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WO2016129027A1 - Dispositif de conditionnement d'air - Google Patents

Dispositif de conditionnement d'air Download PDF

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Publication number
WO2016129027A1
WO2016129027A1 PCT/JP2015/053462 JP2015053462W WO2016129027A1 WO 2016129027 A1 WO2016129027 A1 WO 2016129027A1 JP 2015053462 W JP2015053462 W JP 2015053462W WO 2016129027 A1 WO2016129027 A1 WO 2016129027A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
heat source
unit
heat exchange
shut
Prior art date
Application number
PCT/JP2015/053462
Other languages
English (en)
Japanese (ja)
Inventor
松井　良輔
森本　修
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 JP2016574533A priority Critical patent/JP6257812B2/ja
Priority to GB1711506.4A priority patent/GB2549897B/en
Priority to PCT/JP2015/053462 priority patent/WO2016129027A1/fr
Publication of WO2016129027A1 publication Critical patent/WO2016129027A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • 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
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/005—Arrangement or mounting of control or safety devices of safety devices
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0231—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with simultaneous cooling and heating
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/0272—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using bridge circuits of one-way valves
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2519—On-off valves

Definitions

  • the present invention relates to an air conditioner including a plurality of heat source units and having a shut-off device that shuts off a refrigerant flow when the refrigerant leaks.
  • a conventional air conditioner has a structure in which when a refrigerant leak occurs, the shut-off valve is closed and the operation is stopped, so that the refrigerant leak is minimized (see, for example, Patent Document 1).
  • a detection unit that detects refrigerant leakage, a concentration calculation unit that calculates the concentration of refrigerant leakage detected by the detection unit, and a refrigerant that circulates in the refrigeration cycle are shut off based on the output of the concentration detection unit.
  • An air conditioner having a shut-off device is disclosed.
  • Patent Document 1 The air conditioner of Patent Document 1 is controlled to completely shut off the flow of the refrigerant and stop the operation when the refrigerant leaks. For this reason, the comfort of an air-conditioned space will be impaired by the leakage of a refrigerant
  • the present invention has been made to solve the above-described problems, and provides an air conditioner that can minimize deterioration in comfort of an air-conditioned space even when refrigerant leakage is blocked.
  • the purpose is to do.
  • the air conditioner of the present invention includes a compressor and a heat source side heat exchanger, and includes a plurality of heat source units connected in parallel to each other, and an indoor unit having a load side expansion device and a load side heat exchanger as refrigerant piping.
  • a refrigerant circuit connected via a plurality of heat source units and an indoor unit, each of which is installed between a plurality of heat source units and an indoor unit.
  • a plurality of leakage detectors for detecting each of them, and a control device for controlling the operation of the plurality of heat source units, indoor units, and shut-off device, and the controller detects the refrigerant leakage when the leakage detector detects the refrigerant leakage
  • a shut-off controller that activates a shut-off device connected to a heat source machine that is leaking, and in a plurality of shut-off devices, when there are a shut-off device that is in an active state and a shut-off device that is in an inactive state, Connected to the shut-off device at A capacity setting unit that sets the limited heat exchange capacity in the indoor unit when operated by the source unit, and an operation control that controls the operation of the heat source unit or the indoor unit with the limited heat exchange capacity set in the capacity setting unit as the upper limit A part.
  • the shut-off device when refrigerant leakage is detected, the shut-off device is operated, and the operation of the heat source unit is controlled with the limited heat exchange capability for blocking the refrigerant leak as the upper limit, Since the operation can be continued while minimizing the leakage of the refrigerant, the deterioration of the comfort of the air-conditioned space can be minimized even when the leakage of the refrigerant is interrupted.
  • FIG. 2 It is a block diagram which shows an example of the control apparatus in the air conditioning apparatus of FIG. 2 is a flowchart illustrating an example of setting a reference value in a first refrigerant amount determination mode in the air conditioner of FIG. 1. It is a refrigerant circuit figure which shows Embodiment 2 of the indoor unit of the air conditioning apparatus of this invention.
  • FIG. 1 is a refrigerant circuit diagram showing Embodiment 1 of the air-conditioning apparatus of the present invention.
  • the air conditioner 100 includes a plurality of heat source devices 1A and 1B, a relay device 20 connected to the plurality of heat source devices 1A and 1B via refrigerant pipes 4a and 4b, and a relay device 20 connected via the refrigerant pipe 5. And a plurality of indoor units 30a to 30d.
  • the plurality of heat source units 1A and 1B, the relay device 20, and the plurality of indoor units 30a to 30d constitute a refrigerant circuit 100A connected by refrigerant pipes 4a, 4b, and 5, and the plurality of heat source units 1A and 1B.
  • the cold heat or warm heat generated in the above is delivered to the plurality of indoor units 30a to 30d via the relay device 20.
  • the refrigerant used in the air conditioner 100 include HFC refrigerants such as R410A, R407C, and R404A, HCFC refrigerants such as R22 and R134a, or natural refrigerants such as hydrocarbon and helium.
  • the plurality of heat source units 1A and 1B are arranged in a space outside a building such as a building or a house, for example, and supply cold or hot heat to the indoor units 30a to 30d via the relay device 20.
  • the heat source units 1A and 1B are connected in parallel to each other, and each include a compressor 10, a first flow path switching device 11, a heat source side heat exchanger 12, and an accumulator 13.
  • FIG. 1 although the several heat source machine 1A, 1B has illustrated about the case where it has the same structure, you may have a different structure.
  • the compressor 10 sucks and compresses refrigerant and discharges it in a high temperature and high pressure state.
  • the compressor 10 has a discharge side connected to the first flow path switching device 11 and a suction side connected to the accumulator 13.
  • the compressor 10 may be composed of, for example, an inverter compressor capable of capacity control.
  • the first flow path switching device 11 includes, for example, a four-way valve and the like, and switches the refrigerant flow path according to the operation mode.
  • the first flow path switching device 11 connects the discharge side of the compressor 10 and the check valve 14b in the heating operation mode and the heating main operation mode, and also at the suction side of the heat source side heat exchanger 12 and the accumulator 13. And connect.
  • the first flow path switching device 11 connects the discharge side of the compressor 10 and the heat source side heat exchanger 12 in the cooling operation mode and the cooling main operation mode, and the suction side of the check valve 14d and the accumulator 13 And connect.
  • the heat source side heat exchanger 12 is composed of, for example, a plate fin and tube heat exchanger that exchanges heat between the refrigerant flowing through the heat transfer tubes and the air passing through the fins.
  • One of the heat source side heat exchangers 12 is connected to the first flow path switching device 11, and the other is connected to the refrigerant pipes 4a and 4b via check valves 14b and 14c.
  • the heat source side heat exchanger 12 functions as an evaporator during heating operation, functions as a radiator (gas cooler) during cooling operation, and exchanges heat between air and refrigerant supplied from a blower such as a fan (not shown). I do.
  • the accumulator 13 is connected to the suction side of the compressor 10, and surplus refrigerant due to a difference between the heating operation mode and the cooling operation mode, a change in transient operation (for example, the number of operating units of the indoor units 30a to 30d).
  • the surplus refrigerant with respect to (change) is stored.
  • Each of the heat source units 1A and 1B has four check valves 14a to 14d that make the flow of refrigerant flowing from the heat source units 1A and 1B to the relay device 20 in a certain direction in both the cooling operation mode and the heating operation mode. have.
  • the refrigerant flows out from the first flow path switching device 11 through the check valve 14a to the refrigerant pipe 4a, and from the refrigerant pipe 4b through the check valve 14b to the heat source side heat exchanger 12. Flows in.
  • the refrigerant flows out from the heat source side heat exchanger 12 through the check valve 14c to the refrigerant pipe 4a, and flows from the refrigerant pipe 4b through the check valve 14d.
  • the refrigerant pipe 4a functions as a high-pressure pipe
  • the refrigerant pipe 4b functions as a low-pressure pipe.
  • the relay device 20 is configured as a separate housing from the plurality of heat source devices 1A and 1B and the plurality of indoor units 30a to 30d, and can be installed at a position different from the outdoor space and the indoor space.
  • the relay device 20 is connected to the plurality of heat source devices 1A and 1B via the refrigerant pipes 4a and 4b, and is connected to the indoor units 30a to 30d via the refrigerant pipe 5. Then, the relay device 20 transmits the cold or warm heat supplied from the heat source devices 1A and 1B to the indoor units 30a to 30d.
  • the relay device 20 includes a gas-liquid separator 21, a first throttling device 22, a second throttling device 23, and second flow path switching devices 24a to 24d.
  • the gas-liquid separator 21 is installed at the entrance of the relay device 20, and is connected to the plurality of heat source units 1A and 1B via the refrigerant pipe 4a.
  • the gas-liquid separator 21 separates the high-pressure gas-liquid two-phase refrigerant flowing out from the plurality of heat source units 1A, 1B into liquid refrigerant and gas refrigerant.
  • a gas pipe is connected to the upper part of the gas-liquid separator 21 and a liquid pipe is connected to the lower part.
  • the liquid refrigerant separated in the gas-liquid separator 21 flows from the lower liquid pipe to the indoor units 30a to 30d to supply cold heat, and the gas refrigerant flows from the upper gas pipe to the indoor units 30a to 30d to supply hot heat. .
  • the first throttling device 22 functions as a pressure reducing valve and an opening / closing valve, and decompresses the liquid refrigerant to adjust it to a predetermined pressure, and opens and closes the flow path of the liquid refrigerant.
  • the first expansion device 22 is provided in a lower pipe through which liquid refrigerant flows from the gas-liquid separator 21.
  • the first throttling device 22 may be constituted by a device whose opening degree can be variably controlled, for example, an electronic expansion valve.
  • the second expansion device 23 functions as a pressure reducing valve and an on-off valve, and is installed between the low-pressure piping on the outlet side of the relay device 20 that leads to the refrigerant piping 4 b side and the piping that conducts to the outlet side of the first expansion device 22. ing.
  • the second expansion device 23 opens and closes the refrigerant flow path when bypassing the refrigerant in the heating only operation mode.
  • the 2nd expansion device 23 adjusts a bypass flow volume according to load side load in heating main operation mode.
  • the second expansion device 23 may also be configured with a device whose opening degree can be variably controlled, such as an electronic expansion valve.
  • the second flow path switching devices 24a to 24d switch the flow path according to the operation mode of the plurality of indoor units 30a to 30d, and the number of the second flow path switching devices 24a to 24d corresponds to the number of installed indoor units 30a to 30d (here, 4 One) is installed.
  • the second flow path switching devices 24a to 24d are connected in parallel to the liquid pipe and the gas pipe of the gas-liquid separator 21, respectively, the two opening / closing devices 25a and 25b connected to one refrigerant pipe 5, and the other Two check valves 26 a and 26 b connected to the refrigerant pipe 5.
  • the second flow path switching devices 24a to 24d have two opening / closing devices 25a and 25b and two check valves 26a and 26b is exemplified. Good.
  • the opening / closing devices 25a and 25b are made of, for example, electromagnetic valves and are connected in parallel to each other.
  • One side of the switchgears 25 a and 25 b is connected to the refrigerant pipe 5.
  • the other side of the switchgear 25a is connected to the gas pipe of the gas-liquid separator 21, and the other side of the switchgear 25b is connected to the refrigerant pipe 4b.
  • One of the check valves 26 a and 26 b is connected to the refrigerant pipe 5, and the other is connected to the first expansion device 22 and the second expansion device 23.
  • the refrigerant flows into the indoor units 30a to 30d from the check valve 26a side.
  • the indoor units 30a to 30d perform the heating operation, the refrigerant flows from the indoor units 30a to 30d to the check valve 26b and flows to the second expansion device 23.
  • the indoor units 30a to 30d are arranged at positions where cooling air or heating air can be supplied to an indoor space that is a space inside the building (for example, a living room), and cooling air or Heating air is supplied.
  • FIG. 1 shows an example in which four indoor units 30a to 30d are connected, the number of connected indoor units 30a to 30d is not limited to four, but one or more connected. It only has to be.
  • Each of the indoor units 30a to 30d has a load side heat exchanger 31 and a load side expansion device 32, respectively.
  • the load-side heat exchanger 31 is connected to the second flow path switching devices 24a to 24d of the relay device 20 via the refrigerant pipe 5.
  • the load-side heat exchanger 31 exchanges heat between air supplied from a blower such as a fan (not shown) and a refrigerant, and generates heating air or cooling air to be supplied to the indoor space. is there.
  • the load-side throttle device 32 includes a device whose opening degree can be variably controlled, for example, an electronic expansion valve, etc., and decompresses and expands the refrigerant in the cooling operation mode and supplies the refrigerant to the load-side heat exchanger 31. .
  • the opening degree of the load side throttle device 32 is controlled so that the superheat (superheat degree) obtained as a difference between the temperature detected by the first temperature sensor 43 and the second temperature sensor 44 is constant in the cooling operation mode. Is done.
  • the air conditioner 100 can perform a cooling operation or a heating operation with the indoor units 30a to 30d based on instructions from the indoor units 30a to 30d. That is, the air conditioner 100 can perform the same operation for all the indoor units 30a to 30d, and can perform different operations for each of the indoor units 30a to 30d.
  • the operation mode executed by the air conditioner 100 includes a cooling only operation mode in which all the driven indoor units 30a to 30d execute a cooling operation, and all the driven indoor units 30a to 30d execute a heating operation.
  • each operation mode is demonstrated with the flow of a heat source side refrigerant
  • the cooling only operation mode the heating only operation mode, the cooling main operation mode, and the heating main operation mode
  • the case where the indoor units 30a and 30b operate is illustrated, and a cooling load is applied to the indoor units 30c and 30d.
  • the load side expansion device 32 there is no need to flow the refrigerant, and the load side expansion device 32 corresponding to each state is closed. Then, when a cooling load is generated from the indoor units 30c and 30d, the load side expansion device 32 may be opened to circulate the refrigerant.
  • FIG. 2 is a refrigerant circuit diagram illustrating a refrigerant flow when the air-conditioning apparatus of FIG. 1 is in the cooling only operation mode.
  • the first flow path switching device 11 is switched so that the heat source side refrigerant discharged from the compressor 10 flows into the heat source side heat exchanger 12.
  • a low temperature / low pressure refrigerant is compressed by the compressor 10 and discharged as a high temperature / high pressure gas refrigerant.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 flows into the heat source side heat exchanger 12 via the first flow path switching device 11.
  • the high-pressure liquid refrigerant that has flowed out of the heat source side heat exchanger 12 flows out of the heat source devices 1A and 1B through the check valve 14c, and flows into the relay device 20 through the refrigerant pipe 4a.
  • the high-pressure liquid refrigerant that has flowed into the relay device 20 passes through the gas-liquid separator 21, the first throttle device 22, the check valves 26a of the second flow path switching devices 24a and 24b, and the refrigerant pipe 5, and then the indoor unit 30a, Flows into 30b.
  • the high-pressure liquid refrigerant is expanded by the load-side throttle device 32 and becomes a low-temperature and low-pressure gas-liquid two-phase refrigerant.
  • the gas-liquid two-phase refrigerant flows into the load-side heat exchanger 31 of the indoor units 30a and 30b acting as evaporators and absorbs heat from the room air, thereby cooling the room air and cooling the room air. become.
  • the gas refrigerant that has flowed out of the indoor units 30a and 30b flows out of the relay device 20 via the refrigerant pipe 5 and the opening / closing device 25b of the second flow path switching devices 24a and 24b.
  • FIG. 3 is a refrigerant circuit diagram illustrating a refrigerant flow when the air-conditioning apparatus of FIG. 1 is in the heating only operation mode.
  • the first flow path switching device 11 causes the heat source side refrigerant discharged from the compressor 10 to pass through the heat source side heat exchanger 12. Without switching to the relay device 20.
  • 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 first flow path switching device 11 and the check valve 14a and flows out from the heat source devices 1A and 1B.
  • the high-temperature and high-pressure gas refrigerant flowing out from the heat source devices 1A and 1B flows into the relay device 20 through the refrigerant pipe 4a on the high-pressure refrigerant side.
  • the high-temperature and high-pressure gas refrigerant flowing into the relay device 20 flows into the indoor units 30a and 30b after passing through the gas-liquid separator 21, the opening / closing device 25a of the second flow path switching devices 24a and 24b, and the refrigerant pipe 5. To do.
  • the high-temperature and high-pressure gas refrigerant flows into the load-side heat exchanger 31 that acts as a condenser and dissipates heat to the indoor air, thereby turning into liquid refrigerant while heating the indoor space.
  • the liquid refrigerant that has flowed out of the indoor units 30a and 30b is expanded by the load side throttle device 32, and again passes through the refrigerant pipe 5, the check valve 26b, the second throttle device 23, and the refrigerant pipe 4b, and the heat source machines 1A and 1B again. Flow into.
  • the refrigerant flowing into each of the heat source units 1A and 1B passes through the check valve 14b and becomes a low-temperature / low-pressure gas refrigerant while absorbing heat from the outdoor air by the heat source side heat exchanger 12. Thereafter, the low-temperature and low-pressure gas refrigerant is again sucked into the compressor 10 via the first flow path switching device 11 and the accumulator 13.
  • FIG. 4 is a refrigerant circuit diagram illustrating a refrigerant flow when the air-conditioning apparatus of FIG. 1 is in the cooling main operation mode.
  • the cooling load is generated in the indoor unit 30a and the heating load is generated in the indoor unit 30b is illustrated.
  • the first flow path switching device 11 is switched so that the refrigerant discharged from the compressor 10 flows into the heat source side heat exchanger 12.
  • 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 flows into the heat source side heat exchanger 12 via the first flow path switching device 11.
  • the high-temperature and high-pressure gas refrigerant becomes a gas-liquid two-phase refrigerant while radiating heat to the outdoor air by the heat source side heat exchanger 12.
  • the refrigerant that has flowed out of the heat source side heat exchanger 12 flows into the relay device 20 through the check valve 14c and the refrigerant pipe 4a.
  • the two-phase refrigerant that has flowed into the relay device 20 is separated into a high-pressure gas refrigerant and a high-pressure liquid refrigerant by the gas-liquid separator 21.
  • the high-pressure gas refrigerant flows into the indoor unit 30b after passing through the opening / closing device 25a and the refrigerant pipe 5 of the second flow path switching device 24b. And it flows into the load side heat exchanger 31 of the indoor unit 30b which acts as a condenser, and becomes a liquid refrigerant while heating the indoor space by dissipating heat to the indoor air.
  • the liquid refrigerant that has flowed out of the load side heat exchanger 31 of the indoor unit 30b is expanded by the load side expansion device 32 and passes through the refrigerant pipe 5 and the check valve 26b.
  • the liquid refrigerant that has passed through the check valve 26b is separated by the gas-liquid separator 21 and merged with the intermediate-pressure liquid refrigerant that has been expanded by the second expansion device 23 to an intermediate pressure (for example, high pressure of about ⁇ 0.3 MPa). To do.
  • the merged liquid refrigerant passes through the check valve 26a and the refrigerant pipe 5, and is then expanded by the load side expansion device 32 to become a low-temperature / low-pressure gas-liquid two-phase refrigerant.
  • This two-phase refrigerant flows into the load-side heat exchanger 31 of the indoor unit 30a that functions as an evaporator, and absorbs heat from the room air, thereby becoming a low-temperature and low-pressure gas refrigerant while cooling the room air.
  • the gas refrigerant that has flowed out of the load-side heat exchanger 31 flows out of the relay device 20 via the refrigerant pipe 5 and the opening / closing device 25b, and flows into the heat source devices 1A and 1B again through the refrigerant pipe 4b.
  • the refrigerant that has flowed into each of the heat source devices 1A and 1B passes through the check valve 14d and is again sucked into the compressor 10 via the first flow path switching device 11 and the accumulator 13.
  • FIG. 5 is a refrigerant circuit diagram illustrating a refrigerant flow when the air-conditioning apparatus of FIG. 1 is in the heating main operation mode.
  • FIG. 5 illustrates a case where a cooling load is generated in the indoor unit 30a and a heating load is generated in the indoor unit 30b.
  • the first flow path switching device 11 relays the heat source side refrigerant discharged from the compressor 10 without passing through the heat source side heat exchanger 12. It is switched to flow into the device 20.
  • 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 first flow path switching device 11 and the check valve 14a and flows out from the heat source devices 1A and 1B.
  • the high-temperature and high-pressure gas refrigerant that has flowed out of the heat source devices 1A and 1B flows into the relay device 20 through the refrigerant pipe 4a on the high-pressure refrigerant side.
  • the high-temperature and high-pressure gas refrigerant that has flowed into the relay device 20 flows into the indoor unit 30b after passing through the gas-liquid separator 21, the opening / closing device 25a of the second flow path switching device 24b, and the refrigerant pipe 5.
  • the high-temperature and high-pressure gas refrigerant flows into the load-side heat exchanger 31 of the indoor unit 30b that acts as a condenser and dissipates heat to the indoor air, thereby turning into a liquid refrigerant while heating the indoor space.
  • the liquid refrigerant that has flowed out of the load side heat exchanger 31 of the indoor unit 30b is expanded by the load side expansion device 32, and passes through the check pipe 26b on the refrigerant pipe 5 and the second flow path switching device 24b side, A branch is made to a check valve 26a on the second flow path switching device 24a side and a second expansion device 23 used as a bypass.
  • the liquid refrigerant that has flowed into the check valve 26 a flows into the indoor unit 30 a after passing through the refrigerant pipe 5.
  • the liquid refrigerant is expanded by the load-side throttle device 32 and becomes a low-temperature / low-pressure two-phase refrigerant.
  • This two-phase refrigerant flows into the load-side heat exchanger 31 acting as an evaporator and absorbs heat from the room air, so that it becomes a low-temperature and low-pressure gas refrigerant while cooling the room air.
  • the gas refrigerant flowing out from the load-side heat exchanger 31 passes through the refrigerant pipe 5 and the opening / closing device 25a, and then merges with the liquid refrigerant bypassed at the outlet of the second expansion device 23 and flows out from the relay device 20.
  • the merged refrigerant flows into the heat source units 1A and 1B again through the refrigerant pipe 4b, passes through the check valve 14b, absorbs heat from the outdoor air in the heat source side heat exchanger 12, and is cooled at low temperature and low pressure. become. Then, the low-temperature and low-pressure gas refrigerant is again sucked into the compressor 10 via the first flow path switching device 11 and the accumulator 13.
  • the control of each operation mode and the control of the refrigerant circuit 100A described above are performed by the control device 50.
  • the control device 50 is constituted by a microcomputer or the like, and controls the operation of the entire device based on detection information from various sensors and instructions from a remote controller.
  • the control device 50 is illustrated as being provided in the heat source unit 1A, it may be provided on the indoor units 30a to 30d side, or may be provided on the heat source units 1A and 1B or the indoor units 30a to 30d. May be provided separately.
  • the air conditioner 100 includes a first pressure sensor 41 that detects the pressure of the refrigerant flowing between the gas-liquid separator 21 and the first throttling device 22, and the pressure of the refrigerant that has passed through the first throttling device 22.
  • the second pressure sensor 42 to be detected, the first temperature sensor 43 provided between the load side heat exchanger 31 and the load side expansion device 32, the load side heat exchanger 31 and the second flow path switching devices 24a to 24a.
  • a second temperature sensor 44 provided between the second temperature sensor 24d and an indoor temperature sensor 45 that detects the temperature of the indoor air that is an air conditioning load.
  • the first pressure sensor 41, the first temperature sensor 43, and the second temperature sensor 44 function as a refrigerant temperature sensor that detects the temperature of the refrigerant flowing through the load-side heat exchanger 31.
  • the controller 50 controls the first pressure so that the pressure difference between the pressure detected by the first pressure sensor 41 and the pressure detected by the second pressure sensor 42 becomes a predetermined pressure difference (for example, 0.3 MPa).
  • the operation of the diaphragm device 22 is controlled. Further, the control device 50 determines the difference between the value detected by the first pressure sensor 41 and the temperature detected by the first temperature sensor 43 during the heating operation of the indoor units 30a to 30d.
  • the opening degree of the load side throttle device 32 is controlled so that the obtained subcool (supercooling degree) is constant.
  • the control device 50 has a constant superheat (superheat degree) obtained as a difference between the temperature detected by the first temperature sensor 43 and the temperature detected by the second temperature sensor 44 during the cooling operation of the indoor units 30a to 30d.
  • the opening degree of the load side expansion device 32 is controlled so that
  • the air conditioner 100 is installed between the plurality of heat source units 1A and 1B and the indoor units 30a to 30d, and includes a plurality of blocking devices 6a that block the flow of the refrigerant flowing through the refrigerant pipes 4a and 4b. 6b, 7a, 7b.
  • the shutoff devices 6a and 7a are respectively provided in the refrigerant pipes 4a and 4b that connect the heat source device 1A and the relay device 20, and the shutoff devices 6b and 6b are connected to the refrigerant pipes 4a and 4b that connect the heat source device 1B and the relay device 20, respectively. 7b is provided.
  • the shut-off devices 6a, 6b, 7a, and 7b are composed of, for example, two-way valves, and are opened when power is supplied and closed when power supply is stopped.
  • the opening / closing operation of the shut-off devices 6a, 6b, 7a, 7b is controlled by the control device 50.
  • the shut-off devices 6a, 7a are closed and the heat source unit 1B
  • the shut-off devices 6b and 7b are closed.
  • the air conditioner 100 is installed in each of the heat source devices 1A and 1B, and has a leak detection unit 46 that detects refrigerant leak.
  • the control device 50 is based on the detection result in the leak detection unit 46, and the shut-off device 6a, 6b, 7a and 7b are controlled.
  • FIG. 6 is a functional block diagram showing an example of a control device in the air conditioner of FIG. 1 and 6, the leak detection unit 46 calculates the refrigerant concentration based on the concentration detection unit 46a having a detection member whose resistance value changes according to the refrigerant concentration and the resistance value of the concentration detection unit 46a.
  • a leakage determination unit 46b is a functional block diagram showing an example of a control device in the air conditioner of FIG. 1 and 6, the leak detection unit 46 calculates the refrigerant concentration based on the concentration detection unit 46a having a detection member whose resistance value changes according to the refrigerant concentration and the resistance value of the concentration detection unit 46a.
  • the leakage determination unit 46b calculates the concentration of the refrigerant based on the resistance value of the detection member of the concentration detection unit 46a, and determines whether or not the refrigerant is leaking.
  • the leakage determination unit 46b stores the relationship between the resistance value of the detection member of the concentration detection unit 46a and the refrigerant concentration, and the leakage determination unit 46b calculates the refrigerant concentration based on the resistance value of the concentration detection unit 46a.
  • a predetermined concentration value is set in advance in the leakage determination unit 46b, and the leakage determination unit 46b determines that the refrigerant is not leaking when the refrigerant concentration is less than the predetermined concentration value.
  • the leak determination unit 46b determines that a refrigerant leak has occurred when the refrigerant concentration is equal to or higher than a predetermined concentration.
  • the predetermined concentration corresponds to the refrigerant leakage limit concentration or explosion limit lower limit value employed in the air conditioner 100.
  • the predetermined concentration when carbon dioxide is used as the refrigerant is preferably set to about 1/10 of the leakage limit concentration.
  • the control device 50 controls the operation to be continued if the refrigerant circuit 100A can be operated even when some of the shut-off devices are activated. However, the refrigerant leakage is occurring and a part of the refrigerant circuit is blocked by the blocking device. For this reason, the refrigerant
  • the control device 50 includes a cutoff control unit 51, an operation control unit 52, and a capability setting unit 53.
  • the blocking control unit 51 closes the blocking devices 6a, 7a and 6b, 7b to block the refrigerant flow.
  • the shut-off control unit 51 operates the shut-off device on the side of the heat source unit that has been determined that the refrigerant has leaked, and the shut-off device on the side of the heat source unit that has not leaked the refrigerant remains in an inactive state. To do.
  • the operation control unit 52 controls the operation of the refrigerant circuit 100A. For example, the driving frequency of the compressor 10, the rotational speed (including ON / OFF) of the blower (not shown), and switching of the first flow path switching device 11 are performed. The opening degree of the first throttle device 22 and the second throttle device 23, the switching of the second flow path switching devices 24a to 24d, the opening degree of the load side throttle device 32, and the like are controlled. Further, the operation control unit 52 has a function of controlling switching of the various operation modes described above.
  • the operation control unit 52 is within the range of the limited heat exchange capacity Qe1 and Qc1 even in a state where the flow of the refrigerant to any one of the heat source devices 1A and 1B is interrupted. Drive in.
  • the operation control unit 52 controls the maximum number of the indoor units 30a to 30d by reducing the number of the indoor units 30a to 30d, or reducing the indoor fan air volume or the upper limit of the operating frequency of the compressor 10. Suppress ability.
  • the operation control unit 52 stops the operation when all the shut-off devices 6a, 6b, 7a, and 7b are in the operating state.
  • the capacity setting unit 53 sets the limited heat exchange capacities Qe1 and Qc1 when driving by operating the heat source apparatus in which the shut-off device is in the non-operating state when the shut-off device is in the non-operating state. Is.
  • the capacity setting unit 53 sets the limited heat exchange capacities Qe1 and Qc1
  • the capacity setting unit 53 is in the shut-off device 6b in the non-operating state.
  • 7b the limited heat exchange capacities Qe1 and Qc1 when the operation is continued by the heat source device 1B connected to 7b are set.
  • the above-described operation control unit 52 performs a refrigerant state confirmation operation for controlling the compressor 10 to be driven at the set rotational speed. . Furthermore, the operation control unit 52 controls the refrigerant flow path to execute both the cooling only operation mode and the heating only operation mode during the refrigerant state confirmation operation. Then, the capacity setting unit 53 calculates a limited heat exchange capacity Qe1 during cooling operation and a limited heat exchange capacity Qc1 during heating operation when the heat source unit 1A is shut off.
  • the capacity setting unit 53 calculates the heat exchange temperature differences ⁇ Te1 and ⁇ Tc1 during the refrigerant state check operation, and the limited heat exchange capacity Qe1 and Qc1 based on the heat exchange temperature differences ⁇ Te1 and ⁇ Tc1.
  • An ability calculating unit 53b to calculate and a storage unit 53c are provided.
  • the temperature difference calculation unit 53a acquires the refrigerant temperature Te1 detected by the first temperature sensor 43 and the air temperature Tair1 detected by the indoor temperature sensor 45 in the cooling only operation mode of the refrigerant state confirmation operation.
  • the temperature difference calculation part 53a calculates heat exchange temperature difference (DELTA) Te1 of the load side heat exchanger 31 (evaporator) based on following formula (1).
  • the temperature difference calculation unit 53a is detected by the refrigerant temperature Tc1 obtained by converting the pressure detected by the first pressure sensor 41 into the saturation temperature and the indoor temperature sensor 45 in the heating only operation mode of the refrigerant state confirmation operation.
  • the air temperature Tair1 is acquired.
  • the temperature difference calculation part 53a calculates heat exchange temperature difference (DELTA) Tc1 of the load side heat exchanger 31 (condenser) based on following formula (2).
  • the heat exchange temperature differences ⁇ Te1 and ⁇ Tc1 are calculated for each of the indoor units 30a to 30d. For example, an average value or the like is used.
  • the capacity calculator 53b sets the limited heat exchange capacities Qe1 and Qc1 based on the heat exchange temperature differences ⁇ Te1 and ⁇ Tc1 calculated by the temperature difference calculator 53a.
  • a set evaporator capacity Qestd during cooling operation and a set condenser capacity Qcstd during heating operation are stored in advance as set heat exchange capacities.
  • the set evaporator capacity Qestd and the set condenser capacity Qcstd are determined by the total capacity of the indoor units 30a to 30d connected to the heat source units 1A and 1B.
  • the storage unit 53c stores initial heat exchange temperature differences ⁇ Te0 and ⁇ Tc0 during a test operation or an initial refrigerant state confirmation operation.
  • the operation control unit 52 also performs the refrigerant state confirmation operation when the initial refrigerant state confirmation signal is received by a trial operation at the time of installation of the air conditioning apparatus 100 or a button operation.
  • the initial heat exchange temperature differences ⁇ Te0 and ⁇ Tc0 are calculated in the same manner as described above during the initial refrigerant state confirmation operation such as during a test operation.
  • the temperature difference calculation unit 53a is configured to detect the initial refrigerant temperature Te0 detected by the first temperature sensor 43 and the initial air temperature Tair0 detected by the indoor temperature sensor 45 in the initial cooling operation mode of the refrigerant state confirmation operation. Based on the above, the initial heat exchange temperature difference ⁇ Te0 is calculated based on the following equation (3). Then, the temperature difference calculation unit 53a stores the initial heat exchange temperature difference ⁇ Te0 in the storage unit 53c.
  • the temperature difference calculation unit 53a uses the initial refrigerant temperature Tc0 obtained by converting the pressure detected by the first pressure sensor 41 into the saturation temperature and the indoor temperature sensor 45 in the cooling only operation mode of the initial refrigerant state confirmation operation. Based on the detected initial air temperature Tair0, an initial heat exchange temperature difference ⁇ Tc0 is calculated based on the following equation (4).
  • the capacity calculator 53b calculates the limited heat exchange capacity Qe1 during the cooling operation based on the following formula (5) from the ratio ( ⁇ Te1 / ⁇ Te0) of the heat exchange temperature difference.
  • the capacity calculation unit 53b calculates the limited heat exchange capacity Qc1 during the heating operation based on the ratio ( ⁇ Tc1 / ⁇ Tc0) of the heat exchange temperature difference based on the following formula (6).
  • the operation control unit 52 cancels the refrigerant state confirmation operation, and within the range of the limited heat exchange capabilities Qe1 and Qc1, the cooling operation mode or Perform heating operation mode.
  • the operation control unit 52 controls the maximum number of the indoor units 30a to 30d by reducing the number of the indoor units 30a to 30d, or reducing the indoor fan air volume or the upper limit of the operating frequency of the compressor 10. Suppress ability.
  • FIG. 7 is a flowchart showing an operation example of the air conditioner of FIG. 1, and an operation example of the air conditioner will be described with reference to FIGS.
  • initial heat exchange temperature differences ⁇ Te0 and ⁇ Tc0 are stored in the storage unit 53c in the storage unit 53c in the initial refrigerant state confirmation operation.
  • blocking control part 51 cuts off the interruption
  • step ST3 it is determined in the operation control unit 52 whether or not there is a non-operating cutoff device 6b, 7b (step ST3), and it is determined whether the operation can be continued.
  • the operation of the devices is stopped (NO in step ST3).
  • the operation control unit 52 starts the refrigerant state confirmation operation (step ST4) and the capacity setting unit 53 performs heat exchange during the cooling only operation.
  • a temperature difference ⁇ Te1 and a heat exchange temperature difference ⁇ Tc1 during the heating only operation are calculated (steps ST5 and ST6). Note that either of the heat exchange temperature differences ⁇ Te1 and ⁇ Tc1 may be calculated first.
  • step ST7 the limited heat exchange capacities Qe1 and Qc1 during the cooling operation and the heating operation are calculated in the capacity calculation unit 53b (step ST7). Thereafter, the refrigerant state confirmation operation is canceled, and the cooling operation or the heating operation is performed in a state in which the capacities are set such that the limited heat exchange capacities Qe1 and Qc1 are the upper limit (step ST8).
  • the first embodiment it is possible to block the refrigerant circuit in which leakage occurs at the time of refrigerant leakage and to continue the operation of the heat source machine without refrigerant leakage. At this time, an operation is performed with upper limits of the limited heat exchange capacities Qe1 and Qc1 calculated by the capacity setting unit 53 so as to be lower than the normal capacity. For this reason, the occurrence of an abnormal stop caused by the shortage of refrigerant can be prevented and the operation can be continued reliably.
  • the operation control unit 52 controls the refrigerant circuit 100A so as to execute a refrigerant state confirmation operation in which the compressor 10 is driven at a specified rotational speed.
  • the capacity setting unit 53 has a storage unit 53c that stores the set heat exchange capacities Qestd and Qcstd of the indoor units 30a to 30d, and depends on the state of the load side heat exchanger 31 during the refrigerant state confirmation operation.
  • a limited heat exchange capacity lower than the set heat exchange capacity Qestd, Qcstd is set.
  • the limited heat exchange capacities Qe1 and Qc1 can be accurately set based on the actual refrigerant amount after the shut-off devices 6a, 6b, 7a and 7b are actuated.
  • the capacity setting unit 53 is calculated by the temperature difference calculation unit 53a that calculates the heat exchange temperature differences ⁇ Tc1 and ⁇ Te1 between the refrigerant temperatures Tc1 and Te1 and the air temperature Tair1 during the refrigerant state confirmation operation, and the temperature difference calculation unit 53a.
  • the ratio between the heat exchange temperature differences ⁇ Tc1 and ⁇ Te1 and the initial heat exchange temperature differences ⁇ Tc0 and ⁇ Te0 stored in the storage unit 53c is multiplied by the set evaporator capacity Qestd and the set condenser capacity Qcstd, which are set heat exchange capacity.
  • the limited heat exchange capacities Qe1 and Qc1 can be accurately set based on the actual refrigerant amount after the shut-off devices 6a, 6b, 7a and 7b are actuated.
  • the storage unit 53c is configured so that the initial refrigerant temperature Tc0, Te0 detected by the first pressure sensor 41 or the first temperature sensor 43, which is a refrigerant temperature sensor, and the initial air detected by the indoor temperature sensor 45 are installed.
  • the initial heat exchange temperature differences ⁇ Tc0 and ⁇ Te0 with respect to the temperature Tair0, it is possible to set the limited heat exchange capacities Qe1 and Qc1 that match the installation location or installation situation.
  • Each of the heat source devices 1A and 1B includes a flow path switching device that switches a refrigerant flow path between the cooling operation and the heating operation, and the capacity setting unit 53 sets the limited heat exchange capacities Qc1 and Qe1 during the cooling operation and the heating operation, respectively. If it is set, when the refrigerant leaks, both the cooling operation and the heating operation can be continued.
  • the leak detection unit 46 is installed in the plurality of heat source units 1A and 1B, and the concentration detection unit 46a that detects the leaked refrigerant concentration of the leaked refrigerant, and the leaked refrigerant concentration detected by the concentration detection unit 46a is equal to or greater than a set threshold value. In this case, when it has the leakage determination unit 46b that determines that the refrigerant is leaking, it is possible to accurately detect the leakage of the refrigerant.
  • FIG. FIG. 8 is a refrigerant circuit diagram showing Embodiment 2 of the air-conditioning apparatus according to Embodiment of the present invention.
  • symbol is attached
  • the air conditioner 200 in FIG. 8 is different from the air conditioner 100 in FIG. 1 in that the plurality of heat source devices 1A and 1B and the plurality of indoor units 30a to 30d are directly connected without the relay device 20. is there.
  • the air conditioning apparatus 200 of FIG. 8 has a discharge pressure sensor 241 that is provided on the discharge side of the compressor 10 and detects the discharge pressure of the refrigerant discharged from the compressor 10. Then, the temperature difference calculation unit 53a of the control device 50 uses the initial refrigerant temperature Tc0 and the refrigerant temperature Tc1 obtained by converting the pressure detected by the discharge pressure sensor 241 into the saturation temperature, and the initial heat exchange temperature difference ⁇ Tc0 and the heat exchange temperature. The difference ⁇ Tc1 is calculated.
  • the embodiment of the present invention is not limited to the above embodiment, and various changes can be made.
  • the case where a plurality of indoor units 30a to 30d are provided is illustrated, but it is sufficient that one or more indoor units 30a are connected.
  • the case where the second flow path switching devices 24a to 24d are built in the relay device 20 has been described as an example, they may be built on the indoor units 30a to 30d side.
  • the air conditioning apparatus 100 has been described as being capable of performing a cooling / heating mixed operation, the air conditioning apparatus 100 may be configured to perform only a cooling operation or a heating operation.
  • the heat source side heat exchanger 12 and the load side heat exchanger 31 are equipped with a blower, and in many cases, condensation or evaporation is promoted by blowing, but this is not restrictive.
  • the load-side heat exchanger 31 can be a panel heater using radiation
  • the heat source-side heat exchanger 12 is a water-cooled type that moves heat by water or antifreeze. Can also be used. That is, the heat source side heat exchanger 12 and the load side heat exchanger 31 can be used regardless of the type as long as they have a structure capable of radiating heat or absorbing heat.
  • the leak detection unit 46 is arranged on the heat source unit 1A, 1B side. It may be arranged on the indoor unit 30a to 30d side. Thereby, it is possible to cope with refrigerant leakage of the indoor units 30a to 30d.
  • a shut-off device may be arranged on the refrigerant pipe 5 side in FIG.
  • the refrigerant leakage detection unit is exemplified for the case of determining based on the refrigerant concentration detected by the leakage detection unit 46, but is not limited to this as long as it detects refrigerant leakage.
  • capacitance setting part 53 has illustrated about the case where the limiting heat exchange capability Qe1 and Qc1 are set based on heat exchange temperature difference (DELTA) Tc1 and (DELTA) Te1, set heat exchange capability Qestd at the time of installation, Any method may be used as long as it sets limited heat exchange capacities Qe1 and Qc1 lower than Qcstd.
  • the storage unit 53c stores in advance the limited heat exchange capacities Qe1 and Qc1 when each shut-off device is activated, and the limited heat exchange capacities Qe1 and Qc1 stored in the storage unit 53c when the shut-off device is activated. You may make it set.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

L'invention concerne un dispositif de conditionnement d'air comprenant : une pluralité de dispositifs de fermeture, chacun disposé entre une unité d'intérieur et une pluralité de dispositifs de source de chaleur et interrompant l'écoulement de fluide frigorigène qui coule dans des tuyaux de fluide frigorigène ; une pluralité d'unités de détection de fuites permettant de détecter les fuites de fluide frigorigène à partir de chaque dispositif de source de chaleur ; et un dispositif de commande servant à commander le fonctionnement de la pluralité de dispositifs de source de chaleur, l'unité d'intérieur et les dispositifs de fermeture. Le dispositif de commande comprend : une unité de commande de fermeture servant à actionner le dispositif de fermeture relié au dispositif de source de chaleur qui présente une fuite de fluide frigorigène, lorsqu'une fuite de fluide frigorigène est détectée par l'unité de détection de fuites ; une unité de réglage de capacité servant à fixer, lorsque des dispositifs de fermeture en état de fonctionnement et des dispositifs de fermeture en état de non-fonctionnement sont présents parmi la pluralité de dispositifs de fermeture, une limite de capacité d'échange de chaleur pour l'unité d'intérieur lors de l'actionnement d'un dispositif de source de chaleur relié à un dispositif de fermeture en état de non-fonctionnement ; et une unité de commande de fonctionnement servant à commander le fonctionnement des dispositifs de source de chaleur ou de l'unité d'intérieur à l'aide de la limite de capacité d'échange de chaleur fixée par l'unité de réglage de capacité en tant que limite supérieure.
PCT/JP2015/053462 2015-02-09 2015-02-09 Dispositif de conditionnement d'air WO2016129027A1 (fr)

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GB1711506.4A GB2549897B (en) 2015-02-09 2015-02-09 Air conditioning apparatus
PCT/JP2015/053462 WO2016129027A1 (fr) 2015-02-09 2015-02-09 Dispositif de conditionnement d'air

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7533557B2 (ja) 2022-11-25 2024-08-14 株式会社富士通ゼネラル 空気調和装置

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20230296301A1 (en) * 2022-03-15 2023-09-21 Goodman Manufacturing Company, L.P. Refrigerant leak mitigation for multi-circuit refrigerant systems

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11182990A (ja) * 1997-12-18 1999-07-06 Yamaha Motor Co Ltd 冷媒循環式熱移動装置
JPH11211292A (ja) * 1998-01-26 1999-08-06 Matsushita Electric Ind Co Ltd 冷凍装置の冷媒漏れ検出装置及び冷媒漏れ検出方法
US20030213254A1 (en) * 2002-05-17 2003-11-20 Samsung Electronics Co., Ltd. Air conditioner and control method thereof
JP2007263444A (ja) * 2006-03-28 2007-10-11 Mitsubishi Electric Corp 空気調和装置
JP2008232562A (ja) * 2007-03-22 2008-10-02 Daikin Ind Ltd 空調システム
JP2008249234A (ja) * 2007-03-30 2008-10-16 Mitsubishi Electric Corp 冷凍サイクル装置の故障診断装置及びそれを搭載した冷凍サイクル装置
JP2009257614A (ja) * 2008-04-14 2009-11-05 Hitachi Appliances Inc 空気調和システム
WO2012101673A1 (fr) * 2011-01-26 2012-08-02 三菱電機株式会社 Dispositif de conditionnement d'air
JP2014137161A (ja) * 2013-01-15 2014-07-28 Daikin Ind Ltd 空気調和装置

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11182990A (ja) * 1997-12-18 1999-07-06 Yamaha Motor Co Ltd 冷媒循環式熱移動装置
JPH11211292A (ja) * 1998-01-26 1999-08-06 Matsushita Electric Ind Co Ltd 冷凍装置の冷媒漏れ検出装置及び冷媒漏れ検出方法
US20030213254A1 (en) * 2002-05-17 2003-11-20 Samsung Electronics Co., Ltd. Air conditioner and control method thereof
JP2007263444A (ja) * 2006-03-28 2007-10-11 Mitsubishi Electric Corp 空気調和装置
JP2008232562A (ja) * 2007-03-22 2008-10-02 Daikin Ind Ltd 空調システム
JP2008249234A (ja) * 2007-03-30 2008-10-16 Mitsubishi Electric Corp 冷凍サイクル装置の故障診断装置及びそれを搭載した冷凍サイクル装置
JP2009257614A (ja) * 2008-04-14 2009-11-05 Hitachi Appliances Inc 空気調和システム
WO2012101673A1 (fr) * 2011-01-26 2012-08-02 三菱電機株式会社 Dispositif de conditionnement d'air
JP2014137161A (ja) * 2013-01-15 2014-07-28 Daikin Ind Ltd 空気調和装置

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7533557B2 (ja) 2022-11-25 2024-08-14 株式会社富士通ゼネラル 空気調和装置

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JP6257812B2 (ja) 2018-01-10
GB2549897B (en) 2020-07-22

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