WO2011074028A1 - Climatiseur - Google Patents

Climatiseur Download PDF

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Publication number
WO2011074028A1
WO2011074028A1 PCT/JP2009/006878 JP2009006878W WO2011074028A1 WO 2011074028 A1 WO2011074028 A1 WO 2011074028A1 JP 2009006878 W JP2009006878 W JP 2009006878W WO 2011074028 A1 WO2011074028 A1 WO 2011074028A1
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WO
WIPO (PCT)
Prior art keywords
indoor
heat exchanger
flow rate
connection pipe
refrigerant
Prior art date
Application number
PCT/JP2009/006878
Other languages
English (en)
Japanese (ja)
Inventor
篠崎万誉
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 EP09852226.1A priority Critical patent/EP2515055B1/fr
Priority to PCT/JP2009/006878 priority patent/WO2011074028A1/fr
Priority to JP2011545843A priority patent/JP5734205B2/ja
Priority to US13/511,921 priority patent/US20120285675A1/en
Publication of WO2011074028A1 publication Critical patent/WO2011074028A1/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
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/06—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the arrangements for the supply of heat-exchange fluid for the subsequent treatment of primary air in the room 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
    • F25B47/006—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass for preventing frost
    • 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
    • F25B2313/006—Compression machines, plants or systems with reversible cycle not otherwise provided for two pipes connecting the outdoor side to the indoor side with multiple indoor 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
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves

Definitions

  • the present invention relates to an air conditioner, and more particularly to a multi-room heat pump air conditioner that connects a plurality of indoor units, and can be selectively cooled and heated for each indoor unit,
  • the present invention relates to an air conditioner that can simultaneously operate an indoor unit that performs heating.
  • a conventional air conditioner that can selectively perform cooling and heating for each indoor unit and can simultaneously operate an indoor unit that performs cooling and an indoor unit that performs heating (hereinafter, air that can be operated simultaneously) (Referred to as a harmony machine), for example, "from one heat source machine consisting of a compressor, a four-way switching valve, a heat source machine side heat exchanger, an accumulator, etc., an indoor side heat exchanger, a first flow control device, etc.
  • the first branch portion connected to the connection pipe in a switchable manner and the other of the indoor heat exchangers of the plurality of indoor units are connected via the first flow control device
  • the second A second component connected to the second connection pipe via the flow rate control device Are connected to each other via the second flow rate control device, and the second branch portion and the first connection pipe are further connected to each other via a third flow rate control device.
  • the second flow rate control device, the third flow rate control device, and a repeater incorporating the second branching unit are interposed between the heat source unit and the plurality of indoor units, and
  • the first connection pipe is configured to have a larger diameter than the second connection pipe, a switching valve is provided between the first and second connection pipes of the heat source unit, and the heat source unit side heat exchanger is connected to the condenser.
  • the first connection pipe can be switched to the low-pressure side of the heat source unit and the second connection pipe can be switched to the high-pressure side of the heat source unit in either case of operation or operation of the evaporator.
  • An "air conditioner capable of simultaneous cooling and heating" has been proposed.
  • JP-A-4-335967 (paragraph 0006, FIG. 1)
  • the heat source unit (outdoor) side heat exchanger functions as an evaporator.
  • the heat exchanger (indoor heat exchanger) of the indoor unit during cooling also functions as an evaporator, and the heat source device side heat exchanger and the indoor side heat exchanger functioning as an evaporator are connected in series. It will be.
  • the evaporation temperature of the indoor side heat exchanger functioning as an evaporator also decreases as the evaporation temperature of the heat source unit side heat exchanger decreases. descend.
  • the indoor side heat exchanger which functions as an evaporator is frosted, and there existed a subject that the fall of a cooling capability will arise.
  • cooling operation repeats air_conditionaing
  • the outlet side piping of the indoor heat exchanger in order to prevent the evaporation temperature of the indoor heat exchanger functioning as an evaporator from decreasing, the outlet side piping of the indoor heat exchanger (more specifically, as an evaporator)
  • a throttle device is provided on a pipe that is on the refrigerant outlet side when functioning.
  • This conventional air conditioner adjusts the expansion device to increase the pressure loss on the outlet side of the evaporator, thereby preventing the evaporation temperature of the indoor heat exchanger functioning as an evaporator from being lowered.
  • a throttle device is provided for each indoor heat exchanger. For this reason, since the throttle of each expansion device varies, the flow rate control device provided in the inlet side piping of each indoor side heat exchanger (more specifically, the piping that becomes the refrigerant inlet side when functioning as an evaporator) The aperture adjustment will also change. Therefore, there has been a problem that the operation of the air conditioner becomes unstable.
  • indoor units can be used for cooling operation in places with large sensible heat loads such as computer rooms provided in buildings, that is, in places where the sensible heat ratio (ratio of sensible heat load to cooling load) is large among the cooling loads.
  • the indoor unit currently used in the place of other normal cooling operation load had the subject that required sensible heat capability was not obtained.
  • the sensible heat load is large and the latent heat load (load obtained by excluding the sensible heat load from the cooling load) is small, the evaporation temperature of the indoor heat exchanger decreases due to the balance of the refrigeration cycle, and the indoor heat exchanger freezes. As a result, there was a problem that water leakage occurred.
  • the present invention can prevent frost formation on an indoor heat exchanger that functions as an evaporator even when the outside air temperature is low, and can perform continuous stable operation, and a part of the indoor unit is a computer. Even when used in a place with a large sensible heat load such as a room, an object is to obtain an air conditioner that can obtain a required sensible heat capacity at low cost by using a normal indoor unit as it is.
  • An air conditioner includes a compressor, a four-way switching valve, a heat source machine having a heat source machine-side heat exchanger connected directly or indirectly to the four-way switching valve, an indoor heat exchanger, and the An indoor unit comprising: a plurality of indoor units each having a first flow rate control device connected to one end of the indoor heat exchanger; and a relay unit connecting each of the heat source unit and the indoor unit.
  • Each of these is an air-conditioning apparatus capable of simultaneous cooling and heating operation capable of selectively performing a cooling operation or a heating operation.
  • the relay unit is connected to the heat source unit by the first connection pipe through which the refrigerant flowing out to the heat source unit flows and the second connection pipe through which the refrigerant flowing from the heat source unit flows, and each of the indoor heat exchangers
  • the first branch pipe that connects the other end portion to the first connection pipe or the second connection pipe in a switchable manner, and the first flow control device are respectively connected to the first connection pipe or the second connection pipe.
  • a second branch part that is switchably connected to the pipe, and a flow rate control part that is provided in the first connection pipe and controls the flow rate of the refrigerant flowing through the indoor heat exchanger functioning as an evaporator. is there.
  • the flow rate control unit controls the flow rate of the refrigerant flowing through the indoor heat exchanger functioning as an evaporator (the heat exchanger of the indoor unit during the cooling operation). For this reason, the evaporation temperature of the indoor heat exchanger functioning as an evaporator can be raised. In addition, the sensible heat capacity of the indoor heat exchanger functioning as an evaporator is improved. Therefore, even when the outside air temperature is low, frost formation on the indoor heat exchanger functioning as an evaporator can be prevented and continuous stable operation can be performed. Further, even when a part of the indoor unit is used in a place with a large sensible heat load such as a computer room, the required sensible heat capacity can be obtained at a low cost by using a normal indoor unit as it is.
  • FIG. 1 is a refrigerant circuit diagram illustrating an air-conditioning apparatus according to Embodiment 1 of the present invention.
  • FIG. 1 demonstrates the case where three indoor units and one relay unit are connected to one heat source unit, two or more heat source units, two or more indoor units, and two or more relay units are connected. Even when connected, the same effect can be obtained.
  • the air-conditioning apparatus 100 is an air-conditioning apparatus capable of simultaneous cooling and heating operations in which a cooling operation can be selected in another indoor unit while a cooling operation is selected in another indoor unit.
  • the air conditioner 100 includes a heat source unit A, a relay unit E, and indoor units B, C, and D connected in parallel to each other.
  • the heat source machine A includes a compressor 1, a four-way switching valve 2, a heat source machine side heat exchanger 3, a flow path switching device 30, and the like.
  • the discharge side of the compressor 1 is connected to the connection port of the four-way switching valve 2.
  • the remaining connection port of the four-way switching valve 2 is provided with a suction side of the compressor 1, one end of the heat source device side heat exchanger 3, and a flow path switching device 30. That is, the flow path of the refrigerant discharged from the compressor 1 is switched by the four-way switching valve 2 to a flow path that flows to the heat source apparatus side heat exchanger 3 or a flow path that flows to the flow path switching device 30. Further, the other end of the heat source device side heat exchanger 3 is connected to the flow path switching device 30.
  • the flow path switching device 30 includes four check valves (the check valve 23 to the check valve 26), and one of the four-way switching valve valve 2, the heat source machine side heat exchanger 3, and the first connection pipe 21. And one end of the second connection pipe 22 are connected.
  • the check valve 23 is provided between the heat source device side heat exchanger 3 and the second connection pipe 22 and allows the refrigerant to flow only from the heat source device side heat exchanger 3 to the second connection pipe 22.
  • the check valve 24 is provided between the four-way switching valve 2 and the first connection pipe 21, and allows the refrigerant to flow only from the first connection pipe 21 to the four-way switching valve 2.
  • the check valve 25 is provided between the four-way switching valve 2 and the second connection pipe 22 and allows the refrigerant to flow only from the four-way switching valve 2 to the second connection pipe 22.
  • the check valve 26 is provided between the heat source machine side heat exchanger 3 and the first connection pipe 21, and allows the refrigerant to flow only from the first connection pipe 21 to the heat source machine side heat exchanger 3. .
  • the other end of the second connection pipe 22 branches and is connected to a first branch portion 10 and a second branch portion 11 of the relay machine E described later.
  • the other end of the first connection pipe 21 is connected to the first branching section 10 of the relay machine E described later.
  • the refrigerant discharged from the compressor 1 always flows into the relay machine E through the second connection pipe 22, and the refrigerant flowing out from the relay machine E always has the first connection pipe. 21 will be passed.
  • the pipe diameter of the second connection pipe 22 can be made smaller than the pipe diameter of the first connection pipe 21.
  • Each of the indoor units B, C, and D has the same configuration.
  • the indoor unit B includes an indoor side heat exchanger 5B.
  • One end portion of the indoor side heat exchanger 5B is connected to a second branch portion 11 of the relay unit E described later via a second indoor unit side connection pipe 7B.
  • a flow control device 9B is provided in the second indoor unit side connection pipe 7B.
  • a temperature sensor 4B is provided between the flow control device 9B and the indoor heat exchanger 5B to detect the temperature of the refrigerant flowing through the pipe (or the pipe temperature).
  • the other end of the indoor side heat exchanger 5B is connected to a first branching portion 10 of the relay unit E described later via a first indoor unit side connection pipe 6B.
  • the indoor unit C includes an indoor heat exchanger 5C.
  • One end of the indoor side heat exchanger 5C is connected to a second branching portion 11 of the relay unit E described later via a second indoor unit side connection pipe 7C.
  • the second indoor unit side connection pipe 7C is provided with a flow rate control device 9C.
  • a temperature sensor 4C is provided between the flow control device 9C and the indoor heat exchanger 5C to detect the temperature of the refrigerant flowing through the pipe (or the pipe temperature).
  • the other end of the indoor heat exchanger 5C is connected to a first branching unit 10 of a relay unit E described later via a first indoor unit side connection pipe 6C.
  • the indoor unit D includes an indoor heat exchanger 5D.
  • One end portion of the indoor side heat exchanger 5D is connected to a second branch portion 11 of the relay device E described later via a second indoor unit side connection pipe 7D.
  • a flow control device 9D is provided in the second indoor unit side connection pipe 7D.
  • a temperature sensor 4D is provided between the flow control device 9D and the indoor heat exchanger 5D for detecting the temperature of the refrigerant flowing through the pipe (or the pipe temperature).
  • the other end of the indoor side heat exchanger 5D is connected to a first branching portion 10 of a relay unit E described later via a first indoor unit side connection pipe 6D.
  • the flow rate control device 9 (9B to 9D) corresponds to the first flow rate control device in the present invention.
  • the opening degree of the flow control device 9 (9B to 9D) is controlled as follows. When the corresponding indoor unit (B to D) is in cooling operation, the opening degree of the flow control device 9 (9B to 9D) is controlled based on the degree of superheat on the outlet side of the indoor heat exchanger 5 (5B to 5D). Is done. When the corresponding indoor unit (B to D) is in the heating operation, the opening degree of the flow control device 9 (9B to 9D) is based on the degree of supercooling on the outlet side of the indoor heat exchanger 5 (5B to 5D). Be controlled. In the following description, the reference numerals B to D may be omitted when there is no need to distinguish between the indoor units.
  • the relay machine E includes a first branch unit 10, a second branch unit 11, a gas-liquid separation device 12, a flow rate control device 13, a flow rate control device 15, a heat exchange unit 16, a flow rate control unit 31, and the like. .
  • the first branch unit 10 includes a number of valve devices 8a and 8b corresponding to the number of indoor units.
  • three sets of valve devices 8a and 8b (valve devices 8aB and 8bB, valve devices 8aC and 8bC, and valve devices 8aD and 8bD) are provided.
  • one end of each of the valve devices 8aB and 8bB is connected to the indoor heat exchanger 5B via the first indoor unit side connecting pipe 6B.
  • the other end of the valve device 8aB is connected to the first connection pipe 21, and the other end of the valve device 8bB is connected to the second connection pipe 22.
  • One end of each of the valve devices 8aC and 8bC is connected to the indoor heat exchanger 5C via the first indoor unit side connecting pipe 6C.
  • the other end of the valve device 8aC is connected to the first connection pipe 21, and the other end of the valve device 8bC is connected to the second connection pipe 22.
  • One end of each of the valve devices 8aD and 8bD is connected to the indoor heat exchanger 5D via the first indoor unit side connecting pipe 6D.
  • the other end of the valve device 8aD is connected to the first connection pipe 21, and the other end of the valve device 8bD is connected to the second connection pipe 22.
  • the first branching section 10 controls the opening and closing of the valve device 8a and the valve device 8b, thereby connecting the flow path to which the indoor heat exchanger 5 (5B to 5D) is connected to the first connection pipe 21.
  • the second connection pipe 22 is switched.
  • the second branch portion 11 includes check valves 17 and 18 that are in reverse parallel relation to each other according to the number of indoor units.
  • the check valve 17 allows the refrigerant to flow only in the direction of flowing into the indoor unit.
  • the check valve 18 allows the refrigerant to flow only in the direction of flowing out from the indoor unit.
  • three sets of check valves 17 and 18 (check valves 17B and 18B, check valves 17C and 18C, and check valves 17D and 18D) are provided.
  • one end portion of the check valves 17B and 18B is connected to the indoor heat exchanger 5B via the second indoor unit side connecting pipe 7B.
  • the other end of the check valve 17B is connected to the first meeting portion 17A
  • the other end of the check valve 18B is connected to the second meeting portion 18A.
  • one end of the check valves 17C and 18C is connected to the indoor heat exchanger 5C via the second indoor unit side connecting pipe 7C.
  • the other end of the check valve 17C is connected to the first meeting portion 17A, and the other end of the check valve 18C is connected to the second meeting portion 18A.
  • one end of the check valves 17D and 18D is connected to the indoor heat exchanger 5D via the second indoor unit side connecting pipe 7D.
  • the other end of the check valve 17D is connected to the first meeting portion 17A
  • the other end of the check valve 18D is connected to the second meeting portion 18A.
  • first meeting portion 17A is also connected to the end portion of the second connection pipe 22.
  • 18 A of 2nd meeting parts are also connected also in the middle (2nd connection piping 22 between the flow control device 13 mentioned later and the heat exchange part 16) of the 2nd connection piping 22. As shown in FIG.
  • the second connection pipe 22 is branched and connected to the first branch portion 10 and the second branch portion 11.
  • a gas-liquid separator 12 is provided at this branch.
  • a flow rate control device 13 and a heat exchange unit 16 are provided in the second connection pipe 22 between the gas-liquid separator 12 and the second branching unit 11 from the upstream side of the refrigerant flow.
  • bypass pipe 14 is connected to the second connection pipe 22 between the heat exchange section 16 and the second branch section 11.
  • the other end of the bypass pipe 14 is connected to the first connection pipe 21.
  • the bypass pipe 14 is provided with the heat exchange unit 16 described above. That is, in the heat exchange unit 16, the refrigerant flowing through the second connection pipe 22 and the refrigerant flowing through the bypass pipe 14 exchange heat.
  • the bypass pipe 14 is also provided with a flow rate control device 15 on the upstream side of the refrigerant flow of the heat exchange unit 16.
  • coolant which flowed out from the 2nd branch part 11 flows into the 1st connection piping 21, it will pass this bypass piping 14.
  • the bypass pipe 14 constitutes a part of the first connection pipe 21.
  • a flow rate control unit 31 is provided in the first connection pipe 21 between the first branch unit 10 and the heat source unit A.
  • the flow rate control unit 31 includes a valve device 19 that can be opened and closed, and a capillary tube 20 that is connected in parallel to the valve device 19.
  • the flow control unit 31 controls the flow rate of the refrigerant flowing through the first connection pipe 21 by opening and closing the valve device 19.
  • coolant which flows through the indoor side heat exchanger 5 (the indoor side heat exchanger 5 which flows out a refrigerant
  • the first connection pipe between the flow rate control unit 31 and the first branching unit 10 is provided with a temperature sensor 28 for detecting the temperature (or pipe temperature) of the refrigerant flowing through the pipe.
  • a flow rate control unit 31 may be provided in each of the first indoor unit side connection pipes 6B to 6D, which is a pipe before the refrigerant joins the first connection pipe 21.
  • the first connection pipe 21 (more specifically, the first connection pipe 21 is a pipe after the refrigerant flowing through each of the first indoor unit side connection pipes 6B to 6D merges).
  • the flow rate control unit 31 is provided in the first connection pipe 21) that is upstream of the refrigerant flow with respect to the junction with the bypass pipe 14.
  • a temperature sensor 28 is provided on the upstream side of the refrigerant flow of the flow rate control unit 31.
  • the flow rate control units 31 and the temperature sensor 28 are as many as the number of indoor side heat exchangers. 31 and the temperature sensor 28 are required. That is, there are as many actuators (valve devices 19) to be controlled as the number of indoor heat exchangers, and there are as many detection temperatures (detection temperature of the temperature sensor 28) used for control as the number of indoor heat exchangers. Become. This complicates the control.
  • each flow control unit 31 (more specifically, the valve device 19) performs a throttling operation
  • the flow control devices 9B to 9D change according to the change in the refrigerant flow rate of each indoor heat exchanger that occurs at that time. Aperture adjustment changes. For this reason, the operation of the air conditioner becomes unstable.
  • the first connection pipe 21 (more specifically, the first connection pipe 21 on the upstream side of the refrigerant flow with respect to the junction between the first connection pipe 21 and the bypass pipe 14).
  • the flow rate control unit 31 is provided.
  • a temperature sensor 28 is provided on the upstream side of the refrigerant flow of the flow rate control unit 31.
  • the air conditioning apparatus 100 can perform a stable operation. Thereby, the air conditioning apparatus 100 can perform a stable operation, can simplify the control, and can simplify the piping configuration.
  • the air conditioner 100 roughly performs three types of operation. That is, the air conditioning apparatus 100 performs a cooling only operation, a heating only operation, and a cooling and heating simultaneous operation.
  • the all-cooling operation is an operation in which all of the plurality of indoor units are cooled or stopped.
  • the all-heating operation is an operation in which all of the plurality of indoor units are heated or stopped.
  • Simultaneous cooling / heating operation is an operation mode in which some of the indoor units perform cooling operation and the other part performs heating operation. (Of course, some indoor units are in a stopped state. Also good).
  • movement of two forms is performed. That is, a heating main operation in which most of the indoor units among the plurality of indoor units perform the heating operation and a cooling main operation in which most of the plurality of indoor units perform the cooling operation are performed. Below, the operation state in each driving
  • FIG. 2 is an operation state diagram of the air-conditioning apparatus according to Embodiment 1 of the present invention during a cooling only operation and a heating operation.
  • the solid line arrow shown in FIG. 2 is a refrigerant
  • FIG. 2 shows a case where all of the indoor units B, C, and D are in cooling operation.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 passes through the four-way switching valve 2 and flows into the heat source device side heat exchanger 3.
  • the refrigerant that has flowed into the heat source device side heat exchanger 3 is condensed by exchanging heat with outdoor air, and then flows into the relay device E through the check valve 23 and the second connection pipe 22.
  • the refrigerant flowing into the relay E passes through the gas-liquid separator 12 and the flow rate controller 13 in this order, and then flows into the heat exchange unit 16.
  • the refrigerant that has flowed into the heat exchange unit 16 is cooled by the refrigerant flowing through the bypass pipe 14, and has a sufficient degree of supercooling to flow into the second branch unit 11.
  • the refrigerant that has flowed into the second branch portion 11 is divided into the second indoor unit side connection pipes 7B, 7C, and 7D at the first meeting portion 17A, and flows into the respective flow control devices 9 (9B to 9D).
  • the refrigerant flowing into the flow rate control device 9 (9B to 9D) is depressurized to a predetermined low pressure based on the degree of superheat at the outlet of each indoor heat exchanger 5, and then each indoor unit B, C, D (each room It flows into the inner heat exchanger 5).
  • the refrigerant flowing into each indoor unit B, C, D (each indoor heat exchanger 5) exchanges heat with indoor air in the indoor heat exchanger 5 and is evaporated and gasified, thereby cooling the room.
  • the refrigerant in the gas state includes the first indoor unit side connection pipes 6B, 6C, 6D, the first branching unit 10 (more specifically, the valve devices 8aB, 8aC, 8aD), the flow rate control unit 31, and the first 1 flows into the heat source unit A through the connection pipe 21 of the first unit.
  • the refrigerant flowing into the heat source machine A is sucked into the compressor 1 through the check valve 24 and the four-way switching valve 2.
  • the valve devices 8aB, 8aC, and 8aD are open, and the valve devices 8bB, 8bC, and 8bD are closed.
  • the refrigerant inevitably flows to the check valve 23 and the check valve 24.
  • a part of the refrigerant that has passed through the flow control device 13 flows into the bypass pipe 14.
  • This refrigerant is depressurized to a low pressure by the flow control device 15 and flows into the heat exchange unit 16.
  • the refrigerant decompressed by the flow control device 15 cools and evaporates the refrigerant flowing through the second connection pipe 22 and flows into the first connection pipe 21.
  • This refrigerant merges with the refrigerant that has flowed out of the flow control unit 31, and is sucked into the compressor 1 through the check valve 24 and the four-way switching valve 2.
  • the flow rate control unit 31 is controlled as follows. For example, when raising the evaporation temperature of the indoor side heat exchangers 5B, 5C, and 5D of the indoor units B, C, and D to be cooled, control is performed to close the valve device 19. Further, when the evaporation temperature of the indoor side heat exchangers 5B, 5C, and 5D of the indoor units B, C, and D to be cooled is set to a normal temperature or low, control is performed to open the valve device 19. That is, when the valve device 19 is opened, the flow area of the indoor heat exchangers 5B, 5C, 5D is increased, so that the pressure loss of the indoor heat exchangers 5B, 5C, 5D can be reduced.
  • the evaporating temperature of the indoor side heat exchangers 5B, 5C, 5D can be set to the temperature or lowered.
  • the valve device 19 when the valve device 19 is closed, the refrigerant flows through the capillary tube 20, so that the pressure loss of the indoor heat exchangers 5B, 5C, 5D increases. Therefore, the evaporation temperature of the indoor heat exchangers 5B, 5C, 5D can be increased. In this way, it becomes possible to selectively change the evaporation temperature of the indoor heat exchangers 5B, 5C, 5D.
  • the air-conditioning apparatus 100 according to Embodiment 1 can increase the evaporation temperature of the indoor heat exchangers 5B, 5C, and 5D by controlling the flow rate control unit 31. That is, the sensible heat ratio can be increased by increasing the evaporation temperature of the indoor heat exchangers 5B, 5C, 5D. For this reason, it is possible to select an indoor unit having a small cooling capacity, that is, an indoor unit having a small product shape, as an indoor unit installed in a place with a large sensible heat load such as a computer room. Therefore, cost reduction is possible.
  • the air-conditioning apparatus 100 can also prevent this problem by increasing the evaporation temperature of the indoor heat exchangers 5B, 5C, and 5D.
  • FIG. 2 has shown about the case where all the indoor units B, C, and D carry out heating operation.
  • the high-temperature and high-pressure refrigerant gas discharged from the compressor 1 flows into the relay E through the four-way switching valve 2, the check valve 25, and the second connection pipe 22.
  • the refrigerant that has flowed into the relay E flows into the first branch portion 10 through the gas-liquid separator 12.
  • the refrigerant that has flowed into the first branch portion 10 passes through the valve devices 8bB, 8bC, and 8bD and the first indoor unit side connection pipes 6B, 6C, and 6D, and passes through the indoor units B, C, and D (respective indoor side heat exchanges).
  • the vessel 5 contains the valve devices 8bB, 8bC, and 8bD and the first indoor unit side connection pipes 6B, 6C, and 6D
  • each indoor unit B, C, D (each indoor heat exchanger 5) exchanges heat with indoor air in the indoor heat exchanger 5 to be condensed and liquefied to heat the room.
  • coolant which became the liquid state passes the 2nd indoor unit side connection piping 7B, 7C, 7D through the flow control device 9 controlled by the subcooling degree of the exit of each indoor side heat exchanger 5, and 2nd.
  • the refrigerant that has flowed into the second branch portion 11 passes through the check valves 18B, 18C, and 18D, and then merges at the second meeting portion 18A.
  • the merged refrigerant flows into the flow control device 15 through the second connection pipe 22 and the bypass pipe 14 and is decompressed to a low-pressure gas-liquid two-phase state.
  • the refrigerant depressurized to a low pressure passes through the bypass pipe 14, the heat exchange unit 16, and the first connection pipe 21 and flows into the heat source machine A.
  • the refrigerant that has flowed into the heat source machine A passes through the check valve 26 and flows into the heat source machine side heat exchanger 3.
  • the refrigerant that has flowed into the heat source device side heat exchanger 3 evaporates by exchanging heat with outdoor air and enters a gas state, and is then sucked into the compressor 1 through the four-way switching valve 2.
  • valve devices 8aB, 8aC, and 8aD are in a closed state, and the valve devices 8bB, 8bC, and 8bD are in an open state.
  • the first connection pipe 21 is low pressure and the second connection pipe 22 is high pressure, the refrigerant inevitably flows to the check valve 25 and the check valve 26.
  • FIG. 3 is an operation state diagram during heating main operation in the air-conditioning apparatus according to Embodiment 1 of the present invention.
  • the solid line arrow shown in FIG. 3 is a refrigerant
  • FIG. 3 shows a case where the indoor units B and C perform the heating operation and the indoor unit D performs the cooling operation.
  • the high-temperature and high-pressure refrigerant gas discharged from the compressor 1 flows into the relay E through the four-way switching valve 2, the check valve 25, and the second connection pipe 22.
  • the refrigerant that has flowed into the relay E flows into the first branch portion 10 via the gas-liquid separator 12.
  • the refrigerant that has flowed into the first branch section 10 passes through the valve devices 8bB and 8bC and the first indoor unit side connection pipes 6B and 6C, and the indoor units B and C (indoor heat exchangers 5B and 5C) that are going to be heated. ).
  • the refrigerant that has flowed into the indoor units B and C (the indoor heat exchangers 5B and 5C) exchanges heat with the indoor air to be condensed and liquefied, thereby heating the room. Then, the refrigerant in the liquid state is controlled by the degree of supercooling at the outlets of the indoor heat exchangers 5B and 5C, passes through the flow control devices 9B and 9C in a substantially fully open state, and is slightly reduced in pressure to be high pressure and low pressure. It becomes an intermediate pressure (intermediate pressure). The refrigerant having the intermediate pressure passes through the second indoor unit side connection pipes 7B and 7C and the check valves 18B and 18C, and merges at the second meeting portion 18A.
  • the refrigerant that has joined at the second meeting part 18A of the second branch part 11 flows into the heat exchange part 16.
  • the refrigerant that has flowed into the heat exchanging section 16 is cooled by the refrigerant flowing through the bypass pipe 14, has a sufficient degree of supercooling, and flows out of the heat exchanging section 16.
  • a part of the refrigerant that has flowed out of the heat exchange part 16 flows into the second branch part 11.
  • the refrigerant that has flowed into the second branch portion 11 flows through the first meeting portion 17A and the second indoor unit side connection pipe 7D into the flow control device 9D.
  • the refrigerant that has flowed into the flow control device 9D is depressurized to a predetermined low pressure based on the degree of superheat at the outlet of the indoor heat exchanger 5D, and then flows into the indoor unit D (indoor heat exchanger 5D).
  • the refrigerant that has flowed into the indoor unit D (the indoor heat exchanger 5D) exchanges heat with the indoor air, evaporates and gasifies, and cools the room.
  • the refrigerant in the gas state passes through the first indoor unit side connection pipe 6D, the first branching unit 10 (more specifically, the valve device 8aD), the flow rate control unit 31, and the first connection pipe 21 to be a heat source machine. Flows into A.
  • the refrigerant that has flowed into the heat source machine A passes through the check valve 26 and flows into the heat source machine side heat exchanger 3.
  • the refrigerant that has flowed into the heat source device side heat exchanger 3 evaporates by exchanging heat with outdoor air and enters a gas state, and is then sucked into the compressor 1 through the four-way switching valve 2.
  • the remaining part of the refrigerant that has flowed out of the heat exchange section 16 flows into the bypass pipe 14.
  • This refrigerant is depressurized to a predetermined pressure by the flow control device 15 and flows into the heat exchange unit 16.
  • the refrigerant decompressed by the flow control device 15 cools and evaporates the refrigerant flowing through the second connection pipe 22 and merges with the refrigerant flowing through the first connection pipe 21.
  • the opening degree of the flow control device 15 is controlled so that the difference between the high pressure of the second connection pipe 22 and the intermediate pressure of the second branching section 11 is constant.
  • valve devices 8a and 8b connected to the indoor units B and C to be heated the valve devices 8aB and 8aC are in a closed state, and the valve devices 8bB and 8bC are in an open state.
  • the valve device 8aD is open and the valve device 8bD is closed.
  • the first connection pipe 21 is low pressure and the second connection pipe 22 is high pressure, the refrigerant inevitably flows to the check valve 25 and the check valve 26.
  • the flow rate control unit 31 is controlled as follows. For example, when the evaporation temperature of the indoor heat exchanger 5D of the indoor unit D that is going to be cooled is increased, the valve device 19 is controlled to be closed. Further, when the evaporation temperature of the indoor side heat exchanger 5D of the indoor unit D to be cooled is set to a normal temperature or low, control is performed to open the valve device 19. That is, when the valve device 19 is opened, the flow area of the indoor heat exchanger 5D increases, so that the pressure loss of the indoor heat exchanger 5D can be reduced. Therefore, the evaporation temperature of the indoor heat exchanger 5D can be set to a temperature or can be lowered.
  • the valve device 19 when the valve device 19 is closed, the refrigerant flows through the capillary tube 20, so that the pressure loss of the indoor heat exchanger 5D increases. Therefore, the evaporation temperature of the indoor side heat exchanger 5D of the indoor unit D can be increased. Thus, it becomes possible to selectively change the evaporation temperature of the indoor unit D to be cooled.
  • the evaporation temperature of the heat source device side heat exchanger 3 varies according to the outside air temperature.
  • the evaporation temperature of the indoor side heat exchanger 5D connected in series with the heat source device side heat exchanger 3 is It may decrease as the evaporation temperature of the machine-side heat exchanger 3 decreases, and may be 0 ° C. or lower.
  • frost formation occurs in the indoor heat exchanger 5D.
  • the evaporation temperature of the indoor side heat exchanger 5D of the indoor unit D to be cooled is changed to the second indoor unit side connection pipe 7D (indoor side heat exchanger). It is detected by a temperature sensor 4D provided in the 5D refrigerant inflow side piping.
  • a predetermined temperature for example, 0 ° C.
  • the valve device 19 is closed and the evaporation temperature of the indoor heat exchanger 5D is set to a predetermined temperature (for example, 0 ° C.). ) Keep it higher.
  • a predetermined temperature for example, 0 ° C.
  • the evaporation temperature of the indoor heat exchanger 5D may be detected by the temperature sensor 28.
  • a predetermined temperature for example, 0 ° C.
  • the evaporation temperature of the indoor heat exchanger 5D located upstream of the detected temperature becomes higher by the pressure loss. For this reason, the frost formation to indoor side heat exchanger 5D can be prevented.
  • the sensible heat ratio of the indoor unit D (indoor heat exchanger 5D) is increased by selectively changing the evaporation temperature of the indoor heat exchanger 5D in the flow rate control unit as in the case of the cooling only operation. Can do. For this reason, when the indoor unit D is installed in a place with a large sensible heat load such as a computer room, it is possible to select an indoor unit D having a small cooling capacity, that is, an indoor unit D having a small product shape. . Therefore, cost reduction is possible.
  • the above-mentioned predetermined temperature serving as a threshold value for determining opening and closing of the valve device 19 may be a value other than 0 ° C.
  • the predetermined temperature may be set higher by several degrees C. (for example, 3 degrees C.) in consideration of detection errors of the temperature sensor 4D and the temperature sensor 28, and the like.
  • FIG. 4 is an operation state diagram during cooling main operation in the air-conditioning apparatus according to Embodiment 1 of the present invention.
  • the solid line arrow shown in FIG. 4 is a refrigerant
  • FIG. 3 shows a case where the indoor units B and C perform a cooling operation and the indoor unit D performs a heating operation.
  • the high-temperature and high-pressure refrigerant gas discharged from the compressor 1 passes through the four-way switching valve 2 and exchanges an arbitrary amount of heat in the heat source unit-side heat exchanger 3 to become a gas-liquid two-phase high-temperature and high-pressure refrigerant. It passes through the second connection pipe 22 and flows into the relay machine E. The refrigerant that has flowed into the relay E flows into the gas-liquid separator 12 and is separated into a gas refrigerant and a liquid refrigerant.
  • the gas refrigerant separated by the gas-liquid separator 12 passes through the valve device 8bD of the first branching section 10 and the first indoor unit side connection pipe 6D in this order, and flows into the indoor unit D that is going to be heated.
  • the refrigerant that has flowed into the indoor unit D (each indoor-side heat exchanger 5D) exchanges heat with indoor air to be condensed and liquefied to heat the room.
  • coolant which became the liquid state is controlled by the supercooling degree of the exit of the indoor side heat exchanger 5D, passes the flow control apparatus 9D of a substantially full open state, is decompressed a little, and becomes intermediate pressure.
  • the refrigerant having the intermediate pressure passes through the second indoor unit side connection pipe 7D, the check valve 18D, and the second meeting portion 18A, and then flows through the second connection pipe 22 (separated by the gas-liquid separator 12). Liquefied refrigerant).
  • the liquid refrigerant separated by the gas-liquid separation device 12 of the relay machine E flows into the heat exchange unit 16.
  • the refrigerant that has flowed into the heat exchanging section 16 is cooled by the refrigerant flowing through the bypass pipe 14 to have a sufficient degree of supercooling, flows into the flow control device 13, and is reduced to a predetermined pressure.
  • the opening degree of the flow control device 13 is controlled so that the difference between the high pressure of the second connection pipe 22 on the upstream side of the flow control device 13 and the intermediate pressure of the second branch portion 11 is constant. Is done.
  • Part of the refrigerant that has flowed out of the flow control device 13 flows into the flow control devices 9B and 9C through the first meeting portion 17A of the second branching portion 11 and the second indoor unit side connection pipes 7B and 7C. .
  • the refrigerant flowing into the flow rate control devices 9B and 9C is depressurized to a predetermined low pressure based on the degree of superheat at the outlets of the indoor side heat exchangers 5B and 5C, and then the indoor units B and C (the indoor side heat exchangers 5B and 5C, 5C).
  • the refrigerant that has flowed into the indoor units B and C (the indoor heat exchangers 5B and 5C) exchanges heat with the indoor air and is evaporated and gasified to cool the room.
  • the refrigerant in the gas state passes through the first indoor unit side connection pipes 6B and 6C, the first branch part 10 (more specifically, the valve devices 8aB and 8aC), the flow rate control part 31, and the first connection pipe 21. And flows into the heat source machine A.
  • the refrigerant flowing into the heat source machine A is sucked into the compressor 1 through the check valve 24 and the four-way switching valve 2.
  • the remaining part of the refrigerant that has flowed out of the flow control device 13 flows into the bypass pipe 14.
  • This refrigerant is depressurized to a low pressure by the flow control device 15 and flows into the heat exchange unit 16.
  • the refrigerant decompressed by the flow control device 15 cools and evaporates the refrigerant flowing through the second connection pipe 22 and merges with the refrigerant flowing through the first connection pipe 21.
  • valve devices 8a and 8b connected to the indoor units B and C to be cooled the valve devices 8aB and 8aC are in an open state, and the valve devices 8bB and 8bC are in a closed state.
  • the valve device 8aD is in a closed state and the valve device 8bD is in an open state.
  • the first connection pipe 21 is low pressure and the second connection pipe 22 is high pressure, the refrigerant inevitably flows to the check valve 23 and the check valve 24.
  • the flow control unit 31 is controlled as follows. For example, when raising the evaporation temperature of the indoor side heat exchangers 5B and 5C of the indoor units B and C to be cooled, the valve device 19 is controlled to be closed. In addition, when the evaporation temperature of the indoor side heat exchangers 5B and 5C of the indoor units B and C to be cooled is set to a normal temperature or low, control is performed to open the valve device 19. That is, when the valve device 19 is opened, the flow area of the indoor heat exchangers 5B and 5C is increased, so that the pressure loss of the indoor heat exchangers 5B and 5C can be reduced.
  • the evaporation temperature of the indoor side heat exchangers 5B and 5C can be set to the temperature or lowered.
  • the valve device 19 when the valve device 19 is closed, since the refrigerant flows through the capillary tube 20, the pressure loss of the indoor heat exchangers 5B and 5C increases. Therefore, the evaporation temperature of the indoor heat exchangers 5B and 5C can be increased. Thus, it becomes possible to selectively change the evaporation temperature of the indoor side heat exchangers 5B and 5C of the indoor units B and C to be cooled.
  • the sensible heat ratio of the indoor units B and C is the same as in the cooling only operation. Can be increased. For this reason, when indoor units B and C are installed in a place with a large sensible heat load such as a computer room, indoor units B and C having a small cooling capacity, that is, indoor units B and C having a small product shape are selected. It becomes possible to do. Therefore, cost reduction is possible.
  • FIG. The flow control unit 31 is not limited to the configuration shown in the first embodiment.
  • items not particularly described are the same as those in the first embodiment.
  • FIG. 5 is a refrigerant circuit diagram illustrating an air-conditioning apparatus according to Embodiment 2 of the present invention.
  • the flow control unit 31 of the air-conditioning apparatus 101 according to Embodiment 2 includes a flow control device 27 that can change the opening degree.
  • Other configurations are the same as those of the air-conditioning apparatus 100 shown in the first embodiment.
  • the operation of the air-conditioning apparatus 101 during each operation is also performed except for the flow rate control unit 31. This is the same as the air conditioner 100 shown in the first embodiment.
  • the flow rate control unit 31 is controlled as follows. For example, when increasing the evaporation temperature of the indoor side heat exchangers 5B, 5C, and 5D of the indoor units B, C, and D to be cooled, control is performed to reduce the opening degree of the flow rate control device 27. In addition, when the evaporation temperature of the indoor side heat exchangers 5B, 5C, 5D of the indoor units B, C, D to be cooled is set to a normal temperature or low, the opening degree of the flow control device 27 is increased. I do.
  • the opening degree of the flow control device 27 is increased, the flow area of the indoor heat exchangers 5B, 5C, 5D is increased, so that the pressure loss of the indoor heat exchangers 5B, 5C, 5D can be reduced. Therefore, the evaporating temperature of the indoor side heat exchangers 5B, 5C, 5D can be set to the temperature or lowered.
  • the opening degree of the flow control device 27 is decreased, the pressure loss of the indoor heat exchangers 5B, 5C, 5D increases. Therefore, the evaporation temperature of the indoor heat exchangers 5B, 5C, 5D can be increased.
  • the indoor units B, C, and D are similar to the air conditioner 100 illustrated in the first embodiment.
  • the sensible heat ratio can be increased. For this reason, when the indoor units B, C, and D are installed in a place with a large sensible heat load such as a computer room, the indoor units B, C, and D having a small cooling capacity, that is, the indoor unit B having a small product shape. , C, D can be selected. Therefore, cost reduction is possible.
  • the flow rate control unit 31 includes the flow rate control device 27 that can change the opening degree, the evaporation temperature and the sensible heat ratio of the indoor heat exchangers 5B, 5C, and 5D can be arbitrarily set (for example, linearly) Can be controlled.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Air Conditioning Control Device (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Other Air-Conditioning Systems (AREA)

Abstract

L'invention porte sur un climatiseur grâce auquel le givre est empêché de se former sur un échangeur de chaleur intérieur qui se comporte comme un évaporateur, même si la température extérieure est basse. Une unité intérieure normale peut être utilisée telle quelle, même si elle est utilisée dans un endroit où une partie de l'unité intérieure a une forte charge de chaleur sensible. Le climatiseur divulgué (100) est capable de travailler simultanément en refroidissement/chauffage et il comporte une unité source de chaleur (A), une pluralité d'unités intérieures (B, C, D) et une unité relais (E) qui relie l'unité source de chaleur (A) et les unités intérieures (B, C, D). Une unité de commande du débit (31), qui commande le débit d'un fluide frigorigène qui s'écoule à travers une unité intérieure dans le mode refroidissement, est prévue dans un tuyau (premier tuyau de liaison (21)) en aval d'une section de jonction (première section de dérivation (10)) d'un tuyau dans lequel un fluide frigorigène sortant de l'unité intérieure circule dans le mode refroidissement.
PCT/JP2009/006878 2009-12-15 2009-12-15 Climatiseur WO2011074028A1 (fr)

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PCT/JP2009/006878 WO2011074028A1 (fr) 2009-12-15 2009-12-15 Climatiseur
JP2011545843A JP5734205B2 (ja) 2009-12-15 2009-12-15 空気調和装置
US13/511,921 US20120285675A1 (en) 2009-12-15 2009-12-15 Air-conditioning apparatus

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CN103307668A (zh) * 2012-03-13 2013-09-18 华为技术有限公司 新风盒和新风引入装置
WO2013179334A1 (fr) * 2012-05-30 2013-12-05 三菱電機株式会社 Dispositif de conditionnement d'air
WO2014091741A1 (fr) * 2012-12-10 2014-06-19 パナソニック株式会社 Unité de connexion et climatiseur
US9605885B2 (en) 2013-03-14 2017-03-28 Mitsubishi Electric Corporation Air conditioning system including pressure control device and bypass valve

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US20140116646A1 (en) * 2012-08-29 2014-05-01 Mario Viscovich Conflated Air Conditioning System
JP6053826B2 (ja) * 2012-12-28 2016-12-27 三菱電機株式会社 空気調和装置
EP3121526A4 (fr) * 2014-03-20 2017-12-13 Mitsubishi Electric Corporation Unité côté source de chaleur et climatiseur

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CN103307668A (zh) * 2012-03-13 2013-09-18 华为技术有限公司 新风盒和新风引入装置
CN103307668B (zh) * 2012-03-13 2015-11-25 华为技术有限公司 新风盒和新风引入装置
WO2013179334A1 (fr) * 2012-05-30 2013-12-05 三菱電機株式会社 Dispositif de conditionnement d'air
CN104364591A (zh) * 2012-05-30 2015-02-18 三菱电机株式会社 空气调节装置
JPWO2013179334A1 (ja) * 2012-05-30 2016-01-14 三菱電機株式会社 空気調和装置
CN104364591B (zh) * 2012-05-30 2016-07-27 三菱电机株式会社 空气调节装置
US9719708B2 (en) 2012-05-30 2017-08-01 Mitsubishi Electric Corporation Air-conditioning apparatus with simultaneous heating and cooling operation
WO2014091741A1 (fr) * 2012-12-10 2014-06-19 パナソニック株式会社 Unité de connexion et climatiseur
CN104094063A (zh) * 2012-12-10 2014-10-08 松下电器产业株式会社 连接单元及空调装置
JPWO2014091741A1 (ja) * 2012-12-10 2017-01-05 パナソニックＩｐマネジメント株式会社 接続ユニット及び空気調和装置
CN104094063B (zh) * 2012-12-10 2017-08-04 松下知识产权经营株式会社 连接单元及空调装置
US9605885B2 (en) 2013-03-14 2017-03-28 Mitsubishi Electric Corporation Air conditioning system including pressure control device and bypass valve

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JPWO2011074028A1 (ja) 2013-04-25
EP2515055A4 (fr) 2016-10-26
US20120285675A1 (en) 2012-11-15
EP2515055B1 (fr) 2018-04-25
JP5734205B2 (ja) 2015-06-17
EP2515055A1 (fr) 2012-10-24

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