入される。 In the indoor unit 2, the high-pressure liquid refrigerant is expanded by the load-side throttle device 22 to become a low-temperature low-pressure gas-liquid two-phase state refrigerant. The gas-liquid two-phase state refrigerant flows into the load side heat exchanger 21 used as an evaporator and absorbs heat from the indoor air to become a low-temperature low-pressure gas refrigerant while cooling the indoor air. At this time, the opening degree of the load side throttle device 22 is controlled by the control device 60 so that the degree of superheat becomes constant. The gas refrigerant flowing out of the load side heat exchanger 21 flows into the outdoor unit 1 again through the first main pipe 4a. The gas refrigerant that has flowed into the outdoor unit 1 is sucked into the compressor 10 again through the second four-way valve 12.
　以上より、冷房運転モードでは、第１熱源側熱交換器１３ａ及び第２熱源側熱交換器１３ｂに対して第３熱源側熱交換器１３ｃが直列冷媒流路として繋がる。これにより、冷媒の流速が上昇し、凝縮器の性能が向上できる。これによると、冷媒の流速が遅い場合の下流側の第３熱源側熱交換器１３ｃにて冷媒が液冷媒として溜まってしまう冷媒の寝込みが、抑制できる。 From the above, in the cooling operation mode, the third heat source side heat exchanger 13c is connected to the first heat source side heat exchanger 13a and the second heat source side heat exchanger 13b as a series refrigerant flow path. As a result, the flow velocity of the refrigerant increases, and the performance of the condenser can be improved. According to this, when the flow velocity of the refrigerant is slow, it is possible to prevent the refrigerant from accumulating as a liquid refrigerant in the third heat source side heat exchanger 13c on the downstream side.
　また、第１熱源側熱交換器１３ａには、分割無しで独立して配置され、１つの第１ヘッダー１４ａ及び１つの第１分配器１５ａが設けられている。加えて、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃは、一部分を一体に構成されている。しかし、第２熱源側熱交換器１３ｂには、１つの第２ヘッダー１４ｂ及び１つの第２分配器１５ｂが設けられている。また、第３熱源側熱交換器１３ｃには、１つの第３ヘッダー１４ｃ及び１つの第４ヘッダー１４ｄが設けられている。このため、１台の熱源側熱交換器に２個以上のヘッダー及び分配器を設ける構成に比して、コストが抑制できると共に、設置スペースが狭くできる。 Further, the first heat source side heat exchanger 13a is independently arranged without division, and is provided with one first header 14a and one first distributor 15a. In addition, the second heat source side heat exchanger 13b and the third heat source side heat exchanger 13c are partially integrally configured. However, the second heat source side heat exchanger 13b is provided with one second header 14b and one second distributor 15b. Further, the third heat source side heat exchanger 13c is provided with one third header 14c and one fourth header 14d. Therefore, the cost can be suppressed and the installation space can be narrowed as compared with the configuration in which two or more headers and distributors are provided in one heat source side heat exchanger.
　また、冷房運転モードでは、熱源側熱交換器を直列に接続した上流側、つまり並列に繋がれた第１熱源側熱交換器１３ａ及び第２熱源側熱交換器１３ｂの容積と、下流側、つまり第３熱源側熱交換器１３ｃの容積と、は、下流側に対して上流側を大きくするよう調整している。これは、全熱源側熱交換器の効率を最大とするべく、下流側の第３熱源側熱交換器１３ｃの流入冷媒を乾き度の低い冷媒になるように上流側と下流側との容積比を調整するためである。 Further, in the cooling operation mode, the volumes of the first heat source side heat exchanger 13a and the second heat source side heat exchanger 13b connected in parallel, that is, the upstream side in which the heat source side heat exchangers are connected in series, and the downstream side, That is, the volume of the third heat source side heat exchanger 13c is adjusted so that the upstream side is larger than the downstream side. In order to maximize the efficiency of the total heat source side heat exchanger, the volume ratio between the upstream side and the downstream side is such that the inflow refrigerant of the third heat source side heat exchanger 13c on the downstream side becomes a refrigerant with low dryness. This is to adjust.
［暖房運転モード］
　図３は、実施の形態１に係る空気調和装置１００の暖房運転モード時における冷媒の流れを示す冷媒回路図である。 [Heating operation mode]
FIG. 3 is a refrigerant circuit diagram showing the flow of the refrigerant in the heating operation mode of the air conditioner 100 according to the first embodiment.
　図３では、負荷側熱交換器２１で温熱負荷が発生している場合を例に暖房運転モードの冷媒の流れについて説明する。なお、図３では、冷媒の流れ方向を実線矢印で示している。 In FIG. 3, the flow of the refrigerant in the heating operation mode will be described by taking as an example a case where a thermal load is generated in the load side heat exchanger 21. In FIG. 3, the flow direction of the refrigerant is indicated by a solid arrow.
　図３に示すように、低温低圧の冷媒が圧縮機１０によって圧縮され、高温高圧のガス冷媒になって吐出される。圧縮機１０から吐出された高温高圧のガス冷媒は、第２四方弁１２を通り、室外機１から流出する。室外機１から流出した高温高圧のガス冷媒は、第１主管４ａを通り、負荷側熱交換器２１で室内空気に放熱することによって室内空間を暖房しながら液冷媒になる。この際、負荷側絞り装置２２の開度が、過冷却度が一定になるように制御装置６０により制御される。負荷側熱交換器２１から流出した液冷媒は、負荷側絞り装置２２で膨張させられて、中温中圧の気液二相状態の冷媒になり、第２主管４ｂを通って再び室外機１へ流入する。 As shown in FIG. 3, the low-temperature and low-pressure refrigerant is compressed by the compressor 10 and discharged as a high-temperature and high-pressure gas refrigerant. The high-temperature and high-pressure gas refrigerant discharged from the compressor 10 passes through the second four-way valve 12 and flows out from the outdoor unit 1. The high-temperature and high-pressure gas refrigerant flowing out of the outdoor unit 1 passes through the first main pipe 4a and is dissipated to the indoor air by the load side heat exchanger 21 to become a liquid refrigerant while heating the indoor space. At this time, the opening degree of the load side throttle device 22 is controlled by the control device 60 so that the degree of supercooling becomes constant. The liquid refrigerant flowing out from the load side heat exchanger 21 is expanded by the load side throttle device 22 to become a gas-liquid two-phase state refrigerant at medium temperature and medium pressure, and passes through the second main pipe 4b to the outdoor unit 1 again. Inflow.
　室外機１に流入した中温中圧の気液二相状態の冷媒は、開状態に切り替えられた第１開閉装置３１を通過し、並列出入口配管８へと流入する。並列出入口配管８に流入した冷媒は第１出入口配管９ａ、第２出入口配管９ｂ、第３出入口配管９ｃへと並行に流入し、それぞれ第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃへと流入する。このとき、第２開閉装置３２は、閉状態に切り替えられている。よって、第２主管４ｂを流通する冷媒は、直列並列切り替え配管６へと流入しない。 The medium-temperature, medium-pressure, gas-liquid, two-phase refrigerant that has flowed into the outdoor unit 1 passes through the first switchgear 31 that has been switched to the open state, and flows into the parallel inlet / outlet pipe 8. The refrigerant flowing into the parallel inlet / outlet pipe 8 flows into the first inlet / outlet pipe 9a, the second inlet / outlet pipe 9b, and the third inlet / outlet pipe 9c in parallel, and flows into the first heat source side heat exchanger 13a and the second heat source side heat exchanger, respectively. It flows into 13b and the third heat source side heat exchanger 13c. At this time, the second switchgear 32 is switched to the closed state. Therefore, the refrigerant flowing through the second main pipe 4b does not flow into the series-parallel switching pipe 6.
　ここで、第１開度調整装置３３は、暖房運転モード時に、各熱交換器が最適な冷媒循環量となるように第３熱源側熱交換器１３ｃに流入させる冷媒量を開度変化により調整する。また、第２開度調整装置３４は、暖房運転モード時に、各熱交換器が最適な冷媒循環量となるように第２熱源側熱交換器１３ｂに流入させる冷媒量を開度変化により調整する。 Here, the first opening degree adjusting device 33 adjusts the amount of refrigerant flowing into the third heat source side heat exchanger 13c by changing the opening degree so that each heat exchanger has an optimum refrigerant circulation amount in the heating operation mode. To do. Further, the second opening degree adjusting device 34 adjusts the amount of refrigerant flowing into the second heat source side heat exchanger 13b by changing the opening degree so that each heat exchanger has an optimum refrigerant circulation amount in the heating operation mode. ..
　第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃに流入した冷媒は、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃにて室外空気から吸熱しながら低温低圧のガス冷媒になる。 The refrigerant that has flowed into the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c is the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and The heat exchanger 13c on the third heat source side absorbs heat from the outdoor air and becomes a low-temperature low-pressure gas refrigerant.
　その後、第１熱源側熱交換器１３ａから流出する冷媒は、第１四方弁１１を通って、圧縮機１０の吸入側へ流入する。また、第３熱源側熱交換器１３ｃから流出する冷媒は、開状態に切り替えられている第２開度調整装置３４が配置された直列並列切り替え配管６を通過する。第３熱源側熱交換器１３ｃから流出して第２開度調整装置３４が配置された直列並列切り替え配管６を通過する冷媒は、第２本管５ｂにて、第２熱源側熱交換器１３ｂから流出する冷媒と合流し、第２四方弁１２を通って、圧縮機１０の吸入側へ流入する。 After that, the refrigerant flowing out of the first heat source side heat exchanger 13a flows into the suction side of the compressor 10 through the first four-way valve 11. Further, the refrigerant flowing out from the third heat source side heat exchanger 13c passes through the series-parallel switching pipe 6 in which the second opening degree adjusting device 34 that has been switched to the open state is arranged. The refrigerant that flows out of the third heat source side heat exchanger 13c and passes through the series-parallel switching pipe 6 in which the second opening degree adjusting device 34 is arranged is in the second main pipe 5b in the second heat source side heat exchanger 13b. It merges with the refrigerant flowing out from the compressor, passes through the second four-way valve 12, and flows into the suction side of the compressor 10.
　すなわち、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃを暖房運転モードとして使用する際に、第１熱源側熱交換器１３ａと第２熱源側熱交換器１３ｂと第３熱源側熱交換器１３ｃとが互いに並列に並列冷媒流路で接続される。 That is, when the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as the heating operation mode, the first heat source side heat exchanger 13a and the second heat source The side heat exchanger 13b and the third heat source side heat exchanger 13c are connected in parallel with each other by a parallel refrigerant flow path.
　並列冷媒流路は、第１四方弁１１で圧縮機１０から吐出された冷媒を遮断し、第２四方弁１２で圧縮機１０から吐出された冷媒を負荷側熱交換器２１に供給し、第１開閉装置３１を開とし、第２開閉装置３２を閉とし、第１開度調整装置３３を開とし、第２開度調整装置３４を開として構成される。 In the parallel refrigerant flow path, the first four-way valve 11 shuts off the refrigerant discharged from the compressor 10, and the second four-way valve 12 supplies the refrigerant discharged from the compressor 10 to the load side heat exchanger 21. 1 The opening / closing device 31 is opened, the second opening / closing device 32 is closed, the first opening / closing device 33 is opened, and the second opening / closing device 34 is open.
　以上より、暖房運転モード時では、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃが並列に繋がる。これにより、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃを流れる冷媒の圧力損失が低下し、蒸発器の性能が向上できる。 From the above, in the heating operation mode, the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are connected in parallel. As a result, the pressure loss of the refrigerant flowing through the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c is reduced, and the performance of the evaporator can be improved.
［除霜運転モード］
　図４は、実施の形態１に係る空気調和装置１００の除霜運転モード時における冷媒の流れを示す冷媒回路図である。 [Defrosting operation mode]
FIG. 4 is a refrigerant circuit diagram showing the flow of the refrigerant in the defrosting operation mode of the air conditioner 100 according to the first embodiment.
　図４では、冷媒の流れ方向を実線矢印で示している。 In FIG. 4, the flow direction of the refrigerant is indicated by a solid arrow.
　図４に示すように、低温低圧の冷媒が圧縮機１０によって圧縮され、高温高圧のガス冷媒になって吐出される。圧縮機１０から吐出された高温高圧のガス冷媒は、第１四方弁１１と第２四方弁１２とに分岐して流入する。そして、第１四方弁１１に流入した冷媒は、第１本管５ａを通じて、第１熱源側熱交換器１３ａに流入する。 As shown in FIG. 4, the low-temperature and low-pressure refrigerant is compressed by the compressor 10 and discharged as a high-temperature and high-pressure gas refrigerant. The high-temperature and high-pressure gas refrigerant discharged from the compressor 10 branches into the first four-way valve 11 and the second four-way valve 12 and flows in. Then, the refrigerant that has flowed into the first four-way valve 11 flows into the first heat source side heat exchanger 13a through the first main pipe 5a.
　また、第２四方弁１２に流入した冷媒は、第２本管５ｂを通じて、第２熱源側熱交換器１３ｂに流入する。このとき、第１開度調整装置３３は、開状態に切り替えられている。よって、第２本管５ｂを流通する高温高圧のガス冷媒は、直列並列切り替え配管６を介して第３熱源側熱交換器１３ｃに流入する。このとき、第２開閉装置３２は、閉状態に切り替えられている。よって直列並列切り替え配管６を流通する高温高圧のガス冷媒は、直列出口配管７を介して第２主管４ｂへと流入しない。 Further, the refrigerant flowing into the second four-way valve 12 flows into the second heat source side heat exchanger 13b through the second main pipe 5b. At this time, the first opening degree adjusting device 33 is switched to the open state. Therefore, the high-temperature and high-pressure gas refrigerant flowing through the second main pipe 5b flows into the third heat source side heat exchanger 13c via the series-parallel switching pipe 6. At this time, the second switchgear 32 is switched to the closed state. Therefore, the high-temperature and high-pressure gas refrigerant flowing through the series-parallel switching pipe 6 does not flow into the second main pipe 4b via the series outlet pipe 7.
　第１熱源側熱交換器１３ａに流入したガス冷媒は、第１熱源側熱交換器１３ａにて熱交換器へと着霜した霜を溶かしながら高圧の二相もしくは液冷媒になる。また、第２熱源側熱交換器１３ｂに流入したガス冷媒は、第２熱源側熱交換器１３ｂにて熱交換器へと着霜した霜を溶かしながら高圧の二相もしくは液冷媒になる。さらに第３熱源側熱交換器１３ｃに流入したガス冷媒は、第３熱源側熱交換器１３ｃにて熱交換器へと着霜した霜を溶かしながら高圧の二相もしくは液冷媒になる。 The gas refrigerant flowing into the first heat source side heat exchanger 13a becomes a high-pressure two-phase or liquid refrigerant while melting the frost frosted on the heat exchanger at the first heat source side heat exchanger 13a. Further, the gas refrigerant flowing into the second heat source side heat exchanger 13b becomes a high-pressure two-phase or liquid refrigerant while melting the frost frosted on the heat exchanger at the second heat source side heat exchanger 13b. Further, the gas refrigerant flowing into the third heat source side heat exchanger 13c becomes a high-pressure two-phase or liquid refrigerant while melting the frost frosted on the heat exchanger by the third heat source side heat exchanger 13c.
　第１熱源側熱交換器１３ａから流出した高圧の二相もしくは液冷媒は、第１出入口配管９ａを通って並列出入口配管８に流入する。また、第２熱源側熱交換器１３ｂから流出した高圧の二相もしくは液冷媒は、第２出入口配管９ｂを通って並列出入口配管８に流入する。さらに第３熱源側熱交換器１３ｃから流出した高圧の二相もしくは液冷媒は、第３出入口配管９ｃを通って並列出入口配管８に流入する。これにより、第１熱源側熱交換器１３ａから流出した高圧の二相もしくは液冷媒と、第２熱源側熱交換器１３ｂから流出した高圧の二相もしくは液冷媒と、第３熱源側熱交換器１３ｃから流出した高圧の二相もしくは液冷媒とが並列出入口配管８で合流する。このとき、第１開閉装置３１は、開状態に切り替えられている。よって、第１熱源側熱交換器１３ａ、又は第２熱源側熱交換器１３ｂ、さらに第３熱源側熱交換器１３ｃから流出した高圧の二相もしくは液冷媒は、並列出入口配管８を介して第２主管４ｂを通り、室内機２へ流入する。 The high-pressure two-phase or liquid refrigerant flowing out of the first heat source side heat exchanger 13a flows into the parallel inlet / outlet pipe 8 through the first inlet / outlet pipe 9a. Further, the high-pressure two-phase or liquid refrigerant flowing out from the second heat source side heat exchanger 13b flows into the parallel inlet / outlet pipe 8 through the second inlet / outlet pipe 9b. Further, the high-pressure two-phase or liquid refrigerant flowing out from the third heat source side heat exchanger 13c flows into the parallel inlet / outlet pipe 8 through the third inlet / outlet pipe 9c. As a result, the high-pressure two-phase or liquid refrigerant flowing out of the first heat source side heat exchanger 13a, the high-pressure two-phase or liquid refrigerant flowing out of the second heat source side heat exchanger 13b, and the third heat source side heat exchanger The high-pressure two-phase or liquid refrigerant flowing out from 13c merges at the parallel inlet / outlet pipe 8. At this time, the first opening / closing device 31 is switched to the open state. Therefore, the high-pressure two-phase or liquid refrigerant flowing out of the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c passes through the parallel inlet / outlet pipe 8. 2 Passes through the main pipe 4b and flows into the indoor unit 2.
　すなわち、室外機１では、除霜運転モード時に、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃが並列に接続される。 That is, in the outdoor unit 1, the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are connected in parallel in the defrosting operation mode.
　除霜運転モード時においては、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃを凝縮器として使用し、第１四方弁１１で圧縮機１０から吐出された冷媒を第１熱源側熱交換器１３ａに供給し、第２四方弁１２で圧縮機１０から吐出された冷媒を第２熱源側熱交換器１３ｂに供給し、第１開閉装置３１を開とし、第２開閉装置３２を閉とし、第１開度調整装置３３を開とし、第２開度調整装置３４を開として構成される。 In the defrosting operation mode, the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as condensers, and the compressor 10 is used by the first four-way valve 11. The refrigerant discharged from the compressor 10 is supplied to the first heat source side heat exchanger 13a, and the refrigerant discharged from the compressor 10 is supplied to the second heat source side heat exchanger 13b by the second four-way valve 12, and the first switching device 31 The second opening / closing device 32 is closed, the first opening / closing adjusting device 33 is opened, and the second opening / closing adjusting device 34 is opened.
　室内機２では、高圧液冷媒は、負荷側絞り装置２２で膨張させられて、低温低圧の気液二相状態の冷媒になる。気液二相状態の冷媒は、蒸発器として使用する負荷側熱交換器２１に流入し、室内空気から吸熱することにより、室内空気を冷却しながら低温低圧のガス冷媒になる。しかしながらこの際、負荷側絞り装置２２の開度は、開度が全開となるように制御装置６０により制御される。負荷側熱交換器２１から流出したガス冷媒は、第１主管４ａを通って再び室外機１へ流入する。室外機１に流入したガス冷媒は、第２四方弁１２を通って圧縮機１０へ再度吸入される。 In the indoor unit 2, the high-pressure liquid refrigerant is expanded by the load-side throttle device 22 to become a low-temperature low-pressure gas-liquid two-phase state refrigerant. The gas-liquid two-phase state refrigerant flows into the load side heat exchanger 21 used as an evaporator and absorbs heat from the indoor air to become a low-temperature low-pressure gas refrigerant while cooling the indoor air. However, at this time, the opening degree of the load side throttle device 22 is controlled by the control device 60 so that the opening degree is fully opened. The gas refrigerant flowing out of the load side heat exchanger 21 flows into the outdoor unit 1 again through the first main pipe 4a. The gas refrigerant that has flowed into the outdoor unit 1 is sucked into the compressor 10 again through the second four-way valve 12.
　以上より、除霜運転モードでは、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃが凝縮器として運転するにもかかわらず並列冷媒流路として繋がる。これにより、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃに対して高温高圧の冷媒が並列に流入し、最大の除霜能力を得る。 From the above, in the defrosting operation mode, the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c operate as a condenser, but as a parallel refrigerant flow path. Connect. As a result, the high-temperature and high-pressure refrigerant flows in parallel to the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c, and the maximum defrosting ability is obtained.
　図５は、実施の形態１に係る空気調和装置１００の制御装置６０の動作を説明するためのフローチャートである。 FIG. 5 is a flowchart for explaining the operation of the control device 60 of the air conditioner 100 according to the first embodiment.
　図５に示すように、制御装置６０が冷房運転モードであるか否かを判断する（Ｓ１１）。ステップＳ１１において、制御装置６０が冷房運転モードであると判断した場合（Ｓ１１のＹＥＳ）、熱交換器流路切替装置に第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ、第３熱源側熱交換器１３ｃの冷媒流路を直列冷媒流路に切り替える指示を行なう（Ｓ１２）。 As shown in FIG. 5, it is determined whether or not the control device 60 is in the cooling operation mode (S11). When it is determined in step S11 that the control device 60 is in the cooling operation mode (YES in S11), the heat exchanger flow path switching device includes the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the second. 3 An instruction is given to switch the refrigerant flow path of the heat source side heat exchanger 13c to the series refrigerant flow path (S12).
　具体的には、制御装置６０は、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃを凝縮器として使用し、第１四方弁１１で圧縮機１０から吐出された冷媒を第１熱源側熱交換器１３ａに供給し、第２四方弁１２で圧縮機１０から吐出された冷媒を第２熱源側熱交換器１３ｂに供給し、第１開閉装置３１を開とし、第２開閉装置３２を開とし、第１開度調整装置３３を閉とし、第２開度調整装置３４を開とするように制御を行なう。 Specifically, the control device 60 uses the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c as a condenser, and compresses with the first four-way valve 11. The refrigerant discharged from the machine 10 is supplied to the first heat source side heat exchanger 13a, and the refrigerant discharged from the compressor 10 is supplied to the second heat source side heat exchanger 13b by the second four-way valve 12, and the first opening / closing is performed. Control is performed so that the device 31 is opened, the second opening / closing device 32 is opened, the first opening / closing device 33 is closed, and the second opening / closing device 34 is opened.
　ステップＳ１１において、制御装置６０が冷房運転モードでないと判断した場合（Ｓ１１のＮＯ）及びステップＳ１２における処理の後、制御装置６０は暖房運転モードであるか否かを判断する（Ｓ１３）。 In step S11, when it is determined that the control device 60 is not in the cooling operation mode (NO in S11), and after the processing in step S12, it is determined whether or not the control device 60 is in the heating operation mode (S13).
　ステップＳ１３において、制御装置６０が暖房運転モードであると判断した場合（Ｓ１３のＹＥＳ）、制御装置６０は熱交換器流路切替装置に第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃの冷媒流路を並列冷媒流路に切り替える指示を行なう（Ｓ１４）。 When it is determined in step S13 that the control device 60 is in the heating operation mode (YES in S13), the control device 60 connects the heat exchanger flow path switching device to the first heat source side heat exchanger 13a and the second heat source side heat exchange. An instruction is given to switch the refrigerant flow path of the device 13b and the third heat source side heat exchanger 13c to the parallel refrigerant flow path (S14).
　具体的には、制御装置６０は、第１四方弁１１で圧縮機１０から吐出された冷媒を遮断し、第２四方弁１２で圧縮機１０から吐出された冷媒を負荷側熱交換器２１に供給し、第１開閉装置３１を開とし、第２開閉装置３２を閉とし、第１開度調整装置３３を開とし、第２開度調整装置３４を開とするように制御を行なう。 Specifically, the control device 60 shuts off the refrigerant discharged from the compressor 10 by the first four-way valve 11, and sends the refrigerant discharged from the compressor 10 by the second four-way valve 12 to the load side heat exchanger 21. The first opening / closing device 31 is opened, the second opening / closing device 32 is closed, the first opening / closing device 33 is opened, and the second opening / closing device 34 is opened.
　ステップＳ１３において、制御装置６０が暖房運転モードでないと判断した場合（Ｓ１３のＮＯ）及びステップＳ１４における処理の後、制御装置６０は除霜運転モードであるか否かを判断する（Ｓ１５）。 In step S13, when it is determined that the control device 60 is not in the heating operation mode (NO in S13), and after the processing in step S14, it is determined whether or not the control device 60 is in the defrosting operation mode (S15).
　ステップＳ１５において、制御装置６０が除霜運転モードであると判断した場合（Ｓ１５のＹＥＳ）、制御装置６０は熱交換器流路切替装置に第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃの冷媒流路を並列冷媒流路に切り替える指示を行なう（Ｓ１６）。 When it is determined in step S15 that the control device 60 is in the defrosting operation mode (YES in S15), the control device 60 is connected to the heat exchanger flow path switching device with the first heat source side heat exchanger 13a and the second heat source side heat. An instruction is given to switch the refrigerant flow paths of the exchanger 13b and the third heat source side heat exchanger 13c to parallel refrigerant flow paths (S16).
　具体的には、制御装置６０は、第１四方弁１１で圧縮機１０から吐出された冷媒を第１熱源側熱交換器１３ａに供給し、第２四方弁１２で圧縮機１０から吐出された冷媒を第２熱源側熱交換器１３ｂに供給し、第１開閉装置３１を開とし、第２開閉装置３２を閉とし、第１開度調整装置３３を開とし、第２開度調整装置３４を開とするように制御を行なう。 Specifically, the control device 60 supplies the refrigerant discharged from the compressor 10 by the first four-way valve 11 to the first heat source side heat exchanger 13a, and discharges the refrigerant from the compressor 10 by the second four-way valve 12. The refrigerant is supplied to the second heat source side heat exchanger 13b, the first opening / closing device 31 is opened, the second opening / closing device 32 is closed, the first opening / closing device 33 is opened, and the second opening / closing device 34 is opened. Is controlled so as to open.
　ステップＳ１５において、制御装置６０が除霜運転モードでないと判断した場合（Ｓ１５のＮＯ）及びステップＳ１６における処理の後、ステップＳ１１に戻る。 If it is determined in step S15 that the control device 60 is not in the defrosting operation mode (NO in S15), and after the processing in step S16, the process returns to step S11.
１－３．効果
　以上、実施の形態１によれば、空気調和装置１００は、圧縮機１０、第１四方弁１１、第２四方弁１２、負荷側熱交換器２１、負荷側絞り装置２２並びに少なくとも第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃが冷媒配管３で接続されて冷媒が循環する主回路を備えている。 1-3. Effect As described above, according to the first embodiment, the air conditioner 100 includes the compressor 10, the first four-way valve 11, the second four-way valve 12, the load side heat exchanger 21, the load side throttle device 22, and at least the first heat source. The side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are connected by a refrigerant pipe 3 to include a main circuit in which the refrigerant circulates.
　第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃを冷房運転モードとして使用する際に、上流側にて第１熱源側熱交換器１３ａと第２熱源側熱交換器１３ｂとが互いに並列に、かつ、下流側にて第１熱源側熱交換器１３ａ及び第２熱源側熱交換器１３ｂに対して第３熱源側熱交換器１３ｃが直列に直列冷媒流路で接続される。 When the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as the cooling operation mode, the first heat source side heat exchanger 13a and the first heat exchanger 13a are on the upstream side. The two heat source side heat exchangers 13b are in parallel with each other, and the third heat source side heat exchanger 13c is in series with the first heat source side heat exchanger 13a and the second heat source side heat exchanger 13b on the downstream side. It is connected by a series refrigerant flow path.
　第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃを暖房運転モードとして使用する際に、第１熱源側熱交換器１３ａと第２熱源側熱交換器１３ｂと第３熱源側熱交換器１３ｃとが互いに並列に並列冷媒流路で接続される。 When the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as the heating operation mode, the first heat source side heat exchanger 13a and the second heat source side heat The exchanger 13b and the third heat source side heat exchanger 13c are connected in parallel with each other by a parallel refrigerant flow path.
　第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃを除霜運転モードとして使用する際に、第１熱源側熱交換器１３ａと第２熱源側熱交換器１３ｂと第３熱源側熱交換器１３ｃとが互いに並列に並列冷媒流路で接続される。 When the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as the defrosting operation mode, the first heat source side heat exchanger 13a and the second heat source side The heat exchanger 13b and the third heat source side heat exchanger 13c are connected in parallel with each other by a parallel refrigerant flow path.
　空気調和装置１００は、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃを冷房運転モードとして使用する際に直列冷媒流路に切り替わり、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃを暖房運転モードとして使用する際に並列冷媒流路に切り替わり、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃを除霜雨天モードとして使用する際に並列冷媒流路に切り替わる、熱交換器流路切替装置を有している。熱交換器流路切替装置は、第１開閉装置３１、第２開閉装置３２、第１開度調整装置３３及び第２開度調整装置３４である。 The air conditioner 100 switches to the series refrigerant flow path when the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as the cooling operation mode, and the first When the heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as the heating operation mode, they are switched to the parallel refrigerant flow path, and the first heat source side heat exchanger 13a, the first It has a heat exchanger flow path switching device that switches to a parallel refrigerant flow path when the two heat source side heat exchangers 13b and the third heat source side heat exchanger 13c are used as the defrost rainy weather mode. The heat exchanger flow path switching device is a first switchgear 31, a second switchgear 32, a first opening / closing device 33, and a second opening / closing device 34.
　この構成によれば、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃを冷房運転モードとして使用する際に直列冷媒流路に切り替わり、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃを暖房運転モードとして使用する際に並列冷媒流路に切り替わる熱交換器流路切替装置を有している。 According to this configuration, when the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as the cooling operation mode, they are switched to the series refrigerant flow path and the first It has a heat exchanger flow path switching device that switches to a parallel refrigerant flow path when the heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as the heating operation mode. There is.
　これにより、冷房運転時と暖房運転時とで第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃの流路を直列又は並列に切り替えできる。そして、直列冷媒流路は、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃを冷房運転モードとして使用する際に、上流側にて第１熱源側熱交換器１３ａと第２熱源側熱交換器１３ｂとが互いに並列に、かつ、下流側にて第１熱源側熱交換器１３ａ及び第２熱源側熱交換器１３ｂに対して第３熱源側熱交換器１３ｃが直列に接続される。このため、第１直列冷媒流路は、冷媒の流速が遅くても、凝縮器の下流側には第３熱源側熱交換器１３ｃのみが配置され、蒸発器の下流側の容積が小さく、蒸発器の下流側で液冷媒が溜まる冷媒の寝込みが抑制でき、冷媒が良好に循環できる。 As a result, the flow paths of the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c can be switched in series or in parallel between the cooling operation and the heating operation. The series refrigerant flow path is first on the upstream side when the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as the cooling operation mode. The heat source side heat exchanger 13a and the second heat source side heat exchanger 13b are in parallel with each other, and the third heat source is relative to the first heat source side heat exchanger 13a and the second heat source side heat exchanger 13b on the downstream side. Side heat exchangers 13c are connected in series. Therefore, in the first series refrigerant flow path, even if the flow velocity of the refrigerant is slow, only the third heat source side heat exchanger 13c is arranged on the downstream side of the condenser, the volume on the downstream side of the evaporator is small, and evaporation occurs. The liquid refrigerant accumulates on the downstream side of the vessel.
　実施の形態１によれば、第１熱源側熱交換器１３ａには、１つの第１ヘッダー１４ａ及び１つの第１分配器１５ａが設けられている。第２熱源側熱交換器１３ｂには、１つの第２ヘッダー１４ｂ及び１つの第２分配器１５ｂが設けられている。第３熱源側熱交換器１３ｃには、単一の第３ヘッダー１４ｃ及び単一の第４ヘッダー１４ｄが設けられている。 According to the first embodiment, the first heat source side heat exchanger 13a is provided with one first header 14a and one first distributor 15a. The second heat source side heat exchanger 13b is provided with one second header 14b and one second distributor 15b. The third heat source side heat exchanger 13c is provided with a single third header 14c and a single fourth header 14d.
　この構成によれば、各第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃには、ヘッダーないし分配器が合計２つずつ設けられている。これにより、従来のように１台の熱源側熱交換器に２個以上のヘッダー及び分配器を設ける構成に比して、コストが抑制できると共に、設置スペースを狭くすることができる。 According to this configuration, each of the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c is provided with a total of two headers or distributors. As a result, the cost can be suppressed and the installation space can be narrowed as compared with the conventional configuration in which two or more headers and distributors are provided in one heat source side heat exchanger.
　実施の形態１によれば、第１開度調整装置３３及び第２開度調整装置３４は、開度変化により流量を調整できる絞り装置である。熱交換器流路切替装置は、暖房運転モードで冷媒流路を構成する場合に、第１開度調整装置３３及び第２開度調整装置３４のそれぞれの開度を変更し、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃのそれぞれに流入させる冷媒量を調整する。 According to the first embodiment, the first opening degree adjusting device 33 and the second opening degree adjusting device 34 are throttle devices capable of adjusting the flow rate by changing the opening degree. When the refrigerant flow path is configured in the heating operation mode, the heat exchanger flow path switching device changes the opening degree of each of the first opening degree adjusting device 33 and the second opening degree adjusting device 34 to the first heat source side. The amount of refrigerant flowing into each of the heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c is adjusted.
　この構成によれば、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃを暖房運転モードとして使用する際に、第１熱源側熱交換器１３ａと第２熱源側熱交換器１３ｂと第３熱源側熱交換器１３ｃとに冷媒量が最適に分配できる。 According to this configuration, when the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are used as the heating operation mode, the first heat source side heat exchanger 13a The amount of refrigerant can be optimally distributed to the second heat source side heat exchanger 13b and the third heat source side heat exchanger 13c.
　実施の形態１によれば、第１熱源側熱交換器１３ａの伝熱面積と第２熱源側熱交換器１３ｂの伝熱面積との和の伝熱面積は、第３熱源側熱交換器１３ｃの伝熱面積よりも大きくなるように形成されている。 According to the first embodiment, the total heat transfer area of the heat transfer area of the first heat source side heat exchanger 13a and the heat transfer area of the second heat source side heat exchanger 13b is the third heat source side heat exchanger 13c. It is formed so as to be larger than the heat transfer area of.
　この構成によれば、第１直列冷媒流路は、冷媒の流速が遅くても、蒸発器の下流側には第３熱源側熱交換器１３ｃのみが配置され、蒸発器の下流側の容積が小さく、蒸発器の下流側で液冷媒が溜まる冷媒の寝込みが抑制でき、冷媒が良好に循環できる。 According to this configuration, in the first series refrigerant flow path, even if the flow velocity of the refrigerant is slow, only the third heat source side heat exchanger 13c is arranged on the downstream side of the evaporator, and the volume on the downstream side of the evaporator is large. It is small, and the refrigerant that collects liquid refrigerant on the downstream side of the evaporator can be suppressed from falling asleep, and the refrigerant can be circulated well.
　実施の形態１によれば、第１熱源側熱交換器１３ａは、独立して配置されている。第２熱源側熱交換器１３ｂの一部分は、第３熱源側熱交換器１３ｃと熱交換器構成要素であるフィンを共有して一体に構成される。第２熱源側熱交換器１３ｂの一部分以外の残りの部分は、第３熱源側熱交換器１３ｃとは独立して構成されている。 According to the first embodiment, the first heat source side heat exchanger 13a is arranged independently. A part of the second heat source side heat exchanger 13b is integrally formed with the third heat source side heat exchanger 13c by sharing fins which are heat exchanger components. The remaining part other than a part of the second heat source side heat exchanger 13b is configured independently of the third heat source side heat exchanger 13c.
　この構成によれば、独立した第１熱源側熱交換器１３ａもフィンを共有する場合に対し、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃに使用するヘッダー総数及び分配器総数を少なくすることにより、冷媒配管３である接続配管の簡略化が図れ、空気調和装置１００の小型化が図れる。 According to this configuration, the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger are used as opposed to the case where the independent first heat source side heat exchanger 13a also shares the fins. By reducing the total number of headers and the total number of distributors used in 13c, the connection pipe which is the refrigerant pipe 3 can be simplified, and the air conditioner 100 can be miniaturized.
　実施の形態１によれば、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃは、熱交換器構成要素である伝熱管が扁平管である。 According to the first embodiment, in the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c, the heat transfer tube which is a component of the heat exchanger is a flat tube. ..
　この構成によれば、伝熱管の断面を扁平形状とすることにより、通風抵抗を増大させることなく室外空気と伝熱管との接触面積を増大させることができる。これにより、第１熱源側熱交換器１３ａ、第２熱源側熱交換器１３ｂ及び第３熱源側熱交換器１３ｃを小型化した場合でも十分な熱交換性能が得られる。 According to this configuration, by making the cross section of the heat transfer tube flat, it is possible to increase the contact area between the outdoor air and the heat transfer tube without increasing the ventilation resistance. As a result, sufficient heat exchange performance can be obtained even when the first heat source side heat exchanger 13a, the second heat source side heat exchanger 13b, and the third heat source side heat exchanger 13c are miniaturized.
１－４．変形例
　なお、実施の形態１の圧縮機１０は、低圧シェル型の圧縮機を使用する場合を例に説明した。しかし、たとえば、高圧シェル型の圧縮機を使用しても同様の効果を奏する。 1-4. Modification Example The compressor 10 of the first embodiment has been described by taking the case of using a low-pressure shell type compressor as an example. However, for example, the same effect can be obtained by using a high-pressure shell type compressor.
　また、圧縮機１０の中間圧部に冷媒を流入させる構造を有さない圧縮機を使用した場合を例に説明した。しかし、圧縮機の中間圧部に冷媒を流入させるインジェクションポートを備えた構造の圧縮機にも適用することができる。 Further, the case where a compressor having no structure for flowing the refrigerant into the intermediate pressure portion of the compressor 10 is used has been described as an example. However, it can also be applied to a compressor having a structure provided with an injection port for allowing a refrigerant to flow into the intermediate pressure portion of the compressor.
　また、一般的に、熱源側熱交換器及び負荷側熱交換器には、送風によって冷媒の凝縮又は蒸発を促進させるファンなどの送風機が取り付けられていることが多いが、これに限るものではない。たとえば、負荷側熱交換器の熱交換性能の向上手段として、放射を利用したパネルヒータのようなものも用いることができる。また、熱源側熱交換器としては、水、不凍液などの液体により熱交換する水冷式のタイプの熱交換器を用いることができる。熱交換器には、冷媒の放熱又は吸熱が行えるものであれば、どのようなものでも用いることができる。水冷式のタイプの熱交換器を用いる場合は、たとえば、プレート式熱交換器、二重管式熱交換器などの水冷媒間熱交換器を設置して用いればよい。 Further, in general, the heat source side heat exchanger and the load side heat exchanger are often equipped with a blower such as a fan that promotes the condensation or evaporation of the refrigerant by blowing air, but the present invention is not limited to this. .. For example, as a means for improving the heat exchange performance of the load side heat exchanger, a panel heater using radiation can also be used. Further, as the heat source side heat exchanger, a water-cooled type heat exchanger that exchanges heat with a liquid such as water or antifreeze can be used. Any heat exchanger can be used as long as it can dissipate heat or absorb heat from the refrigerant. When a water-cooled type heat exchanger is used, for example, a water-refrigerant heat exchanger such as a plate heat exchanger or a double-tube heat exchanger may be installed and used.
　実施の形態は、例として提示したものであり、実施の形態の範囲を限定することは意図していない。実施の形態は、その他の様々な形態で実施されることが可能であり、実施の形態の要旨を逸脱しない範囲で、種々の省略、置き換え、変更を行なうことができる。これら実施の形態及びその変形は、実施の形態の範囲及び要旨に含まれる。 The embodiment is presented as an example and is not intended to limit the scope of the embodiment. The embodiment can be implemented in various other forms, and various omissions, replacements, and changes can be made without departing from the gist of the embodiment. These embodiments and variations thereof are included in the scope and gist of the embodiments.
　１　室外機、２　室内機、３　冷媒配管、４ａ　第１主管、４ｂ　第２主管、５ａ　第１本管、５ｂ　第２本管、６　直列並列切り替え配管、７　直列出口配管、８　並列出入口配管、９ａ　第１出入口配管、９ｂ　第２出入口配管、９ｃ　第３出入口配管、１０　圧縮機、１１　第１四方弁、１２　第２四方弁、１３ａ　第１熱源側熱交換器、１３ｂ　第２熱源側熱交換器、１３ｃ　第３熱源側熱交換器、１４ａ　第１ヘッダー、１４ｂ　第２ヘッダー、１４ｃ　第３ヘッダー、１４ｄ　第４ヘッダー、１５ａ　第１分配器、１５ｂ　第２分配器、１６　ファン、２１　負荷側熱交換器、２２　負荷側絞り装置、３１　第１開閉装置、３２　第２開閉装置、３３　第１開度調整装置、３４　第２開度調整装置、６０　制御装置、１００　空気調和装置。 1 outdoor unit, 2 indoor unit, 3 refrigerant pipe, 4a 1st main pipe, 4b 2nd main pipe, 5a 1st main pipe, 5b 2nd main pipe, 6 series parallel switching pipe, 7 series outlet pipe, 8 parallel inlet / outlet pipe, 9a 1st inlet / outlet pipe, 9b 2nd inlet / outlet pipe, 9c 3rd inlet / outlet pipe, 10 compressor, 11 1st 4-way valve, 12 2nd 4-way valve, 13a 1st heat source side heat exchanger, 13b 2nd heat source side heat exchange Vessel, 13c 3rd heat source side heat exchanger, 14a 1st header, 14b 2nd header, 14c 3rd header, 14d 4th header, 15a 1st distributor, 15b 2nd distributor, 16 fan, 21 load side heat Exchanger, 22 load side throttle device, 31 first opening / closing device, 32 second opening / closing device, 33 first opening adjustment device, 34 second opening adjustment device, 60 control device, 100 air conditioner.

Claims (10)

  1. 　圧縮機、冷媒流路切替装置、負荷側熱交換器、負荷側絞り装置、第１熱源側熱交換器、第２熱源側熱交換器及び第３熱源側熱交換器が配管で接続されて冷媒が循環する主回路と、
    　前記第１熱源側熱交換器、前記第２熱源側熱交換器及び前記第３熱源側熱交換器の冷媒流路を切り替えるための熱交換器流路切替装置と、
    　前記熱交換器流路切替装置を制御する制御装置と
    を具備し、
    　前記制御装置は、前記第１熱源側熱交換器、前記第２熱源側熱交換器及び前記第３熱源側熱交換器を除霜運転モードとして使用する際に、前記第１熱源側熱交換器、前記第２熱源側熱交換器及び前記第３熱源側熱交換器の冷媒流路を並列冷媒流路に切り替えるように前記熱交換器流路切替装置を制御し、
    　前記並列冷媒流路は、前記第１熱源側熱交換器、前記第２熱源側熱交換器及び前記第３熱源側熱交換器が互いに並列に接続される冷媒流路である、
    空気調和装置。     A compressor, a refrigerant flow path switching device, a load side heat exchanger, a load side throttle device, a first heat source side heat exchanger, a second heat source side heat exchanger, and a third heat source side heat exchanger are connected by a pipe to provide a refrigerant. The main circuit that circulates and
    A heat exchanger flow path switching device for switching the refrigerant flow paths of the first heat source side heat exchanger, the second heat source side heat exchanger, and the third heat source side heat exchanger.
    A control device for controlling the heat exchanger flow path switching device is provided.
    When the control device uses the first heat source side heat exchanger, the second heat source side heat exchanger, and the third heat source side heat exchanger as the defrosting operation mode, the first heat source side heat exchanger The heat exchanger flow path switching device is controlled so as to switch the refrigerant flow paths of the second heat source side heat exchanger and the third heat source side heat exchanger to parallel refrigerant flow paths.
    The parallel refrigerant flow path is a refrigerant flow path in which the first heat source side heat exchanger, the second heat source side heat exchanger, and the third heat source side heat exchanger are connected in parallel with each other.
    Air conditioner.
  2. 　前記制御装置は、
    　前記第１熱源側熱交換器、前記第２熱源側熱交換器及び前記第３熱源側熱交換器を冷房運転モードとして使用する際に、前記熱交換器流路切替装置を前記第１熱源側熱交換器、前記第２熱源側熱交換器及び前記第３熱源側熱交換器の冷媒流路を直列冷媒流路に切り替えるように制御し、
    　前記直列冷媒流路は、上流側にて前記第１熱源側熱交換器と前記第２熱源側熱交換器とが互いに並列に、かつ、下流側にて前記第１熱源側熱交換器及び前記第２熱源側熱交換器に対して前記第３熱源側熱交換器が直列に接続された冷媒流路である、
    請求項１に記載の空気調和装置。     The control device is
    When the first heat source side heat exchanger, the second heat source side heat exchanger, and the third heat source side heat exchanger are used as the cooling operation mode, the heat exchanger flow path switching device is used on the first heat source side. Control the refrigerant flow paths of the heat exchanger, the second heat source side heat exchanger, and the third heat source side heat exchanger to switch to the series refrigerant flow path.
    In the series refrigerant flow path, the first heat source side heat exchanger and the second heat source side heat exchanger are arranged in parallel with each other on the upstream side, and the first heat source side heat exchanger and the above on the downstream side. A refrigerant flow path in which the third heat source side heat exchanger is connected in series to the second heat source side heat exchanger.
    The air conditioner according to claim 1.
  3. 　前記制御装置は、
    　前記第１熱源側熱交換器、前記第２熱源側熱交換器及び前記第３熱源側熱交換器を暖房運転モードとして使用する際に、前記熱交換器流路切替装置を前記第１熱源側熱交換器、前記第２熱源側熱交換器及び前記第３熱源側熱交換器の冷媒流路を前記並列冷媒流路に切り替えるように制御する、
    請求項１又は請求項２に記載の空気調和装置。     The control device is
    When the first heat source side heat exchanger, the second heat source side heat exchanger, and the third heat source side heat exchanger are used as the heating operation mode, the heat exchanger flow path switching device is used on the first heat source side. Control so that the refrigerant flow paths of the heat exchanger, the second heat source side heat exchanger, and the third heat source side heat exchanger are switched to the parallel refrigerant flow paths.
    The air conditioner according to claim 1 or 2.
  4. 　前記第１熱源側熱交換器、前記第２熱源側熱交換器及び前記第３熱源側熱交換器のうちの１つは、１つのヘッダ及び１つの分配器が設けられた熱源側熱交換器である、
    請求項１～請求項３のいずれか１項に記載の空気調和装置。     One of the first heat source side heat exchanger, the second heat source side heat exchanger, and the third heat source side heat exchanger is a heat source side heat exchanger provided with one header and one distributor. Is,
    The air conditioner according to any one of claims 1 to 3.
  5. 　前記第１熱源側熱交換器、前記第２熱源側熱交換器及び前記第３熱源側熱交換器のうちの１つは、冷媒の流入側及び流出側にそれぞれ１つのヘッダが設けられた熱源側熱交換器である、
    請求項１～請求項４のいずれか１項に記載の空気調和装置。     One of the first heat source side heat exchanger, the second heat source side heat exchanger, and the third heat source side heat exchanger is a heat source provided with one header on each of the inflow side and the outflow side of the refrigerant. Side heat exchanger,
    The air conditioner according to any one of claims 1 to 4.
  6. 　前記冷媒流路切替装置は、
    　前記圧縮機から吐出された冷媒を前記第１熱源側熱交換器に供給又は遮断を行う第１四方弁と、
    　前記圧縮機から吐出された冷媒を前記第２熱源側熱交換器又は前記負荷側熱交換器のどちらかに供給する第２四方弁とを有し、
    　前記熱交換器流路切替装置は、
    　前記冷媒流路の切り替えに使用される第１開閉装置と、
    　前記冷媒流路の切り替えに使用される第２開閉装置と、
    　前記冷媒流路の切り替えに使用される第１開度調整装置と、
    　前記冷媒流路の切り替えに使用される第２開度調整装置とを有し、
    　前記直列冷媒流路においては、前記第１四方弁で前記圧縮機から吐出された冷媒が前記第１熱源側熱交換器に供給され、前記第２四方弁で前記圧縮機から吐出された冷媒が前記第２熱源側熱交換器に供給され、前記第１開閉装置が閉とれ、前記第２開閉装置が開とされ、前記第１開度調整装置が閉とされ、前記第２開度調整装置が開とされ、
    　前記並列冷媒流路においては、前記第１四方弁で前記圧縮機から吐出された冷媒が遮断され、前記第２四方弁で前記圧縮機から吐出された冷媒が負荷側熱交換器に供給され、前記第１開閉装置が開とされ、前記第２開閉装置が閉とされ、前記第１開度調整が開とされ、前記第２開度調整装置が開とされる、
    請求項３に記載の空気調和装置。     The refrigerant flow path switching device is
    A first four-way valve that supplies or shuts off the refrigerant discharged from the compressor to the first heat source side heat exchanger.
    It has a second four-way valve that supplies the refrigerant discharged from the compressor to either the second heat source side heat exchanger or the load side heat exchanger.
    The heat exchanger flow path switching device is
    The first switchgear used to switch the refrigerant flow path and
    A second switchgear used to switch the refrigerant flow path and
    The first opening degree adjusting device used for switching the refrigerant flow path and
    It has a second opening degree adjusting device used for switching the refrigerant flow path, and has.
    In the series refrigerant flow path, the refrigerant discharged from the compressor by the first four-way valve is supplied to the first heat source side heat exchanger, and the refrigerant discharged from the compressor by the second four-way valve is supplied. It is supplied to the second heat source side heat exchanger, the first opening / closing device is closed, the second opening / closing device is opened, the first opening / closing device is closed, and the second opening / closing device is closed. Is opened,
    In the parallel refrigerant flow path, the refrigerant discharged from the compressor is shut off by the first four-way valve, and the refrigerant discharged from the compressor is supplied to the load side heat exchanger by the second four-way valve. The first opening / closing device is opened, the second opening / closing device is closed, the first opening / closing adjustment is opened, and the second opening / closing adjustment device is opened.
    The air conditioner according to claim 3.
  7. 　前記第１開度調整装置及び前記第２開度調整装置は、開度変化により流量を調整できる絞り装置であり、
    　前記熱交換器流路切替装置は、
    　前記並列冷媒流路に切り替える場合に、前記第１開度調整装置及び前記第２開度調整装置のそれぞれの開度を変更し、前記第１熱源側熱交換器、前記第２熱源側熱交換器及び前記第３熱源側熱交換器のそれぞれに流入させる冷媒量を調整する、
    請求項６に記載の空気調和装置。     The first opening degree adjusting device and the second opening degree adjusting device are throttle devices capable of adjusting the flow rate by changing the opening degree.
    The heat exchanger flow path switching device is
    When switching to the parallel refrigerant flow path, the opening degrees of the first opening degree adjusting device and the second opening degree adjusting device are changed, and the first heat source side heat exchanger and the second heat source side heat exchange are performed. Adjust the amount of refrigerant flowing into each of the device and the third heat source side heat exchanger.
    The air conditioner according to claim 6.
  8. 　前記第１熱源側熱交換器の伝熱面積と前記第２熱源側熱交換器の伝熱面積との和の伝熱面積は、前記第３熱源側熱交換器の伝熱面積よりも大きくなるように形成される、
    請求項１～請求項７のいずれか１項に記載の空気調和装置。     The sum of the heat transfer areas of the first heat source side heat exchanger and the heat transfer area of the second heat source side heat exchanger is larger than the heat transfer area of the third heat source side heat exchanger. Formed as
    The air conditioner according to any one of claims 1 to 7.
  9. 　前記第１熱源側熱交換器は、前記第２熱源側熱交換器及び前記第３熱源側熱交換器に対して独立して配置され、
    　前記第２熱源側熱交換器の一部分は、前記第３熱源側熱交換器と熱交換器構成要素であるフィンを共有して一体に構成され、
    　前記第２熱源側熱交換器の前記一部分以外の残りの部分は、前記第３熱源側熱交換器とは独立して構成される、
    請求項１～請求項８のいずれか１項に記載の空気調和装置。     The first heat source side heat exchanger is arranged independently of the second heat source side heat exchanger and the third heat source side heat exchanger.
    A part of the second heat source side heat exchanger is integrally formed by sharing the fins which are the heat exchanger components with the third heat source side heat exchanger.
    The rest of the second heat source side heat exchanger other than the first part is configured independently of the third heat source side heat exchanger.
    The air conditioner according to any one of claims 1 to 8.
  10. 　前記第１熱源側熱交換器、前記第２熱源側熱交換器及び前記第３熱源側熱交換器のうちの１つは、熱交換器構成要素である伝熱管が扁平管である熱源側熱交換器である、
    請求項１～請求項９のいずれか１項に記載の空気調和装置。     One of the first heat source side heat exchanger, the second heat source side heat exchanger, and the third heat source side heat exchanger is heat source side heat in which the heat transfer tube which is a component of the heat exchanger is a flat tube. It is an exchanger,
    The air conditioner according to any one of claims 1 to 9.
PCT/JP2019/028595 2019-07-22 2019-07-22 Air-conditioning device WO2021014520A1 (en)

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JPH0420764A (en) * 1990-05-16 1992-01-24 Hitachi Ltd Air conditioner
WO2018047416A1 (en) * 2016-09-12 2018-03-15 三菱電機株式会社 Air conditioner
WO2018047331A1 (en) * 2016-09-12 2018-03-15 三菱電機株式会社 Air conditioning device

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US5237833A (en) * 1991-01-10 1993-08-24 Mitsubishi Denki Kabushiki Kaisha Air-conditioning system
CN101280979A (en) * 2008-05-26 2008-10-08 刘雄 Air conditioner heat pump device

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Publication number Priority date Publication date Assignee Title
JPH0420764A (en) * 1990-05-16 1992-01-24 Hitachi Ltd Air conditioner
WO2018047416A1 (en) * 2016-09-12 2018-03-15 三菱電機株式会社 Air conditioner
WO2018047331A1 (en) * 2016-09-12 2018-03-15 三菱電機株式会社 Air conditioning device

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