WO2009133644A1 - 空気調和装置 - Google Patents
空気調和装置 Download PDFInfo
- Publication number
- WO2009133644A1 WO2009133644A1 PCT/JP2008/070841 JP2008070841W WO2009133644A1 WO 2009133644 A1 WO2009133644 A1 WO 2009133644A1 JP 2008070841 W JP2008070841 W JP 2008070841W WO 2009133644 A1 WO2009133644 A1 WO 2009133644A1
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- WO
- WIPO (PCT)
- Prior art keywords
- side refrigerant
- refrigerant
- heat exchanger
- unit
- heat source
- Prior art date
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Classifications
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
- F24F11/32—Responding to malfunctions or emergencies
- F24F11/36—Responding to malfunctions or emergencies to leakage of heat-exchange fluid
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2221/00—Details or features not otherwise provided for
- F24F2221/54—Heating and cooling, simultaneously or alternatively
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
- F25B2400/04—Refrigeration circuit bypassing means
- F25B2400/0401—Refrigeration circuit bypassing means for the compressor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
- F25B2400/14—Power generation using energy from the expansion of the refrigerant
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
- F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
Definitions
- the present invention relates to an air conditioner using a refrigeration cycle, and more particularly to a multi-room air conditioner that includes a plurality of indoor units and can be operated simultaneously with cooling and heating.
- an outdoor unit including a compressor and an outdoor heat exchanger, a plurality of indoor units each having an indoor heat exchanger, and a relay unit that connects the outdoor unit and the indoor unit are provided.
- Cooling operation all cooling operation mode
- heating operation all heating operation mode
- cooling operation in one indoor unit and heating operation in another indoor unit cooling operation capacity larger than heating operation capacity
- an air conditioner that can perform a main operation mode or a heating main operation mode in which the heating operation capacity is larger than the cooling operation capacity.
- the first branch portion formed by switching one of the plurality of indoor units to the first connection pipe or the second connection pipe and the other of the plurality of indoor units are connected.
- the first branch is connected to the second branch portion connected to the second connection pipe via the first flow control device connected to the indoor unit, and further to the first branch via the second flow control device.
- an “air conditioner” in which the first and second connection pipes are extended and connected between the heat source unit and the relay unit see, for example, Patent Document 1).
- a refrigeration cycle apparatus including a second refrigerant cycle, which is provided in a pipe that is annularly connected to a high-pressure pipe, and performs heat exchange between the first refrigerant cycle and the second refrigerant cycle during heating operation.
- a first intermediate heat exchanger and a second intermediate heat exchanger that is provided in a pipe that is annularly connected to the low-pressure pipe and performs heat exchange between the first refrigerant cycle and the second refrigerant cycle during cooling operation.
- a refrigeration cycle apparatus characterized by comprising There has been proposed (e.g., see Patent Document 2).
- the allowable concentration of the refrigerant leaking into the room where the indoor unit is installed is determined by international standards.
- R410A international standard which is one of the flon refrigerant concentration 0.44 kg / m 3
- the permissible concentration by the international standard of carbon dioxide (CO 2) is 0.07 kg / m 3, according to the international standard of propane
- the allowable concentration is 0.008 kg / m 3 .
- the air conditioner as described in Patent Document 1, since it is configured by one refrigerant circuit, when the refrigerant leaks into the room where the indoor unit is installed, all the refrigerant in the refrigerant circuit is discharged. It will leak into this room.
- the air conditioner may use several tens of kilograms or more of refrigerant, and if the refrigerant leaks into the room where the indoor unit of such an air conditioner is installed, the refrigerant concentration in the room or the like May exceed the permissible concentration specified in international standards.
- a heat source side refrigerant circuit heat source side refrigerant cycle
- a use side refrigerant circuit provided in the indoor unit and the branch unit
- the amount of refrigerant leaking into the room or the like can be reduced.
- the first refrigerant is cooled by exchanging heat with the second refrigerant and then returned to the high-pressure pipe.
- the entropy is reduced, and the heating capacity and heat exchange efficiency of the indoor unit are reduced.
- the entropy of the first refrigerant gradually increases, and the cooling capacity and heat exchange efficiency of the indoor unit are reduced.
- the present invention has been made in order to solve the above problems, and is a multi-chamber type capable of simultaneous cooling and heating operation in which a refrigerant that may be affected by the human body is prevented from leaking into a room or the like in which an indoor unit is installed. It aims to provide an air conditioning apparatus.
- the air conditioner according to the present invention includes a compressor, an outdoor heat exchanger, a plurality of intermediate heat exchangers, and a refrigerant flow rate control device provided between the intermediate heat exchangers connected in series.
- the plurality of intermediate heat exchangers and the refrigerant flow rate control device are provided in a relay unit, and the plurality of indoor heat exchangers are provided in each of the plurality of indoor units,
- heat exchange is performed between the heat source side refrigerant circulating in the heat source side refrigerant circuit and the usage side refrigerant circulating in the usage side refrigerant circuit.
- An air conditioner includes a compressor, an outdoor heat exchanger, a plurality of intermediate heat exchangers, a first refrigerant flow control device provided between the intermediate heat exchangers, and the plurality of intermediate heats A second refrigerant flow control device provided on the inlet side of the first intermediate heat exchanger located upstream of the exchanger, and a second intermediate heat exchange located downstream of the plurality of intermediate heat exchangers A plurality of intermediate heat exchangers and a plurality of intermediate heat exchangers connected in parallel to a heat source side refrigerant circuit connected in series with a third refrigerant flow control device provided on the outlet side of the unit A compressor circuit and an outdoor heat exchanger provided in an outdoor unit, the plurality of intermediate heat exchangers, the first refrigerant flow control device, and the second refrigerant flow control device.
- the third refrigerant flow control device is provided in the relay section, and A plurality of indoor heat exchangers are provided in each of the indoor units, and in the plurality of intermediate heat exchangers, a heat source side refrigerant that circulates through the heat source side refrigerant circuit, and a use side refrigerant that circulates through the use side refrigerant circuit; The heat exchange is performed.
- An air conditioner according to the present invention is provided between a compressor, an outdoor heat exchanger, a plurality of intermediate heat exchangers, and each of the intermediate heat exchangers, and recovers expansion power during decompression of the heat source side refrigerant.
- a heat source side refrigerant circuit in which an expansion device refrigerant flow rate control device comprising an expansion power recovery unit and a compression unit that compresses the heat source side refrigerant using the expansion power is connected in series; and each of the plurality of intermediate heat exchangers
- a plurality of use-side refrigerant circuits connected in parallel to each other, and the compressor and the outdoor heat exchanger are provided in an outdoor unit, and the plurality of intermediate heat exchangers and the
- the expansion device refrigerant flow control device is provided in the relay section, the plurality of indoor heat exchangers are provided in each of the plurality of indoor units, and the heat source side refrigerant circuit in the plurality of intermediate heat exchangers Circulating heat source side refrigerant and before A use
- the heat source side refrigerant circuit and the use side refrigerant circuit are made independent while enabling simultaneous cooling and heating, so that the heat source side refrigerant leaks to the place where the indoor unit is installed. There is nothing to do. Therefore, if a highly safe use-side refrigerant is used, the human body will not be adversely affected.
- the above-described effects can be achieved, and the plurality of intermediate heat exchangers (the first intermediate heat exchanger and the second intermediate heat exchanger) provided in the relay portion can be reduced in size. Can be realized. Therefore, it is possible to realize a compact relay unit provided with the intermediate heat exchanger.
- the air conditioner according to the present invention has the above-described effects, and the expansion power of the heat source side refrigerant can be used for boosting the heat source side refrigerant, the power in the compressor can be reduced, and the refrigeration cycle efficiency is improved. improves. *
- FIG. 1 is a circuit diagram illustrating a circuit configuration of an air conditioner according to Embodiment 1.
- FIG. It is a refrigerant circuit figure which shows the flow of the refrigerant
- FIG. 6 is a ph diagram showing the change of the heat source side refrigerant in the cooling main operation mode. It is a refrigerant circuit figure which shows the flow of the refrigerant
- FIG. 6 is a ph diagram showing the change of the heat source side refrigerant in the heating only operation mode.
- FIG. 6 is a ph diagram showing the change of the heat source side refrigerant in the cooling main operation mode. It is a refrigerant circuit diagram which shows the flow of the refrigerant
- FIG. 6 is a ph diagram showing the change of the heat source side refrigerant in the cooling main operation mode.
- 6 is a circuit diagram illustrating a circuit configuration of an air-conditioning apparatus according to Embodiment 2.
- FIG. 6 is a circuit diagram illustrating a circuit configuration of an air-conditioning apparatus according to Embodiment 3.
- FIG. It is a refrigerant circuit figure which shows the flow of the refrigerant
- FIG. 6 is a ph diagram showing the change of the heat source side refrigerant in the cooling main operation mode.
- FIG. 6 is a ph diagram showing the change of the heat source side refrigerant in the heating only operation mode. It is a refrigerant circuit figure which shows the flow of the refrigerant
- FIG. 6 is a ph diagram showing the change of the heat source side refrigerant in the cooling main operation mode. It is a refrigerant circuit diagram which shows the flow of the refrigerant
- FIG. 6 is a circuit diagram illustrating a circuit configuration of an air-conditioning apparatus 400 according to Embodiment 4.
- FIG. FIG. 5 is a ph diagram showing the change of the heat source side refrigerant in the cooling only operation mode.
- FIG. 6 is a ph diagram showing the change of the heat source side refrigerant in the heating only operation mode.
- It is a circuit diagram which shows the circuit structure of the air conditioning apparatus which concerns on Embodiment 5 of this invention.
- FIG. 12 is an installation schematic diagram of an air-conditioning apparatus according to Embodiment 6.
- FIG. 1 is a circuit diagram showing a circuit configuration of an air-conditioning apparatus 100 according to Embodiment 1 of the present invention. Based on FIG. 1, the circuit configuration of the air conditioning apparatus 100 will be described.
- the air conditioner 100 is installed in a building, a condominium, or the like, and uses a refrigeration cycle (heat source side refrigerant circuit and usage side refrigerant circuit) that circulates refrigerant (heat source side refrigerant and usage side refrigerant), thereby cooling load and heating.
- the load can be supplied simultaneously.
- the relationship of the size of each component may be different from the actual one.
- the air conditioning apparatus 100 includes one outdoor unit 10, a plurality of indoor units 30, and one relay unit 20 interposed between these units.
- the air conditioner 100 has a cooling operation mode in which all indoor units 30 perform a cooling operation, a heating operation mode in which all indoor units 30 perform a heating operation, and a cooling load rather than a heating load.
- a large cooling / heating simultaneous operation mode hereinafter referred to as cooling main operation mode
- a cooling / heating simultaneous operation mode hereinafter referred to as heating main operation mode
- the number of outdoor units 10, indoor units 30, and relay unit 20 is not limited to the number shown.
- the outdoor unit 10 has a function of supplying cold heat to the indoor unit 30 via the relay unit 20.
- the indoor unit 30 is installed in a room or the like having an air conditioning target area, and has a function of supplying cooling air or heating air to the air conditioning target area.
- the relay unit 20 has a function of connecting the outdoor unit 10 and the indoor unit 30 and transmitting cold heat supplied from the outdoor unit 10 to the indoor unit 30. That is, the outdoor unit 10 and the relay unit 20 are connected via the first intermediate heat exchanger 21 and the second intermediate heat exchanger 22 provided in the relay unit 20, and both the relay unit 20 and the indoor unit 30 are
- the relay section 20 is connected via a first intermediate heat exchanger 21 and a second intermediate heat exchanger 22.
- the outdoor unit 10 includes a compressor 11, a four-way valve 12 that is a flow path switching unit, and an outdoor heat exchanger 13 that are connected in series by a heat source side refrigerant pipe 1. Further, the outdoor unit 10 includes a heat source side refrigerant flow path including a first connection pipe 4, a second connection pipe 5, a check valve 51, a check valve 52, a check valve 53, and a check valve 54. A switching unit 50 is provided.
- the heat source side refrigerant flow switching unit 50 has a function of setting the flow of the heat source side refrigerant flowing into the relay unit 20 in a certain direction regardless of the operation performed by the indoor unit 30.
- the heat source side refrigerant flow switching unit 50 may not be provided.
- the check valve 51 is provided in the heat source side refrigerant pipe 1 between the relay unit 20 and the four-way valve 12, and allows the flow of the heat source side refrigerant only in a predetermined direction (direction from the relay unit 20 to the outdoor unit 10). To do.
- the check valve 52 is provided in the heat source side refrigerant pipe 1 between the outdoor heat exchanger 13 and the relay unit 20, and the heat source side refrigerant flows only in a predetermined direction (direction from the outdoor unit 10 to the relay unit 20). Is allowed.
- the check valve 53 is provided in the first connection pipe 4, and only in the direction from the heat source side refrigerant pipe 1 connected to the first extension pipe 41 to the heat source side refrigerant pipe 1 connected to the second extension pipe 42.
- the circulation of the heat source side refrigerant is allowed.
- the check valve 54 is provided in the second connection pipe 5 and only in the direction from the heat source side refrigerant pipe 1 connected to the first extension pipe 41 to the heat source side refrigerant pipe 1 connected to the second extension pipe 42. The circulation of the heat source side refrigerant is allowed.
- the first connection pipe 4 connects the heat source side refrigerant pipe 1 on the upstream side of the check valve 51 and the heat source side refrigerant pipe 1 on the upstream side of the check valve 52 in the outdoor unit 10.
- the second connection pipe 5 connects the heat source side refrigerant pipe 1 on the downstream side of the check valve 51 and the heat source side refrigerant pipe 1 on the downstream side of the check valve 52 in the outdoor unit 10.
- the heat source side refrigerant flow switching unit 50 is configured.
- the compressor 11 sucks the heat source side refrigerant and compresses the heat source side refrigerant to a high temperature and high pressure state.
- the compressor 11 may be composed of an inverter compressor capable of capacity control.
- the four-way valve 12 switches the flow of the heat source side refrigerant during the heating operation and the flow of the heat source side refrigerant during the cooling operation.
- the outdoor heat exchanger 13 functions as an evaporator during heating operation, functions as a condenser during cooling operation, and performs heat exchange between air supplied from a blower such as a fan (not shown) and the heat source side refrigerant,
- the heat source side refrigerant is vaporized or condensed and liquefied.
- the heat source side refrigerant flow switching unit 50 has a function of making the flow direction of the heat source side refrigerant flowing into the relay unit 20 constant as described above.
- An indoor heat exchanger 31 is mounted on the indoor unit 30.
- the indoor heat exchanger 31 is connected to a use-side refrigerant flow switching unit 60 provided in the relay unit 20 via a third extension pipe 43 and a fourth extension pipe 44.
- This indoor heat exchanger 31 functions as a condenser during heating operation, functions as an evaporator during cooling operation, and air supplied from a blower such as a fan (not shown) and a use side refrigerant (for this use side refrigerant, Heat exchange is performed between the heating air and the cooling air to be supplied to the air-conditioning target area.
- the relay unit 20 is provided with a first intermediate heat exchanger 21, a refrigerant flow rate control device 25, and a second intermediate heat exchanger 22 that are sequentially connected in series by the heat source side refrigerant pipe 2.
- the relay unit 20 is provided with a first pump 26, a second pump 27, and a use-side refrigerant flow switching unit 60. And while connecting the 1st intermediate
- the first usage side refrigerant pipe 3 a and the second usage side refrigerant pipe 3 b are connected to the third extension pipe 43 and the fourth extension pipe 44.
- the first usage side refrigerant pipe 3a and the second usage side refrigerant pipe 3b may be collectively referred to as a usage side refrigerant pipe 3.
- the first intermediate heat exchanger 21 and the second intermediate heat exchanger 22 function as a condenser or an evaporator, perform heat exchange between the heat source side refrigerant and the use side refrigerant, and supply cold heat to the indoor heat exchanger 31.
- the refrigerant flow control device 25 functions as a pressure reducing valve or an expansion valve, and decompresses the heat source side refrigerant to expand it.
- the refrigerant flow control device 25 may be configured by a device whose opening degree can be variably controlled, for example, an electronic expansion valve.
- the use side refrigerant flow switching unit 60 is an indoor unit that selects either the use side refrigerant exchanged by the first intermediate heat exchanger 21 or the use side refrigerant exchanged by the second intermediate heat exchanger 22. 30.
- the usage-side refrigerant flow switching unit 60 includes a plurality of water flow switching valves (a first switching valve 61 and a second switching valve 62).
- the first switching valve 61 and the second switching valve 62 are provided in a number corresponding to the number of indoor units 30 connected to the relay unit 20 (four in each case).
- the usage-side refrigerant pipe 3 is branched (here, four branches) according to the number of indoor units 30 connected to the relay unit 20 by the usage-side refrigerant flow switching unit 60.
- the path switching unit 60 and the third extension pipe 43 and the fourth extension pipe 44 connected to each of the indoor units 30 are connected. That is, the first switching valve 61 and the second switching valve 62 are provided in each of the branched usage-side refrigerant pipes 3.
- the first switching valve 61 is a utilization side refrigerant pipe 3 between the first pump 26 and the second pump 27 and each indoor heat exchanger 31, that is, a utilization side refrigerant pipe 3 on the inflow side of the indoor heat exchanger 31. Is provided.
- the first switching valve 61 is constituted by a three-way valve, and is connected to the first pump 26 and the second pump 27 via the use side refrigerant pipe 3 and is connected to the third extension pipe via the use side refrigerant pipe 3. 43 is connected.
- the 1st switching valve 61 connects the utilization side refrigerant
- the second switching valve 62 is provided on the use side refrigerant pipe 3 between the indoor heat exchanger 31 and the first intermediate heat exchanger 21 and the second intermediate heat exchanger 22, that is, on the outflow side of the indoor heat exchanger 31. It is provided in the use side refrigerant pipe 3.
- the second switching valve 62 is constituted by a three-way valve, and is connected to the fourth extension pipe 44 through the use side refrigerant pipe 3 and is connected to the first pump 26 and the second through the use side refrigerant pipe 3.
- the pump 27 is connected.
- the second switching valve 62 connects the fourth extension pipe 44 with the use side refrigerant pipe 3a and the use side refrigerant pipe 3b and switches the flow path of the use side refrigerant by being controlled. It is.
- the first pump 26 is provided in the first usage-side refrigerant pipe 3 a between the first intermediate heat exchanger 21 and the first switching valve 61 of the usage-side refrigerant flow switching unit 60, and the first usage-side refrigerant The usage-side refrigerant that conducts through the pipe 3, the third extension pipe 43, and the fourth extension pipe 44 is circulated.
- the second pump 27 is provided in the second usage-side refrigerant pipe 3b between the second intermediate heat exchanger 22 and the first switching valve 61 of the usage-side refrigerant flow switching unit 60, and the second usage-side refrigerant The usage-side refrigerant that conducts through the pipe 3b, the third extension pipe 43, and the fourth extension pipe 44 is circulated.
- the kind of the 1st pump 26 and the 2nd pump 27 is not specifically limited, For example, it is good to comprise by what can control capacity
- the compressor 11, the four-way valve 12, the outdoor heat exchanger 13, the first intermediate heat exchanger 21, the refrigerant flow control device 25, and the second intermediate heat exchanger 22 are combined with the heat source side refrigerant pipe 1,
- the first extension pipe 41, the heat source side refrigerant pipe 2 and the second extension pipe 42 are connected in series in order to constitute the heat source side refrigerant circuit A.
- the first intermediate heat exchanger 21, the first pump 26, the first switching valve 61, the indoor heat exchanger 31, and the second switching valve 62 include the first usage-side refrigerant pipe 3a, the third extension pipe 43, and the fourth switching valve.
- the first use side refrigerant circuit B1 is configured by being connected in series with the extension pipe 44 in order.
- the second intermediate heat exchanger 21, the second pump 27, the first switching valve 61, the indoor heat exchanger 31, and the second switching valve 62 are connected to the second usage-side refrigerant pipe 3b, the third extension pipe 43, and the second switching valve 61, respectively.
- 4 extension piping 44 is connected in series in order, and 2nd utilization side refrigerant circuit B2 is comprised.
- the outdoor unit 10 and the relay unit 20 are connected via the first intermediate heat exchanger 21 and the second intermediate heat exchanger 22 provided in the relay unit 20, and the relay unit 20.
- the indoor unit 30 are connected via a use-side refrigerant flow switching unit 60 provided in the relay unit 20, and circulate through the heat source-side refrigerant circuit A in the first intermediate heat exchanger 21.
- the heat source side refrigerant and the use side refrigerant circulating in the first use side refrigerant circuit B1 circulate in the second intermediate heat exchanger 22 through the heat source side refrigerant circuit and the second use side refrigerant circuit B2 through the heat source side refrigerant circuit A.
- the usage-side refrigerant exchanges heat with each other.
- the first usage side refrigerant circuit B1 and the second usage side refrigerant circuit B2 may be collectively referred to as a usage side refrigerant circuit B.
- the first extension pipe 41 and the second extension pipe 42 connect the outdoor unit 10 and the relay unit 20 via the heat source side refrigerant pipe 1 and the heat source side refrigerant pipe 2.
- the first extension pipe 41 and the second extension pipe 42 are separable between the outdoor unit 10 and the relay unit 20 so that the outdoor unit 10 and the relay unit 20 can be separated.
- the third extension pipe 43 and the fourth extension pipe 44 connect the relay unit 20 and the indoor unit 30 via the use-side refrigerant pipe 3.
- the third extension pipe 43 and the fourth extension pipe 44 are separable between the relay unit 20 and the indoor unit 30 so that the relay unit 20 and the indoor unit can be separated.
- refrigerant circuit A for example, a non-azeotropic refrigerant mixture such as R407C, a pseudo-azeotropic refrigerant mixture such as R410A, or a single refrigerant such as R22 can be used.
- a heat source side refrigerant for example, a refrigerant mainly composed of tetrafluoropropene, etc.
- a heat source side refrigerant flow switching unit 50 is provided as shown in FIG. 1, and the first intermediate heat exchanger 21 and the second intermediate
- the heat exchange performance when heating water can be improved.
- the use side refrigerant circuit B is connected to the indoor heat exchanger 31 of the indoor unit 30 as described above. Therefore, in the air conditioning apparatus 100, in consideration of a case where the usage-side refrigerant leaks into a room or the like where the indoor unit 30 is installed, a highly safe one is used as the usage-side refrigerant. Therefore, for example, water, antifreeze, a mixture of water and antifreeze, a mixture of water and an additive having a high anticorrosion effect, or the like can be used as the use-side refrigerant. According to this configuration, refrigerant leakage due to freezing or corrosion can be prevented even at a low outside air temperature, and high reliability can be obtained. In addition, when the indoor unit 30 is installed in a place that dislikes moisture, such as a computer room, it is possible to use a fluorine-based inert liquid having high thermal insulation as the use-side refrigerant.
- the air conditioner 100 can perform a cooling operation or a heating operation in the indoor unit 30 based on an instruction from each indoor unit 30. That is, the air conditioner 100 can perform the same operation for all of the indoor units 30 and can perform different operations for each of the indoor units 30.
- four operation modes which the air conditioning apparatus 100 performs ie, a cooling only operation mode, a heating only operation mode, a cooling main operation mode, and a heating main operation mode, are demonstrated with the flow of a refrigerant
- coolant ie, a cooling only operation mode, a heating only operation mode, a cooling main operation mode, and a heating main operation mode.
- FIG. 2 is a refrigerant circuit diagram illustrating a refrigerant flow when the air-conditioning apparatus 100 is in the cooling only operation mode.
- FIG. 3 is a ph diagram (diagram illustrating the relationship between the refrigerant pressure and enthalpy) showing the transition of the heat source side refrigerant in the cooling only operation mode.
- tube represented by the thick line shows the piping through which a refrigerant
- the flow direction of the heat source side refrigerant is indicated by a solid line arrow
- the flow direction of the use side refrigerant is indicated by a broken line arrow.
- the refrigerant states at points [a] to [d] shown in FIG. 3 are the refrigerant states at [a] to [d] shown in FIG. 2, respectively.
- the outdoor unit 10 switches the four-way valve 12 so that the heat source side refrigerant discharged from the compressor 11 flows into the outdoor heat exchanger 13.
- the opening of the refrigerant flow control device 25 is narrowed, the first pump 26 is stopped, the second pump 27 is driven, and the first switching valve 61 and the second switching of the usage-side refrigerant flow switching unit 60 are performed.
- the valve 62 is switched so that the use-side refrigerant circulates between the second intermediate heat exchanger 22 and each indoor unit 30. In this state, the operation of the compressor 11 is started.
- a low-temperature / low-pressure vapor refrigerant is compressed by the compressor 11 and discharged as a high-temperature / high-pressure refrigerant.
- the refrigerant compression process of the compressor 11 is represented by an isentropic line shown from the point [a] to the point [b] in FIG. 3 assuming that heat does not enter and exit from the surroundings.
- the high-temperature and high-pressure refrigerant discharged from the compressor 11 passes through the four-way valve 12 and flows into the outdoor heat exchanger 13.
- the outdoor heat exchanger 13 condenses and liquefies while radiating heat to the outdoor air, and becomes a high-pressure liquid refrigerant.
- the change of the refrigerant in the outdoor heat exchanger 13 is performed under a substantially constant pressure.
- the refrigerant change at this time is represented by a slightly inclined straight line that is slightly inclined from the point [b] to the point [c] in FIG.
- the high-pressure liquid refrigerant that has flowed out of the outdoor heat exchanger 13 is conducted through the second extension pipe 42 via the heat source side refrigerant flow switching unit 50 (check valve 52) and flows into the relay unit 20.
- the high-pressure liquid refrigerant that has flowed into the relay unit 20 is expanded (depressurized) by the refrigerant flow control device 25 via the first intermediate heat exchanger 21 to be in a low-temperature / low-pressure gas-liquid two-phase state.
- the change of the refrigerant in the refrigerant flow control device 25 is performed under a constant enthalpy.
- the refrigerant change at this time is represented by the vertical line shown from the point [c] to the point [d] in FIG.
- the refrigerant in the gas-liquid two-phase state throttled by the refrigerant flow control device 25 flows into the second intermediate heat exchanger 22.
- the refrigerant that has flowed into the second intermediate heat exchanger 22 absorbs heat from the use-side refrigerant circulating in the second use-side refrigerant circuit B2, and becomes a low-temperature and low-pressure vapor refrigerant while cooling the use-side refrigerant.
- the change of the refrigerant in the second intermediate heat exchanger 22 is performed under a substantially constant pressure. Considering the pressure loss of the second intermediate heat exchanger 22, the refrigerant change at this time is represented by a slightly inclined straight line that is slightly inclined from the point [d] to [a] in FIG.
- the low-temperature and low-pressure vapor refrigerant flowing out of the second intermediate heat exchanger 22 is conducted through the first extension pipe 41 and compressed through the heat source side refrigerant flow switching unit 50 (check valve 51) and the four-way valve 12. Return to machine 11.
- the low-temperature / low-pressure vapor refrigerant flowing into the compressor 11 is conducted through the refrigerant pipe, so that the pressure is slightly lower than that of the low-temperature / low-pressure vapor refrigerant just after flowing out of the second intermediate heat exchanger 22.
- FIG. 3 it is represented by the same point [a].
- the high-pressure liquid refrigerant flowing into the refrigerant flow control device 25 is conducted through the refrigerant pipe, the pressure is slightly lower than that of the high-pressure liquid refrigerant flowing out of the outdoor heat exchanger 13, but the same is true in FIG. It is represented by point [c].
- the refrigerant pressure loss due to such pipe passage and the pressure loss in the outdoor heat exchanger 13, the first intermediate heat exchanger 21, and the second intermediate heat exchanger 22 are the following heating operation modes and cooling modes. The same applies to the main operation mode and the heating main operation mode, and the description is omitted unless necessary.
- the use side refrigerant in the use side refrigerant circuit B will be described.
- the utilization side refrigerant cooled by the heat source side refrigerant in the second intermediate heat exchanger 22 flows into the utilization side refrigerant flow switching unit 60 by the second pump 27.
- the usage-side refrigerant that has flowed into the usage-side refrigerant flow switching unit 60 is conducted through the usage-side refrigerant piping 3, the first switching valve 61, and the third extension piping 43 and flows into each of the indoor heat exchangers 31.
- the indoor heat exchanger 31 absorbs heat from the room air and cools the air-conditioning target area such as the room where the indoor unit 30 is installed. Thereafter, the use-side refrigerant that has flowed out of the indoor heat exchanger 31 is conducted through the fourth extension pipe 44 and the second switching valve 62 and joined by the use-side refrigerant flow switching unit 60, and then the second intermediate heat exchanger. Re-enters 22.
- FIG. 4 is a refrigerant circuit diagram illustrating a refrigerant flow when the air-conditioning apparatus 100 is in the heating only operation mode.
- FIG. 5 is a ph diagram (diagram illustrating the relationship between the refrigerant pressure and enthalpy) showing the transition of the heat source side refrigerant in the heating only operation mode.
- a pipe represented by a thick line shows a pipe through which the refrigerant (heat source side refrigerant and utilization side refrigerant) circulates.
- the flow direction of the heat source side refrigerant is indicated by a solid line arrow, and the flow direction of the use side refrigerant is indicated by a broken line arrow.
- the refrigerant states at points [a] to [d] shown in FIG. 5 are the refrigerant states at [a] to [d] shown in FIG. 4, respectively.
- the four-way valve 12 causes the heat source side refrigerant discharged from the compressor 11 to flow into the relay unit 20 without passing through the outdoor heat exchanger 13. Switch to.
- the opening of the refrigerant flow control device 25 is throttled, the first pump 26 is driven, the second pump 27 is stopped, and the first switching valve 61 and the second switching of the usage-side refrigerant flow switching unit 60 are performed.
- the valve 62 is switched so that the use-side refrigerant circulates between the first intermediate heat exchanger 21 and each indoor unit 30. In this state, the operation of the compressor 11 is started.
- a low-temperature / low-pressure vapor refrigerant is compressed by the compressor 11 and discharged as a high-temperature / high-pressure refrigerant.
- the refrigerant compression process of the compressor 11 is represented by an isentropic line shown from the point [a] to the point [b] in FIG.
- the high-temperature and high-pressure refrigerant discharged from the compressor 11 is conducted through the second extension pipe 42 through the four-way valve 12 and the heat source side refrigerant flow switching unit 50 (check valve 54), and the relay unit 20 1 flows into the intermediate heat exchanger 21.
- the refrigerant flowing into the first intermediate heat exchanger 21 condenses and liquefies while dissipating heat to the use side refrigerant circulating in the first use side refrigerant circuit B1, and becomes a high-pressure liquid refrigerant.
- the change in the refrigerant at this time is represented by a straight line that is slightly inclined from the point [b] to the point [c] in FIG.
- the high-pressure liquid refrigerant that has flowed out of the first intermediate heat exchanger 21 is conducted through the heat-source-side refrigerant pipe 2, and is squeezed and expanded (decompressed) by the refrigerant flow control device 25 to be in a low-temperature and low-pressure gas-liquid two-phase state Become.
- the refrigerant change at this time is represented by the vertical line shown from the point [c] to the point [d] in FIG.
- the refrigerant in the gas-liquid two-phase state throttled by the refrigerant flow control device 25 passes through the second intermediate heat exchanger 22, conducts the heat source side refrigerant pipe 2 and the first extension pipe 41, and flows into the outdoor unit 10. .
- the refrigerant flows into the outdoor heat exchanger 13 through the heat source side refrigerant flow switching unit 50 (check valve 53). Then, the outdoor heat exchanger 13 absorbs heat from the outdoor air and becomes a low-temperature / low-pressure vapor refrigerant.
- the change in the refrigerant at this time is represented by a straight line that is slightly inclined from the point [d] to the point [a] in FIG.
- the low-temperature and low-pressure vapor refrigerant that has flowed out of the outdoor heat exchanger 13 returns to the compressor 11 via the four-way valve 12.
- the use-side refrigerant in the use side refrigerant circuit B will be described.
- the use-side refrigerant is circulated only in the first use-side refrigerant circuit B1.
- the use-side refrigerant heated by the heat source-side refrigerant in the first intermediate heat exchanger 21 flows into the use-side refrigerant flow switching unit 60 by the first pump 26.
- the usage-side refrigerant that has flowed into the usage-side refrigerant flow switching unit 60 is conducted through the usage-side refrigerant piping 3, the first switching valve 61, and the third extension piping 43 and flows into each of the indoor heat exchangers 31.
- the indoor heat exchanger 31 radiates heat to the room air and heats the air-conditioning target area such as the room where the indoor unit 30 is installed. Thereafter, the use-side refrigerant that has flowed out of the indoor heat exchanger 31 is conducted through the fourth extension pipe 44 and the second switching valve 62, joined at the use-side refrigerant flow switching unit 60, and then the first intermediate heat exchanger. Re-enters 21.
- FIG. 6 is a refrigerant circuit diagram illustrating a refrigerant flow when the air-conditioning apparatus 100 is in the cooling main operation mode.
- FIG. 7 is a ph diagram (diagram illustrating the relationship between refrigerant pressure and enthalpy) showing the transition of the heat source side refrigerant in the cooling main operation mode.
- tube represented by the thick line shows the piping through which a refrigerant
- the flow direction of the heat source side refrigerant is indicated by a solid line arrow
- the flow direction of the use side refrigerant is indicated by a broken line arrow.
- the refrigerant states at points [a] to [e] shown in FIG. 7 are the refrigerant states at [a] to [e] shown in FIG. 6, respectively.
- the cooling main operation mode is a simultaneous cooling / heating operation mode in which the cooling load is larger, for example, in which three indoor units 30 perform cooling operation and one indoor unit 30 performs heating operation. is there.
- the three indoor units 30 that perform the cooling operation are the indoor unit 30a, the indoor unit 30b, and the indoor unit 30c from the left side of the page, and the one indoor unit 30 that is on the right side of the page that performs the heating operation is the indoor unit. It is shown as 30d.
- the first switching valve 61 connected to each of the indoor units 30a to 30d is referred to as a first switching valve 61a to a first switching valve 61d
- the second switching valve 62 connected to each of them is a second switching valve. 62a to the second switching valve 62d are illustrated.
- the outdoor unit 10 uses the four-way valve 12 and the heat source side refrigerant discharged from the compressor 11 to the outdoor heat exchanger 13. Switch to allow inflow.
- the opening degree of the refrigerant flow control device 25 is reduced, and the first pump 26 and the second pump 27 are driven.
- the use side refrigerant flow switching unit 60 of the relay unit 20 the first switching valve 61a to the first switching valve 61c and the second switching valve 62a to the second switching valve 62c are connected to the second intermediate heat exchanger 22 and the indoor unit.
- a low-temperature / low-pressure vapor refrigerant is compressed by the compressor 11 and discharged as a high-temperature / high-pressure refrigerant.
- the refrigerant compression process of the compressor 11 is represented by an isentropic line shown from the point [a] to the point [b] in FIG.
- the high-temperature and high-pressure refrigerant discharged from the compressor 11 passes through the four-way valve 12 and flows into the outdoor heat exchanger 13. Then, it is condensed and liquefied while dissipating heat to the outdoor air in the outdoor heat exchanger 13, and becomes a high-pressure gas-liquid two-phase refrigerant.
- the refrigerant change at this time is represented by a straight line that is slightly inclined from the point [b] to the point [c] in FIG.
- the high-pressure gas-liquid two-phase refrigerant that has flowed out of the outdoor heat exchanger 13 is conducted through the second extension pipe 42 via the heat source side refrigerant flow switching unit 50 (check valve 52) and flows into the relay unit 20.
- the high-pressure gas-liquid two-phase refrigerant flowing into the relay unit 20 is first condensed and liquefied while dissipating heat to the use-side refrigerant circulating in the first use-side refrigerant circuit B1 in the first intermediate heat exchanger 21, and the high-pressure liquid refrigerant and become. That is, the first intermediate heat exchanger 21 functions as a condenser.
- the change in the refrigerant at this time is represented by a straight line that is slightly inclined and shown from point [c] to point [d] in FIG.
- the high-pressure liquid refrigerant that has flowed out of the first intermediate heat exchanger 21 is throttled and expanded (depressurized) by the refrigerant flow rate control device 25 to be in a low-temperature / low-pressure gas-liquid two-phase state.
- the refrigerant change at this time is represented by the vertical line shown from the point [d] to the point [e] in FIG.
- the refrigerant in the gas-liquid two-phase state throttled by the refrigerant flow control device 25 flows into the second intermediate heat exchanger 22.
- the refrigerant that has flowed into the second intermediate heat exchanger 22 absorbs heat from the use-side refrigerant circulating in the second use-side refrigerant circuit B2, and becomes a low-temperature and low-pressure vapor refrigerant while cooling the use-side refrigerant. That is, the second intermediate heat exchanger 22 functions as an evaporator.
- the change in the refrigerant at this time is represented by a slightly inclined straight line shown in FIG. 7 from point [e] to [a].
- the low-temperature and low-pressure vapor refrigerant flowing out from the second intermediate heat exchanger 22 is conducted through the heat-source-side refrigerant pipe 2 and the first extension pipe 41, and the heat-source-side refrigerant flow switching unit 50 (check valve 51) and four-way It returns to the compressor 11 through the valve 12.
- the flow of the use side refrigerant in the use side refrigerant circuit B will be described.
- the usage-side refrigerant is circulated in both the first usage-side refrigerant circuit B1 and the second usage-side refrigerant circuit B2. That is, both the first intermediate heat exchanger 21 and the second intermediate heat exchanger 22 are made to function.
- the flow of the usage-side refrigerant in the first usage-side refrigerant circuit B1 when the indoor unit 30d performs the heating operation will be described, and then the second usage when the indoor unit 30a to the indoor unit 30c perform the cooling operation.
- the flow of the use side refrigerant in the side refrigerant circuit B2 will be described.
- the use side refrigerant heated by the heat source side refrigerant in the first intermediate heat exchanger 21 flows into the use side refrigerant flow switching unit 60 by the first pump 26.
- the usage-side refrigerant that has flowed into the usage-side refrigerant flow switching unit 60 is conducted through the first usage-side refrigerant piping 3a and the third extension piping 43 connected to the first switching valve 61d, and the indoor heat exchange of the indoor unit 30d is performed.
- the indoor heat exchanger 31 radiates heat to the room air and heats the air-conditioning target area such as the room where the indoor unit 30d is installed.
- the use-side refrigerant that has flowed out of the indoor heat exchanger 31 flows out of the indoor unit 30d and is connected to the fourth extension pipe 44 and the first use-side refrigerant pipe 3a, and the use-side refrigerant flow switching unit 60 (second It flows again into the first intermediate heat exchanger 21 via the switching valve 62d).
- the use side refrigerant cooled by the heat source side refrigerant in the second intermediate heat exchanger 22 flows into the use side refrigerant flow switching unit 60 by the second pump 27.
- the usage-side refrigerant that has flowed into the usage-side refrigerant flow switching unit 60 conducts through the second usage-side refrigerant piping 3b and the third extension piping 43 connected to the first switching valve 61a to the first switching valve 61c, and It flows into the indoor heat exchanger 31 of the units 30a to 30c. Then, the indoor heat exchanger 31 absorbs heat from the room air and cools the air-conditioning target area such as the room where the indoor units 30a to 30c are installed.
- the usage-side refrigerant that has flowed out of the indoor heat exchanger 31 flows out of the indoor units 30a to 30c and flows into the fourth extension pipe 44, the second switching valve 62a to the second switching valve 62c, and the second usage-side refrigerant pipe.
- 3 b is conducted and joined at the use side refrigerant flow switching unit 60, and then flows into the second intermediate heat exchanger 22 again.
- FIG. 8 is a refrigerant circuit diagram showing a refrigerant flow when the air-conditioning apparatus 100 is in the heating main operation mode.
- FIG. 9 is a ph diagram (diagram illustrating the relationship between the refrigerant pressure and enthalpy) showing the transition of the heat source side refrigerant in the heating main operation mode.
- a pipe represented by a thick line shows a pipe through which the refrigerant (heat source side refrigerant and utilization side refrigerant) circulates.
- the flow direction of the heat source side refrigerant is indicated by a solid line arrow, and the flow direction of the use side refrigerant is indicated by a broken line arrow.
- the refrigerant states at points [a] to [e] shown in FIG. 9 are the refrigerant states at [a] to [e] shown in FIG. 8, respectively.
- the heating main operation mode is a cooling and heating simultaneous operation mode in the case where the heating load is larger, for example, in which three indoor units 30 perform a heating operation and one indoor unit 30 performs a cooling operation. is there.
- the three indoor units 30 that perform the heating operation are the indoor unit 30a, the indoor unit 30b, and the indoor unit 30c from the left side of the paper, and the one indoor unit 30 that is on the right side of the paper that performs the cooling operation is the indoor unit. It is shown as 30d.
- the first switching valve 61 connected to each of the indoor units 30a to 30d is referred to as a first switching valve 61a to a first switching valve 61d
- the second switching valve 62 connected to each of them is a second switching valve. 62a to the second switching valve 62d are illustrated.
- the outdoor unit 10 uses the four-way valve 12 and the heat source side refrigerant discharged from the compressor 11 to the outdoor heat exchanger 13. It switches so that it may flow into the relay part 20 without going through.
- the opening degree of the refrigerant flow control device 25 is reduced, and the first pump 26 and the second pump 27 are driven.
- the first switching valve 61a to the first switching valve 61c and the second switching valve 62a to the second switching valve 62c are connected to the first intermediate heat exchanger 21 and the indoor unit.
- a low-temperature / low-pressure vapor refrigerant is compressed by the compressor 11 and discharged as a high-temperature / high-pressure refrigerant.
- the refrigerant compression process of the compressor 11 is represented by an isentropic line shown from the point [a] to the point [b] in FIG.
- the high-temperature and high-pressure refrigerant discharged from the compressor 11 is conducted through the second extension pipe 42 through the four-way valve 12 and the heat source side refrigerant flow switching unit 50 (check valve 54), and the relay unit 20 1 flows into the intermediate heat exchanger 21.
- the refrigerant flowing into the first intermediate heat exchanger 21 condenses and liquefies while dissipating heat to the use side refrigerant circulating in the first use side refrigerant circuit B1, and becomes a high-pressure liquid refrigerant. That is, the first intermediate heat exchanger 21 functions as a condenser.
- the refrigerant change at this time is represented by a straight line that is slightly inclined and shown from point [b] to point [c] in FIG.
- the high-pressure liquid refrigerant that has flowed out of the first intermediate heat exchanger 21 is squeezed and expanded (depressurized) by the refrigerant flow control device 25 to be in a low-temperature / low-pressure gas-liquid two-phase state.
- the refrigerant change at this time is represented by the vertical line shown from the point [c] to the point [d] in FIG.
- the gas-liquid two-phase refrigerant throttled by the refrigerant flow control device 25 flows into the second intermediate heat exchanger 22.
- the refrigerant flowing into the second intermediate heat exchanger 22 absorbs heat from the use-side refrigerant circulating in the second use-side refrigerant circuit B2, thereby cooling the use-side refrigerant while maintaining a low-temperature / low-pressure gas-liquid two-phase state.
- the refrigerant change at this time is represented by a slightly inclined straight line that is slightly inclined and shown from [d] to [e] in FIG.
- the low-temperature, low-pressure gas-liquid two-phase refrigerant that has flowed out of the second intermediate heat exchanger 22 is conducted through the heat source side refrigerant pipe 2 and the first extension pipe 41 and flows into the outdoor unit 10.
- the refrigerant flows into the outdoor heat exchanger 13 through the heat source side refrigerant flow switching unit 50 (check valve 53).
- the outdoor heat exchanger 13 absorbs heat from the outdoor air and becomes a low-temperature / low-pressure vapor refrigerant.
- the refrigerant change at this time is represented by a straight line that is slightly inclined from the point [e] to the point [a] in FIG.
- the low-temperature and low-pressure vapor refrigerant that has flowed out of the outdoor heat exchanger 13 returns to the compressor 11 via the four-way valve 12.
- the flow of the use side refrigerant in the use side refrigerant circuit B will be described.
- the usage-side refrigerant is circulated in both the first usage-side refrigerant circuit B1 and the second usage-side refrigerant circuit B2. That is, both the first intermediate heat exchanger 21 and the second intermediate heat exchanger 22 are made to function.
- the flow of the usage-side refrigerant in the first usage-side refrigerant circuit B1 when causing the indoor units 30a to 30c to perform the heating operation will be described, and then the second usage when causing the indoor unit 30d to perform the cooling operation.
- the flow of the use side refrigerant in the side refrigerant circuit B2 will be described.
- the use side refrigerant heated by the heat source side refrigerant in the first intermediate heat exchanger 21 flows into the use side refrigerant flow switching unit 60 by the first pump 26.
- the usage-side refrigerant that has flowed into the usage-side refrigerant flow switching unit 60 conducts through the first usage-side refrigerant piping 3a and the third extension piping 43 that are connected to the first switching valve 61a to the first switching valve 61c. It flows into the indoor heat exchanger 31 of the units 30a to 30c. Then, the indoor heat exchanger 31 radiates heat to the room air, and heats the air-conditioning target area such as the room where the indoor units 30a to 30c are installed.
- the usage-side refrigerant that has flowed out of the indoor heat exchanger 31 flows out of the indoor units 30a to 30c and flows into the fourth extension pipe 44, the second switching valve 62a to the second switching valve 62c, and the first usage-side refrigerant pipe. 3a is conducted and joined at the use-side refrigerant flow switching unit 60, and then flows into the first intermediate heat exchanger 21 again.
- the use side refrigerant cooled by the heat source side refrigerant in the second intermediate heat exchanger 22 flows into the use side refrigerant flow switching unit 60 by the second pump 27.
- the usage-side refrigerant that has flowed into the usage-side refrigerant flow switching unit 60 is conducted through the second usage-side refrigerant piping 3b and the third extension piping 43 connected to the first switching valve 61d, and the indoor heat exchange of the indoor unit 30d is performed.
- the indoor heat exchanger 31 absorbs heat from the room air and cools the air-conditioning target area such as the room where the indoor unit 30d is installed.
- the use-side refrigerant that has flowed out of the indoor heat exchanger 31 flows out of the indoor unit 30d and is connected to the fourth extension pipe 44, the second switching valve 62d, and the second use-side refrigerant pipe 3b, and the use-side refrigerant flow path. It flows into the second intermediate heat exchanger 22 again through the switching unit 60.
- the first usage-side refrigerant circuit connected to the indoor unit 30 installed in a space where a human exists (such as a living space or a space where a human travels). Since the use side refrigerant such as water or antifreeze circulates in B1 and the second use side refrigerant circuit B2, it is prevented that the refrigerant that may affect the human body or safety leaks into the space where humans exist. it can.
- the relay unit 20 since the relay unit 20 is provided with a circuit configuration that enables simultaneous cooling and heating, the outdoor unit 10 and the relay unit 20 are connected to two extension pipes (first extension pipe 41). And the second extension pipe 42), the relay unit 20 and the indoor unit 30 can be connected by two extension pipes (a third extension pipe 43 and a fourth extension pipe 44).
- the outdoor unit 10 and the relay unit 20 may be connected to each other, and the relay unit 20 and the indoor unit 30 may be connected to each other by two extension pipes, so that the cost of piping materials and the installation man-hour can be greatly reduced. Is possible.
- the outdoor unit and the relay unit are connected to each other, and the relay unit and the indoor unit are each connected by four extension pipes.
- the air conditioner 100 according to the first embodiment Since the number of extension pipes can be halved, the cost of the number of pipes can be greatly reduced. In particular, when installed in a building such as a building, the cost due to the piping length can be greatly reduced.
- the refrigerant flow switching unit 50 is provided in the outdoor unit 10, the heat source side refrigerant discharged from the compressor 11 always flows into the relay unit 20 through the second extension pipe 42, and the relay unit 20.
- the heat source side refrigerant flowing out of the refrigerant always flows into the outdoor unit 10 through the first extension pipe 41. Therefore, in the 1st intermediate heat exchanger 21 and the 2nd intermediate heat exchanger 22, since the heat source side refrigerant circuit A and the utilization side refrigerant circuit B always become countercurrent, heat exchange efficiency becomes high.
- the refrigerant flow switching unit 50 is provided in the outdoor unit 10, so that the heat source side refrigerant flowing out from the relay unit 20 always passes through the first extension pipe 41, so that the thickness of the first extension pipe 41 is reduced. This can further reduce the cost of piping.
- the relay unit 20 and the indoor unit 30 are configured to be separable, it is possible to reuse equipment that has conventionally used water refrigerant. That is, it is easy to reuse existing indoor units and extension pipes (extension pipes corresponding to the third extension pipe 43 and the fourth extension pipe 44 according to Embodiment 1) and connect the relay unit 20 to them.
- the air-conditioning apparatus 100 according to Embodiment 1 can be configured.
- the existing indoor unit and the extension pipe can be reused, it is sufficient to install and connect only the relay unit 20 as a common part, and the indoor unit where the indoor unit is installed is not affected. That is, the relay unit 20 can be connected without being restricted during construction.
- the air conditioner 100 since the refrigerant flow control device 25 is provided not in the indoor unit 30 but in the relay unit 20, the flow rate of the refrigerant flowing into the refrigerant flow control device 25 increases.
- the quiet indoor unit 30 can be provided without the vibration caused by the above and the refrigerant sound generated at this time being transmitted to the room where the indoor unit 30 is installed. As a result, the air conditioner 100 does not cause discomfort to the user in the room where the indoor unit 30 is installed.
- FIG. 10 is a circuit diagram showing another circuit configuration of the air conditioner 100. Based on FIG. 10, another circuit configuration of the air conditioning apparatus 100 will be described.
- the air conditioner 100 shown in FIGS. 1 to 9 is configured such that all of the heat source side refrigerant that has passed through the refrigerant flow control device 25 flows into the second intermediate heat exchanger 22, but the air conditioner shown in FIG.
- the apparatus 100 is configured to bypass a part of the heat source side refrigerant without flowing into the second intermediate heat exchanger 22.
- FIG. 10 also shows the refrigerant flow when the air-conditioning apparatus 100 is in the heating main operation mode. Further, in FIG.
- a pipe represented by a thick line shows a pipe through which the refrigerant (heat source side refrigerant and utilization side refrigerant) circulates. Further, the flow direction of the heat source side refrigerant is indicated by a solid line arrow, and the flow direction of the use side refrigerant is indicated by a broken line arrow.
- the relay unit 20 of the air conditioner 100 includes a bypass pipe 45 that bypasses the second intermediate heat exchanger 22 and a bypass that controls the flow rate of the heat-source-side refrigerant that conducts the bypass pipe 45.
- a refrigerant flow rate control device 46 is provided.
- the bypass pipe 45 changes the heat source side refrigerant pipe 2 between the first intermediate heat exchanger 21 and the refrigerant flow control device 25 to the heat source side refrigerant pipe 2 between the second intermediate heat exchanger 22 and the outdoor unit 10. It is provided to connect. Further, the bypass refrigerant flow control device 46 is provided in the bypass pipe 45.
- the heating main operation mode of the air conditioner 100 configured as described above will be described together with the flow of the refrigerant.
- FIG. 11 is a ph diagram (diagram illustrating the relationship between refrigerant pressure and enthalpy) showing the change of the heat source side refrigerant in the heating main operation mode.
- the refrigerant states at points [a] to [g] shown in FIG. 11 are the refrigerant states at [a] to [g] shown in FIG. 10, respectively.
- the three indoor units 30 that perform the heating operation are the indoor unit 30a, the indoor unit 30b, and the indoor unit 30c from the left side of the sheet, and the one indoor unit 30 that performs the cooling operation on the right side of the sheet is the indoor unit. It is shown as 30d.
- the first switching valve 61 is changed to the first switching valve 61a to the first switching valve 61d
- the second switching valve 62 is changed to the second switching valve 62a to the second switching valve 62d. It is shown.
- the outdoor unit 10 switches the four-way valve 12 as in the heating main operation mode described with reference to FIG.
- the refrigerant flow rate control device 25 the first pump 26, the second pump 27, and the use-side refrigerant flow switching unit 60 (the first switching valves 61 and the respective ones) as in the heating main operation mode described in FIG. 8.
- the second switching valve 62 is controlled and the opening degree of the bypass refrigerant flow control device 46 is controlled to be reduced. In this state, the operation of the compressor 11 is started.
- the flow of the heat source side refrigerant in the heat source side refrigerant circuit A will be described.
- a part of the high-pressure liquid refrigerant that has flowed out of the first intermediate heat exchanger 21 is throttled and expanded (depressurized) by the refrigerant flow rate control device 25 to be in a low-temperature / low-pressure gas-liquid two-phase state.
- the refrigerant change at this time is represented by the vertical line shown from the point [c] to the point [d] in FIG.
- the refrigerant in the gas-liquid two-phase state throttled by the refrigerant flow control device 25 flows into the second intermediate heat exchanger 22 and absorbs heat from the use-side refrigerant circulating in the second use-side refrigerant circuit B2, so that the use side While cooling the refrigerant, it becomes a low temperature / low pressure vapor refrigerant.
- the refrigerant change at this time is represented by a slightly inclined straight line that is slightly inclined from [d] to [e] in FIG.
- the remainder of the high-pressure liquid refrigerant that has flowed out of the first intermediate heat exchanger 21 flows into the bypass pipe 45 and is throttled (expanded) by the bypass refrigerant flow control device 46.
- the refrigerant change at this time is represented by a vertical line shown from the point [c] to the point [f] in FIG.
- the refrigerant throttled by the bypass refrigerant flow control device 46 merges with the vapor refrigerant flowing out of the second intermediate heat exchanger 22, becomes a gas-liquid two-phase refrigerant, and flows out of the relay unit 20.
- the gas-liquid two-phase refrigerant flows into the outdoor unit 10 and returns to the compressor 11 via the heat source side refrigerant flow switching unit 50, the outdoor heat exchanger 13, and the four-way valve 12.
- the air conditioner 100 is configured in this way, in addition to having the effects of the air conditioner 100 described with reference to FIGS. 1 to 9, the heat source side refrigerant in the second intermediate heat exchanger 22 in the heating main operation mode.
- the pressure loss can be reduced.
- a superheat degree detector that measures the degree of superheat on the outlet side of the second intermediate heat exchanger 22, for example, the temperature of the refrigerant and
- a superheat degree calculator for calculating the superheat degree, 2
- the effect that the flow rate of the heat source side refrigerant flowing into the intermediate heat exchanger 22 can be controlled by the degree of superheat of the heat source side refrigerant on the outlet side of the second intermediate heat exchanger 22 can also be obtained.
- the relay section 20 is provided with a bypass pipe 48A that bypasses the first intermediate heat exchanger 21 and a bypass refrigerant flow control device 49A that controls the flow rate of the heat-source-side refrigerant that conducts the bypass pipe 48A. Also good.
- FIG. 13 shows a configuration example in which the gas-liquid separator 47 is not provided in the configuration shown in FIG. 12, and the other configuration will be described with reference to FIG.
- the present invention is not limited to this and is supercritical. The same effect can be obtained even when a refrigerant that dissipates heat while the temperature decreases in a state (for example, carbon dioxide that is one of natural refrigerants) is used as the heat source side refrigerant.
- a refrigerant that dissipates heat while the temperature decreases in a state for example, carbon dioxide that is one of natural refrigerants
- the above-described condenser operates as a radiator.
- FIG. 12 is a circuit diagram showing still another circuit configuration of the air conditioner 100. Based on FIG. 12, still another circuit configuration of the air-conditioning apparatus 100 will be described.
- the air conditioning apparatus 100 shown in FIG. 12 is provided with a gas-liquid separator 47 on the upstream side of the first intermediate heat exchanger 21, and in the cooling main operation mode, the vapor refrigerant flows into the first intermediate heat exchanger 21.
- the liquid refrigerant is configured to be bypassed so as not to flow into the first intermediate heat exchanger 21.
- FIG. 12 also shows the refrigerant flow when the air-conditioning apparatus 100 is in the cooling main operation mode. Moreover, in FIG.
- the piping represented by the thick line shows the piping through which the refrigerant (the heat source side refrigerant and the usage side refrigerant) circulates. Further, the flow direction of the heat source side refrigerant is indicated by a solid line arrow, and the flow direction of the use side refrigerant is indicated by a broken line arrow.
- the relay unit 20 of the air conditioner 100 includes a gas-liquid separator 47 that separates the heat-source-side refrigerant into a vapor refrigerant and a liquid refrigerant, and a liquid that is separated by the gas-liquid separator 47.
- a liquid refrigerant bypass pipe 48 that bypasses the refrigerant between the first intermediate heat exchanger 21 and the refrigerant flow control device 25 is provided.
- the gas-liquid separator 47 is provided on the upstream side of the first intermediate heat exchanger 21.
- the liquid refrigerant bypass pipe 48 is provided so as to connect the gas-liquid separator 47 and between the first intermediate heat exchanger 21 and the refrigerant flow control device 25.
- the liquid refrigerant bypass pipe 48 is provided with a liquid refrigerant flow rate control device 49 that controls the flow rate of the heat source side refrigerant that is conducted through the liquid refrigerant bypass pipe 48.
- the cooling main operation mode of the air conditioning apparatus 100 configured as described above will be described together with the flow of the refrigerant.
- FIG. 14 is a ph diagram (diagram showing the relationship between refrigerant pressure and enthalpy) showing the change of the heat source side refrigerant in the cooling main operation mode.
- the refrigerant states at points [a] to [g] shown in FIG. 14 are the refrigerant states at [a] to [g] shown in FIG. 12, respectively.
- the three indoor units 30 that perform the cooling operation are the indoor unit 30a, the indoor unit 30b, and the indoor unit 30c from the left side of the paper, and the one indoor unit 30 that is on the right side of the paper that performs the heating operation is the indoor unit. It is shown as 30d.
- the first switching valve 61 is changed to the first switching valve 61a to the first switching valve 61d
- the second switching valve 62 is changed to the second switching valve 62a to the second switching valve 62d. It is shown.
- the outdoor unit 10 switches the four-way valve 12 in the same manner as the cooling main operation mode described in FIG.
- the refrigerant flow rate control device 25 the first pump 26, the second pump 27, and the use-side refrigerant flow switching unit 60 (the first switching valve 61 and the respective ones) as in the cooling main operation mode described in FIG.
- the second switching valve 62 is controlled, and the gas-liquid separator 47 is controlled to reduce the opening of the liquid refrigerant flow control device 49 so that the vapor refrigerant and the liquid refrigerant are separated. In this state, the operation of the compressor 11 is started.
- a low-temperature / low-pressure vapor refrigerant is compressed by the compressor 11 and discharged as a high-temperature / high-pressure refrigerant.
- the refrigerant compression process of the compressor 11 is represented by an isentropic line shown from the point [a] to the point [b] in FIG.
- the high-temperature and high-pressure refrigerant discharged from the compressor 11 passes through the four-way valve 12 and flows into the outdoor heat exchanger 13. Then, it is condensed and liquefied while dissipating heat to the outdoor air in the outdoor heat exchanger 13, and becomes a high-pressure gas-liquid two-phase refrigerant.
- the refrigerant change at this time is represented by a straight line that is slightly inclined and shown from point [b] to point [c] in FIG.
- the high-pressure gas-liquid two-phase refrigerant that has flowed out of the outdoor heat exchanger 13 is conducted through the second extension pipe 42 via the heat source side refrigerant flow switching unit 50 and flows into the relay unit 20.
- the high-pressure gas-liquid two-phase refrigerant that has flowed into the relay unit 20 flows into the gas-liquid separator 47 and is separated into a vapor-like refrigerant and a liquid refrigerant.
- the refrigerant changes from the gas-liquid two-phase state at point [c] to the saturated vapor at point [d], and from the gas-liquid two-phase state at point [c] to point [e]. It is represented by a broken line arrow that becomes a saturated liquid.
- the vapor refrigerant flows into the first intermediate heat exchanger 21, and the liquid refrigerant is conducted through the liquid refrigerant bypass pipe 48.
- the refrigerant that has flowed into the first intermediate heat exchanger 21 condenses while radiating heat to the use-side refrigerant circulating in the first use-side refrigerant circuit B1 in the first intermediate heat exchanger 21.
- the refrigerant change at this time is represented by a straight line that is slightly inclined from the point [d] to the point [f] in FIG.
- the liquid refrigerant flowing through the liquid refrigerant bypass pipe 48 is slightly decompressed by the liquid refrigerant flow control device 49.
- the refrigerant change at this time is represented by the vertical line shown from the point [e] to the point [f] in FIG.
- the refrigerant that has been slightly decompressed by the liquid refrigerant flow control device 49 then merges with the refrigerant that has radiated heat in the first intermediate heat exchanger 21.
- the merged refrigerant is squeezed and expanded (decompressed) by the refrigerant flow control device 25 to be in a low-temperature / low-pressure gas-liquid two-phase state.
- the refrigerant change at this time is represented by the vertical line shown from the point [f] to the point [g] in FIG.
- the low-temperature, low-pressure gas-liquid two-phase refrigerant throttled by the refrigerant flow control device 25 flows into the second intermediate heat exchanger 22.
- the refrigerant that has flowed into the second intermediate heat exchanger 22 absorbs heat from the use-side refrigerant circulating in the second use-side refrigerant circuit B2, and becomes a low-temperature and low-pressure vapor refrigerant while cooling the use-side refrigerant.
- the change in the refrigerant at this time is represented by a straight line that is slightly inclined from the point [g] to [a] in FIG.
- the low-temperature and low-pressure vapor refrigerant flowing out of the second intermediate heat exchanger 22 is conducted through the heat source side refrigerant pipe 2 and the first extension pipe 41 and compressed through the heat source side refrigerant flow switching unit 50 and the four-way valve 12. Return to machine 11.
- the liquid refrigerant is used when the refrigerant that radiates heat while condensing on the high pressure side is filled. Bypasses the first intermediate heat exchanger 21, and gas refrigerant that can be used for heat dissipation in the first intermediate heat exchanger 21 flows into the first intermediate heat exchanger 21, so that heat is radiated in the first intermediate heat exchanger 21.
- coolant was demonstrated, it is not limited to this, It is a supercritical state as a heat source side refrigerant
- the heat source side refrigerant circuit A may be filled with a refrigerant that dissipates heat.
- the heat exchanger first intermediate heat exchanger 21 or second intermediate heat exchanger 22
- FIG. FIG. 15 is a circuit diagram showing a circuit configuration of an air-conditioning apparatus 200 according to Embodiment 2 of the present invention. Based on FIG. 15, the circuit configuration of the air conditioning apparatus 200 will be described.
- This air conditioner 200 is installed in a building, a condominium, etc., like the air conditioner 100, and uses a refrigeration cycle (heat source side refrigerant circuit and utilization side refrigerant circuit) that circulates refrigerant (heat source side refrigerant and utilization side refrigerant).
- a refrigeration cycle heat source side refrigerant circuit and utilization side refrigerant circuit
- refrigerant heat source side refrigerant and utilization side refrigerant
- the cooling load and the heating load can be supplied simultaneously.
- differences from the first embodiment will be mainly described, and the same parts as those in the first embodiment will be denoted by the same reference numerals and description thereof will be omitted.
- the air conditioner 200 according to the second embodiment is based on the configuration of the air conditioner 100 according to the first embodiment, and a third intermediate between the refrigerant flow control device 25 and the second intermediate heat exchanger 21.
- the relay part 20a which provided the heat exchanger 23 and the 2nd refrigerant
- the refrigerant pipe 2 is connected in series and is provided in the relay portion 20a.
- the third intermediate heat exchanger 23 functions as a condenser or an evaporator like the first intermediate heat exchanger 21 and the second intermediate heat exchanger 22. Similar to the refrigerant flow control device 25, the second refrigerant flow control device 28 decompresses and expands the heat source side refrigerant.
- the first usage side refrigerant pipe 3 a and the second usage side refrigerant pipe 3 b are branched to pass through the third intermediate heat exchanger 23.
- a third switching valve 63 is provided in the first usage-side refrigerant pipe 3a connected to the third intermediate heat exchanger 23, and a fourth switching valve 64 is provided in the second usage-side refrigerant pipe 3b.
- the 3rd switching valve 63 and the 4th switching valve 64 are comprised by the three-way valve, switching the flow of the utilization side refrigerant
- the inflow of the use-side refrigerant to the heat exchanger 23 can be adjusted.
- the air conditioner 200 after the use-side refrigerant that has exchanged heat with the heat-source-side refrigerant in the third intermediate heat exchanger 23 is sucked into the first pump 26 by the third switching valve 63 and the fourth switching valve 64.
- a path that circulates between the indoor unit 30 or a utilization side refrigerant that has exchanged heat with the heat source side refrigerant in the third intermediate heat exchanger 23 is sucked into the second pump 27, and then between the indoor unit 30. Any one of the circulating paths can be selectively switched.
- the third switching valve 63 and the fourth switching valve 64 constitute a second usage side refrigerant flow switching unit 65.
- the air conditioner 100 operates the third intermediate heat exchanger 23 as an evaporator that cools the use-side refrigerant in the same way as the second intermediate heat exchanger 22 in the cooling only operation mode and the cooling main operation mode.
- the third intermediate heat exchanger 23 can be operated as a condenser that heats the use-side refrigerant in the same manner as the first intermediate heat exchanger 21. That is, the third intermediate heat exchanger 23 can be made to function according to the magnitude of the load in the indoor unit 30.
- the third intermediate heat exchanger 23 can be used as a condenser when the indoor unit 30 has a large heat load for heating while having the same effect as the first embodiment. If the indoor unit 30 has a large heat load for cooling, the third intermediate heat exchanger 23 can be used as an evaporator. Therefore, the total capacity of the heat exchanger of the relay part 20a (total capacity of the first intermediate heat exchanger 21, the second intermediate heat exchanger 22, and the third intermediate heat exchanger 23) can be reduced, and the relay part Miniaturization of the heat exchanger provided in 20a can be realized. That is, it can contribute to the compactness of the relay part 20a.
- FIG. 16 is a circuit diagram showing a circuit configuration of an air-conditioning apparatus 300 according to Embodiment 3 of the present invention. Based on FIG. 16, the circuit configuration of the air conditioning apparatus 300 will be described.
- This air conditioner 300 is installed in a building, a condominium, etc., like the air conditioner 100 and the air conditioner 200, and refrigeration cycle (heat source side refrigerant circuit and use side) that circulates refrigerant (heat source side refrigerant and use side refrigerant).
- the cooling load and the heating load can be supplied simultaneously by using the refrigerant circuit.
- differences from the first and second embodiments will be mainly described, and the same parts as those in the first and second embodiments will be denoted by the same reference numerals and the description thereof will be omitted. It shall be.
- the air conditioner 300 according to the third embodiment is based on the configuration of the air conditioner 100 according to the first embodiment, but includes the relay unit 20b provided with the expansion device 80 instead of the refrigerant flow rate control device 25.
- the expansion device 80 includes an expansion power recovery unit 81 that recovers expansion power during decompression of the heat source side refrigerant, a power transmission unit 83 that transmits the expansion power to the compression unit 82, and an expansion transmitted from the power transmission unit 83. And a compression unit 82 that compresses the heat source side refrigerant using power.
- the expansion power recovery unit 81 of the expansion device 80 is installed in the heat source side refrigerant pipe 2 between the first intermediate heat exchanger 21 and the refrigerant flow control device 25.
- the compression unit 82 of the expansion device is installed in the heat source side refrigerant pipe 2 between the second intermediate heat exchanger 22 and the outdoor unit 10.
- the relay unit 20b is provided with a compression unit bypass pipe 85 that bypasses the compression unit 82 of the expansion device 80.
- the compression section bypass pipe 85 connects the heat source side refrigerant pipe 2 on the upstream side of the compression section 82 and the heat source side refrigerant pipe 2 on the downstream side of the compression section 82 to bypass the compression section 82 of the expansion device 80. It is like that.
- the compression unit bypass pipe 85 is provided with a refrigerant flow rate control device 86 for controlling the flow rate of the heat source side refrigerant that is conducted through the compression unit bypass pipe 85.
- the air conditioner 300 can perform a cooling operation or a heating operation in the indoor unit 30 based on an instruction from each indoor unit 30. That is, the air conditioner 300 can execute four operation modes (a cooling only operation mode, a heating only operation mode, a cooling main operation mode, and a heating main operation mode) as with the air conditioning device 100 and the air conditioning device 200. It has become.
- the cooling only operation mode, the heating only operation mode, the cooling main operation mode, and the heating main operation mode executed by the air conditioning apparatus 300 will be described together with the flow of the refrigerant.
- FIG. 17 is a refrigerant circuit diagram illustrating the refrigerant flow when the air-conditioning apparatus 300 is in the cooling only operation mode.
- FIG. 18 is a ph diagram (diagram illustrating the relationship between refrigerant pressure and enthalpy) showing the transition of the heat source side refrigerant in the cooling main operation mode.
- a pipe represented by a thick line shows a pipe through which the refrigerant (heat source side refrigerant and utilization side refrigerant) circulates.
- the flow direction of the heat source side refrigerant is indicated by a solid line arrow
- the flow direction of the use side refrigerant is indicated by a broken line arrow.
- the refrigerant states at points [a] to [e] shown in FIG. 18 are refrigerant states at [a] to [d] shown in FIG. 17, respectively.
- coolant of the use side refrigerant circuit B at the time of this cooling only operation mode since it is the same as that of Embodiment 1, description is abbreviate
- the outdoor unit 10 switches the four-way valve 12 so that the heat source side refrigerant discharged from the compressor 11 flows into the outdoor heat exchanger 13.
- the refrigerant flow rate control device 86 is closed, the first pump 26 is stopped, the second pump 27 is driven, and the first switching valve 61 and the second switching valve 62 of the use-side refrigerant flow switching unit 60 are driven. Is switched between the second intermediate heat exchanger 22 and each indoor unit 30 so that the use-side refrigerant circulates. In this state, the operation of the compressor 11 is started.
- a low-temperature / low-pressure vapor refrigerant is compressed by the compressor 11 and discharged as a high-temperature / high-pressure refrigerant.
- the refrigerant compression process of the compressor 11 is represented by an isentropic line shown from the point [a] to the point [b] in FIG.
- the high-temperature and high-pressure refrigerant discharged from the compressor 11 passes through the four-way valve 12 and flows into the outdoor heat exchanger 13. Then, the outdoor heat exchanger 13 condenses and liquefies while radiating heat to the outdoor air, and becomes a high-pressure liquid refrigerant.
- the refrigerant change at this time is represented by a slightly inclined straight line that is slightly inclined from the point [b] to the point [c] in FIG. 18 in consideration of the pressure loss of the outdoor heat exchanger 13.
- the high-pressure liquid refrigerant that has flowed out of the outdoor heat exchanger 13 is conducted through the second extension pipe 42 via the heat source side refrigerant flow switching unit 50 (check valve 52) and flows into the relay unit 20b.
- the high-pressure liquid refrigerant that has flowed into the relay section 20b is recovered in decompression power by the expansion power recovery section 81 of the expansion device 80 via the first intermediate heat exchanger 21 and decompressed, and is in a low-temperature / low-pressure gas-liquid two-phase state. become.
- the change in the refrigerant in the expansion power recovery unit 81 reduces the enthalpy because the expansion power is recovered.
- the refrigerant change at this time is represented by a slightly inclined vertical line from point [c] to point [d] in FIG.
- the refrigerant in the gas-liquid two-phase state in which the expansion power is recovered and throttled by the expansion power recovery unit 81 flows into the second intermediate heat exchanger 22.
- the refrigerant that has flowed into the second intermediate heat exchanger 22 absorbs heat from the use-side refrigerant circulating in the second use-side refrigerant circuit B2, and becomes a low-temperature and low-pressure vapor refrigerant while cooling the use-side refrigerant.
- the refrigerant change at this time is represented by a slightly inclined straight line that is slightly inclined from [d] to [e] in FIG.
- the low-temperature and low-pressure vapor refrigerant flowing out of the second intermediate heat exchanger 22 is conducted through the heat source side refrigerant pipe 2, flows into the compression unit 82 of the expansion device 80, is recovered by the expansion power recovery unit 81, and transmits power. It is discharged after being compressed by the power transmitted through the section 83.
- the refrigerant change at this time is represented by an isentropic line shown from the point [e] to the point [a] in FIG.
- the refrigerant compressed by the compression unit 82 is conducted through the first extension pipe 41 and returns to the compressor 11 through the heat source side refrigerant flow switching unit 50 (check valve 51) and the four-way valve 12.
- FIG. 19 is a refrigerant circuit diagram illustrating a refrigerant flow when the air-conditioning apparatus 300 is in the heating only operation mode.
- FIG. 20 is a ph diagram (diagram illustrating the relationship between the refrigerant pressure and enthalpy) showing the transition of the heat source side refrigerant in the heating only operation mode.
- a pipe represented by a thick line shows a pipe through which the refrigerant (heat source side refrigerant and utilization side refrigerant) circulates.
- the flow direction of the heat source side refrigerant is indicated by a solid line arrow
- the flow direction of the use side refrigerant is indicated by a broken line arrow.
- the refrigerant states at points [a] to [e] shown in FIG. 20 are the refrigerant states at [a] to [e] shown in FIG. 19, respectively.
- coolant of the use side refrigerant circuit B at the time of this heating only operation mode since it is the same as that of Embodiment 1, description is abbreviate
- the four-way valve 12 causes the heat source side refrigerant discharged from the compressor 11 to flow into the relay unit 20 without passing through the outdoor heat exchanger 13. Switch to.
- the opening of the refrigerant flow control device 86 is fully opened, the first pump 26 is driven, the second pump 27 is stopped, and the first switching valve 61 and the second switching valve 60 of the use-side refrigerant flow switching unit 60 are stopped.
- the switching valve 62 is switched so that the use-side refrigerant circulates between the first intermediate heat exchanger 21 and each indoor unit 30. In this state, the operation of the compressor 11 is started.
- a low-temperature / low-pressure vapor refrigerant is compressed by the compressor 11 and discharged as a high-temperature / high-pressure refrigerant.
- the refrigerant compression process of the compressor 11 is represented by an isentropic line shown from the point [a] to the point [b] in FIG.
- the high-temperature and high-pressure refrigerant discharged from the compressor 11 is conducted through the second extension pipe 42 through the four-way valve 12 and the heat source side refrigerant flow switching unit 50 (check valve 54), and the relay unit 20 1 flows into the intermediate heat exchanger 21.
- the refrigerant flowing into the first intermediate heat exchanger 21 condenses and liquefies while dissipating heat to the use side refrigerant circulating in the first use side refrigerant circuit B1, and becomes a high-pressure liquid refrigerant.
- the refrigerant change at this time is represented by a straight line that is slightly inclined and shown from point [b] to point [c] in FIG.
- the high-pressure liquid refrigerant that has flowed out of the first intermediate heat exchanger 21 is recovered in expansion power by the expansion power recovery unit 81 of the expansion device 80 and depressurized to be in a low-temperature / low-pressure gas-liquid two-phase state.
- the refrigerant change at this time is represented by a slightly inclined vertical line from point [c] to point [d] in FIG.
- the refrigerant in the gas-liquid two-phase state, in which the expansion power is recovered by the expansion power recovery unit 81 and reduced in pressure passes through the second intermediate heat exchanger 22, and a part of the refrigerant flows into the compression unit 82 of the expansion device 80. .
- the refrigerant flowing into the compression unit 82 is recovered by the expansion power recovery unit 81 and is compressed by the power transmitted via the power transmission unit 83.
- the refrigerant change at this time is represented by an isentropic line shown from the point [d] to the point [d '] in FIG.
- the refrigerant compressed by the compression unit 82 is depressurized inside the compression unit 82 to the pressure of the remaining refrigerant passing through the compression unit bypass pipe 85.
- the refrigerant change at this time is represented by an isenthalpy line shown from the point [d ′] to the point [d ′′] in FIG. 20.
- This refrigerant merges with the remaining refrigerant flowing through the compression section bypass pipe 85.
- the change of the refrigerant at this time is represented by a horizontal line shown from the point [d ′′] to the point [e] in FIG. 20.
- the remainder of the refrigerant that has passed through the second intermediate heat exchanger 22 is conducted through the compression unit bypass pipe 85 and flows into the heat source side refrigerant pipe 2 downstream of the compression unit 82 via the refrigerant flow rate control device 86. That is, the refrigerant compressed by the compression unit 82 is mixed with the remaining refrigerant flowing in from the compression unit bypass pipe 85 and decompressed.
- the change of the refrigerant at this time is represented by a horizontal line indicated by points [d] to [e] in FIG.
- the mixed refrigerant passes through the heat source side refrigerant pipe 2 and the first extension pipe 41 and flows into the outdoor unit 10.
- the refrigerant flows into the outdoor heat exchanger 13 through the heat source side refrigerant flow switching unit 50 (check valve 53).
- the outdoor heat exchanger 13 absorbs heat from the outdoor air and becomes a low-temperature / low-pressure vapor refrigerant.
- the refrigerant change at this time is represented by a straight line that is slightly inclined from the point [e] to the point [a] in FIG.
- the low-temperature and low-pressure vapor refrigerant that has flowed out of the outdoor heat exchanger 13 returns to the compressor 11 via the four-way valve 12.
- FIG. 21 is a refrigerant circuit diagram illustrating a refrigerant flow when the air-conditioning apparatus 300 is in the cooling main operation mode.
- FIG. 22 is a ph diagram (diagram illustrating the relationship between the refrigerant pressure and enthalpy) showing the transition of the heat source side refrigerant in the cooling main operation mode.
- a pipe represented by a thick line shows a pipe through which the refrigerant (heat source side refrigerant and utilization side refrigerant) circulates.
- the flow direction of the heat source side refrigerant is indicated by a solid line arrow, and the flow direction of the use side refrigerant is indicated by a broken line arrow.
- the refrigerant states at points [a] to [f] shown in FIG. 22 are refrigerant states at [a] to [f] shown in FIG. 21, respectively.
- the three indoor units 30 that perform the cooling operation are the indoor unit 30a, the indoor unit 30b, and the indoor unit 30c from the left side of the paper, and the one indoor unit 30 that is on the right side of the paper that performs the heating operation is the indoor unit 30d.
- the first switching valve 61 connected to each of the indoor units 30a to 30d is referred to as a first switching valve 61a to a first switching valve 61d
- the second switching valve 62 connected to each of them is a second switching valve.
- 62a to the second switching valve 62d are illustrated.
- coolant of the utilization side refrigerant circuit B at the time of this cooling main operation mode since it is the same as that of Embodiment 1, description is abbreviate
- the outdoor unit 10 uses the four-way valve 12 and the heat source side refrigerant discharged from the compressor 11 to the outdoor heat exchanger 13. Switch to allow inflow.
- the opening of the refrigerant flow control device 86 is fully opened, and the first pump 26 and the second pump 27 are driven.
- the use side refrigerant flow switching unit 60 of the relay unit 20 the first switching valve 61a to the first switching valve 61c and the second switching valve 62a to the second switching valve 62c are connected to the second intermediate heat exchanger 22 and the indoor unit.
- a low-temperature / low-pressure vapor refrigerant is compressed by the compressor 11 and discharged as a high-temperature / high-pressure refrigerant.
- the refrigerant compression process of the compressor 11 is represented by an isentropic line shown from the point [a] to the point [b] in FIG.
- the high-temperature and high-pressure refrigerant discharged from the compressor 11 passes through the four-way valve 12 and flows into the outdoor heat exchanger 13. Then, it is condensed and liquefied while dissipating heat to the outdoor air in the outdoor heat exchanger 13, and becomes a high-pressure gas-liquid two-phase refrigerant.
- the refrigerant change at this time is represented by a straight line that is slightly inclined from the point [b] to the point [c] in FIG.
- the high-pressure gas-liquid two-phase refrigerant that has flowed out of the outdoor heat exchanger 13 is conducted through the second extension pipe 42 via the heat source side refrigerant flow switching unit 50 (check valve 52) and flows into the relay unit 20.
- the high-pressure gas-liquid two-phase refrigerant flowing into the relay unit 20 is first condensed and liquefied while dissipating heat to the use-side refrigerant circulating in the first use-side refrigerant circuit B1 in the first intermediate heat exchanger 21, and the high-pressure liquid refrigerant and become.
- the change in the refrigerant at this time is represented by a straight line that is slightly inclined from the point [c] to the point [d] in FIG.
- the high-pressure liquid refrigerant that has flowed out of the first intermediate heat exchanger 21 is recovered in decompression power by the expansion power recovery unit 81 of the expansion device 80 and depressurized to be in a low-temperature / low-pressure gas-liquid two-phase state.
- the refrigerant change at this time is represented by a slightly inclined vertical line from point [d] to point [e] in FIG.
- the refrigerant in the gas-liquid two-phase state in which the expansion power is recovered and throttled by the expansion power recovery unit 81 flows into the second intermediate heat exchanger 22.
- the refrigerant that has flowed into the second intermediate heat exchanger 22 absorbs heat from the use-side refrigerant circulating in the second use-side refrigerant circuit B2, and becomes a low-temperature and low-pressure vapor refrigerant while cooling the use-side refrigerant.
- the refrigerant change at this time is represented by a slightly inclined straight line that is slightly inclined and shown from point [e] to [f] in FIG.
- the low-temperature and low-pressure vapor refrigerant flowing out of the second intermediate heat exchanger 22 is conducted through the heat source side refrigerant pipe 2, flows into the compression unit 82 of the expansion device 80, is recovered by the expansion power recovery unit 81, and transmits power.
- the refrigerant change at this time is represented by an isentropic line shown from the point [f] to the point [a] in FIG.
- the refrigerant compressed by the compression unit 82 is conducted through the first extension pipe 41 and returns to the compressor 11 through the heat source side refrigerant flow switching unit 50 (check valve 51) and the four-way valve 12.
- FIG. 23 is a refrigerant circuit diagram illustrating a refrigerant flow when the air-conditioning apparatus 300 is in the heating main operation mode.
- FIG. 24 is a ph diagram (diagram illustrating the relationship between the refrigerant pressure and enthalpy) showing the transition of the heat source side refrigerant in the heating main operation mode.
- a pipe indicated by a thick line indicates a pipe through which the refrigerant (heat source side refrigerant and utilization side refrigerant) circulates.
- the flow direction of the heat source side refrigerant is indicated by a solid line arrow, and the flow direction of the use side refrigerant is indicated by a broken line arrow.
- the refrigerant states at points [a] to [e] shown in FIG. 24 are the refrigerant states at [a] to [e] shown in FIG. 23, respectively.
- the three indoor units 30 that perform the heating operation are the indoor unit 30a, the indoor unit 30b, and the indoor unit 30c from the left side of the paper, and the one indoor unit 30 that is on the right side of the paper that performs the cooling operation is the indoor unit 30d.
- the first switching valve 61 connected to each of the indoor units 30a to 30d is referred to as a first switching valve 61a to a first switching valve 61d
- the second switching valve 62 connected to each of them is a second switching valve.
- 62a to the second switching valve 62d are illustrated.
- coolant of the utilization side refrigerant circuit B at the time of this cooling main operation mode since it is the same as that of Embodiment 1, description is abbreviate
- the outdoor unit 10 uses the four-way valve 12 and the heat source side refrigerant discharged from the compressor 11 to the outdoor heat exchanger 13. It switches so that it may flow into the relay part 20 without going through.
- the opening of the refrigerant flow control device 86 is fully opened, and the first pump 26 and the second pump 27 are driven.
- the first switching valve 61a to the first switching valve 61c and the second switching valve 62a to the second switching valve 62c are connected to the first intermediate heat exchanger 21 and the indoor unit.
- a low-temperature / low-pressure vapor refrigerant is compressed by the compressor 11 and discharged as a high-temperature / high-pressure refrigerant.
- the refrigerant compression process of the compressor 11 is represented by an isentropic line shown from the point [a] to the point [b] in FIG.
- the high-temperature and high-pressure refrigerant discharged from the compressor 11 is conducted through the second extension pipe 42 via the four-way valve 12 and the heat source side refrigerant flow switching unit 50 (check valve 52), and the relay unit 20 1 flows into the intermediate heat exchanger 21.
- the refrigerant flowing into the first intermediate heat exchanger 21 condenses and liquefies while dissipating heat to the use side refrigerant circulating in the first use side refrigerant circuit B1, and becomes a high-pressure liquid refrigerant.
- the refrigerant change at this time is represented by a straight line that is slightly inclined and shown from point [b] to point [c] in FIG.
- the high-pressure liquid refrigerant that has flowed out of the first intermediate heat exchanger 21 is recovered in expansion power by the expansion power recovery unit 81 of the expansion device 80 and depressurized to be in a low-temperature / low-pressure gas-liquid two-phase state.
- the refrigerant change at this time is represented by a slightly inclined vertical line from point [c] to point [d] in FIG.
- the refrigerant in the gas-liquid two-phase state in which the expansion power is recovered and throttled by the expansion power recovery unit 81 flows into the second intermediate heat exchanger 22.
- the refrigerant flowing into the second intermediate heat exchanger 22 absorbs heat from the use-side refrigerant circulating in the second use-side refrigerant circuit B2, thereby cooling the use-side refrigerant while maintaining a low-temperature / low-pressure gas-liquid two-phase state. Becomes a refrigerant.
- the refrigerant change at this time is represented by a slightly inclined straight line that is slightly inclined from [d] to [e] in FIG.
- the refrigerant change at this time is represented by an isentropic line shown from the point [e] to the point [e ′] and an isentropic line shown from the point [e ′] to the point [e ′′] in FIG.
- the remainder of the refrigerant heated by the second intermediate heat exchanger 22 is conducted through the compression unit bypass pipe 85 and flows into the heat source side refrigerant pipe 2 downstream of the compression unit 82 via the refrigerant flow rate control device 86. That is, the refrigerant compressed by the compression unit 82 is mixed with the remaining refrigerant flowing in from the compression unit bypass pipe 85 and decompressed.
- the mixed refrigerant passes through the heat source side refrigerant pipe 2 and the first extension pipe 41 and flows into the outdoor unit 10.
- the refrigerant flows into the outdoor heat exchanger 13 through the heat source side refrigerant flow switching unit 50 (check valve 51).
- the outdoor heat exchanger 13 absorbs heat from the outdoor air and becomes a low-temperature / low-pressure vapor refrigerant.
- the refrigerant change at this time is represented by a straight line that is slightly inclined from the point [f] to the point [a] in FIG.
- the low-temperature and low-pressure vapor refrigerant that has flowed out of the outdoor heat exchanger 13 returns to the compressor 11 via the four-way valve 12.
- air conditioning apparatus 300 configured as described above, in addition to the effects of air conditioning apparatus 100 according to Embodiment 1, power generated when the heat source side refrigerant expands in the cooling only operation mode and the cooling main operation mode. Can be used for compression (pressure increase) of the heat source side refrigerant, and the refrigeration cycle efficiency is improved. Moreover, if the structure of the air conditioning apparatus 300 is applied to the air conditioning apparatus 200 according to Embodiment 2, in addition to the effects of the air conditioning apparatus 200, the refrigeration cycle efficiency can be further improved.
- Embodiment 3 although the case where the compression part 82 of the expansion apparatus 80 is provided in the exit side of the 2nd intermediate heat exchanger 22 is shown as an example, in 1st heating operation mode and heating main operation mode, it is 1st.
- the compressor 82 may be provided on the inlet side of the first intermediate heat exchanger 21 in order to compress the refrigerant flowing into the intermediate heat exchanger 21.
- the refrigerant flowing into the first intermediate heat exchanger 21 can be compressed in the heating only operation mode and the heating main operation mode, and the refrigeration cycle efficiency in the heating only operation mode and the heating main operation mode can be increased. Improvements can be made.
- FIG. FIG. 25 is a circuit diagram showing a circuit configuration of an air-conditioning apparatus 400 according to Embodiment 4 of the present invention. Based on FIG. 25, the circuit configuration of the air-conditioning apparatus 400 will be described.
- This air conditioner 400 is installed in a building, condominium, etc., like the air conditioner 100, the air conditioner 200, and the air conditioner 300, and refrigeration cycle (heat source side) that circulates refrigerant (heat source side refrigerant and use side refrigerant).
- the cooling load and the heating load can be supplied simultaneously by using the refrigerant circuit and the use side refrigerant circuit).
- differences from the first to third embodiments will be mainly described. The same parts as those in the first to third embodiments are denoted by the same reference numerals, and the description thereof is omitted. It shall be.
- the air conditioner 400 according to the fourth embodiment is based on the configuration of the air conditioner 100 according to the first embodiment, and the first intermediate heat exchanger 21 in the heat source side refrigerant circuit A.
- the second refrigerant flow control device 25b is provided upstream of the second intermediate heat exchanger 22, and the relay unit 20c provided with the third refrigerant flow control device 25c downstream of the second intermediate heat exchanger 22 is provided.
- the relay section 20c has a room in which either one or both of the use side refrigerant exchanged by the first intermediate heat exchanger 21 and the use side refrigerant exchanged by the second intermediate heat exchanger 22 are selected.
- a use-side refrigerant flow switching unit 60 a that supplies the unit 30 is provided.
- the second refrigerant flow control device 25b, the first intermediate heat exchanger 21, the refrigerant flow control device 25 (hereinafter referred to as the first refrigerant flow control device 25a for convenience), the second The intermediate heat exchanger 22 and the third refrigerant flow control device 25c are sequentially connected in series by the heat source side refrigerant pipe 2 and provided in the relay portion 20c. Similar to the first refrigerant flow control device 25a, the second refrigerant flow control device 25b and the third refrigerant flow control device 25c function as a pressure reducing valve or an expansion valve, and decompress the heat source side refrigerant to expand it.
- the second refrigerant flow control device 25b and the third refrigerant flow control device 25c may be configured by a device whose opening degree can be variably controlled, for example, an electronic expansion valve.
- the use-side refrigerant flow switching unit 60a includes a plurality of water flow switching valves (fifth switching valve 66, sixth switching valve 67, seventh switching valve 68, and eighth switching valve 69).
- the number of the fifth switching valve 66, the sixth switching valve 67, the seventh switching valve 68, and the eighth switching valve 69 corresponds to the number of indoor units 30 connected to the relay unit 20c (here, four each). Is provided.
- the use side refrigerant pipe 3 is branched (here, four branches) in accordance with the number of indoor units 30 connected to the relay unit 20c by the use side refrigerant flow switching unit 60a.
- the path switching unit 60 a and the third extension pipe 43 and the fourth extension pipe 44 connected to each of the indoor units 30 are connected. That is, the fifth switching valve 66, the sixth switching valve 67, the seventh switching valve 68, and the eighth switching valve 69 are provided in each of the branched usage-side refrigerant pipes 3.
- the fifth switching valve 66 is provided in the use side refrigerant pipe 3 a between the first pump 26 and each indoor heat exchanger 31, that is, in the use side refrigerant pipe 3 a on the inflow side of the indoor heat exchanger 31. .
- the fifth switching valve 66 is constituted by a two-way valve, and is connected to the first pump 26 via the use side refrigerant pipe 3a and is connected to the third extension pipe 43 via the use side refrigerant pipe 3a. It has become so.
- the sixth switching valve 67 is provided in the use side refrigerant pipe 3b between the second pump 27 and each indoor heat exchanger 31, that is, in the use side refrigerant pipe 3b on the inflow side of the indoor heat exchanger 31. .
- the sixth switching valve 67 is a two-way valve, and is connected to the second pump 27 via the use side refrigerant pipe 3b and is connected to the third extension pipe 43 via the use side refrigerant pipe 3b. It has become so.
- the seventh switching valve 68 is provided in the use side refrigerant pipe 3 a between the indoor heat exchanger 31 and the first intermediate heat exchanger 21, that is, in the use side refrigerant pipe 3 a on the outflow side of the indoor heat exchanger 31. ing.
- the seventh switching valve 68 is constituted by a two-way valve, and is connected to the fourth extension pipe 44 through the use side refrigerant pipe 3a and connected to the first pump 26 through the use side refrigerant pipe 3a. It has come to be.
- the eighth switching valve 69 is provided in the use side refrigerant pipe 3 b between the indoor heat exchanger 31 and the second intermediate heat exchanger 22, that is, in the use side refrigerant pipe 3 b on the outflow side of the indoor heat exchanger 31.
- the eighth switching valve 69 is constituted by a two-way valve, and is connected to the fourth extension pipe 44 via the use side refrigerant pipe 3b and to the second pump 27 via the use side refrigerant pipe 3b. It has come to be.
- the air conditioner 400 can perform a cooling operation or a heating operation in the indoor unit 30 based on an instruction from each indoor unit 30. That is, the air conditioner 400 is similar to the air conditioner 100, the air conditioner 200, and the air conditioner 300 in four operation modes (cooling operation mode, heating operation mode, cooling main operation mode, and heating main operation mode). ) Can be executed.
- the cooling only operation mode, the heating only operation mode, the cooling main operation mode, and the heating main operation mode executed by the air conditioning apparatus 300 will be described together with the flow of the refrigerant.
- FIG. 26 is a ph diagram (diagram illustrating the relationship between the refrigerant pressure and the enthalpy) showing the change of the heat source side refrigerant when the air-conditioning apparatus 400 is in the cooling only operation mode.
- coolant a heat-source side refrigerant
- the outdoor unit 10 switches the four-way valve 12 so that the heat source side refrigerant discharged from the compressor 11 flows into the outdoor heat exchanger 13.
- the relay unit 20c the first refrigerant flow control device 25a and the third refrigerant flow control device 25c are fully opened, the second refrigerant flow control device 25b is narrowed, and the first pump 26 and the second pump 27 are turned off.
- the fifth switching valve 66, the sixth switching valve 67, the seventh switching valve 68, and the eighth switching valve 69 of the usage-side refrigerant flow switching unit 60a are driven, and the first intermediate heat exchanger 21 and each indoor unit 30 are connected. And between the second intermediate heat exchanger 22 and each indoor unit 30 are fully opened so that the use-side refrigerant circulates. In this state, the operation of the compressor 11 is started.
- a low-temperature / low-pressure vapor refrigerant is compressed by the compressor 11 and discharged as a high-temperature / high-pressure refrigerant.
- This refrigerant compression process of the compressor 11 is represented by an isentropic line shown from the point [a] to the point [b] in FIG. 26, assuming that heat does not enter and exit from the surroundings.
- the high-temperature and high-pressure refrigerant discharged from the compressor 11 passes through the four-way valve 12 and flows into the outdoor heat exchanger 13.
- the outdoor heat exchanger 13 condenses and liquefies while radiating heat to the outdoor air, and becomes a high-pressure liquid refrigerant.
- the change of the refrigerant in the outdoor heat exchanger 13 is performed under a substantially constant pressure.
- the refrigerant change at this time is represented by a slightly inclined straight line that is slightly inclined from the point [b] to the point [c] in FIG.
- the high-pressure liquid refrigerant that has flowed out of the outdoor heat exchanger 13 is conducted through the second extension pipe 42 via the heat source side refrigerant flow switching unit 50 (check valve 52) and flows into the relay unit 20c.
- the high-pressure liquid refrigerant that has flowed into the relay unit 20c is throttled and expanded (depressurized) by the second refrigerant flow control device 25b, and enters a low-temperature / low-pressure gas-liquid two-phase state.
- the change of the refrigerant in the second refrigerant flow control device 25b is performed under a constant enthalpy.
- the refrigerant change at this time is represented by the vertical line shown from the point [c] to the point [d] in FIG.
- the gas-liquid two-phase refrigerant throttled by the second refrigerant flow control device 25b flows into the first intermediate heat exchanger 21.
- the refrigerant that has flowed into the first intermediate heat exchanger 21 absorbs heat from the use-side refrigerant circulating in the first use-side refrigerant circuit B1, and becomes a refrigerant in a gas-liquid two-phase state while cooling the use-side refrigerant.
- the change of the refrigerant in the first intermediate heat exchanger 21 is performed under a substantially constant pressure.
- the refrigerant change at this time is represented by a slightly inclined straight line that is slightly inclined from the point [d] to [e] in FIG.
- the heat-source-side refrigerant that has flowed out of the first intermediate heat exchanger 21 passes through the first flow control device 25a, flows into the second intermediate heat exchanger 22, and absorbs heat from the use-side refrigerant that circulates in the second use-side refrigerant circuit B2. By doing so, it becomes a low-temperature and low-pressure vapor refrigerant while cooling the use-side refrigerant.
- the change of the refrigerant in the second intermediate heat exchanger 22 is performed under a substantially constant pressure.
- the refrigerant change at this time is represented by a slightly inclined straight line that is slightly inclined from the point [e] to [a] in FIG. 25 in consideration of the pressure loss of the second intermediate heat exchanger 22.
- the low-temperature and low-pressure vapor refrigerant flowing out of the second intermediate heat exchanger 22 is conducted through the first extension pipe 41 and compressed through the heat source side refrigerant flow switching unit 50 (check valve 51) and the four-way valve 12. Return to machine 11.
- both the first pump 26 and the second pump 27 are driven.
- the use-side refrigerant cooled by the heat source-side refrigerant in the first intermediate heat exchanger 21 and the second intermediate heat exchanger 22 flows into the use-side refrigerant flow switching unit 60a by the first pump 26 and the second pump 27.
- the usage-side refrigerant that has flowed into the usage-side refrigerant flow switching unit 60a passes through the fifth switching valve 66 and the sixth switching valve 67, is conducted through the usage-side refrigerant piping 3 and the third extension piping 43, and the indoor heat exchanger 31. Flows into each of the.
- the indoor heat exchanger 31 absorbs heat from the room air and cools the air-conditioning target area such as the room where the indoor unit 30 is installed. Thereafter, the usage-side refrigerant that has flowed out of the indoor heat exchanger 31 is conducted through the fourth extension pipe 44, passes through the seventh switching valve 68 and the eighth switching valve 69, and merges at the usage-side refrigerant flow switching unit 60a. After being branched, it flows again into the first intermediate heat exchanger 21 and the second intermediate heat exchanger 22.
- FIG. 27 is a ph diagram (diagram illustrating the relationship between refrigerant pressure and enthalpy) showing the change of the heat source side refrigerant when the air-conditioning apparatus 400 is in the heating only operation mode.
- coolant a heat-source side refrigerant
- the four-way valve 12 causes the heat source side refrigerant discharged from the compressor 11 to flow into the relay unit 20 c without passing through the outdoor heat exchanger 13. Switch to.
- the relay unit 20c the first refrigerant flow control device 25a and the second refrigerant flow control device 25b are fully opened, the opening degree of the third refrigerant flow control device 25c is reduced, and the first pump 26 and the second pump 27 are driven,
- the fifth switching valve 66, the sixth switching valve 67, the seventh switching valve 68, and the eighth switching valve 69 of the usage-side refrigerant flow switching unit 60a are connected between the first intermediate heat exchanger 21 and each indoor unit 30, and
- the use side refrigerant is fully opened between the second intermediate heat exchanger 22 and each indoor unit 30 so as to circulate. In this state, the operation of the compressor 11 is started.
- a low-temperature / low-pressure vapor refrigerant is compressed by the compressor 11 and discharged as a high-temperature / high-pressure refrigerant.
- the refrigerant compression process of the compressor 11 is represented by an isentropic line shown from the point [a] to the point [b] in FIG.
- the high-temperature and high-pressure refrigerant discharged from the compressor 11 is conducted through the second extension pipe 42 via the four-way valve 12 and the heat source side refrigerant flow switching unit 50 (check valve 54), and the relay unit 20c
- the refrigerant flows into the first intermediate heat exchanger 21 via the two refrigerant flow control devices 25b.
- the refrigerant flowing into the first intermediate heat exchanger 21 is condensed and liquefied while dissipating heat to the use side refrigerant circulating in the first use side refrigerant circuit B1, and becomes a high-pressure gas-liquid two-phase refrigerant.
- the refrigerant change at this time is represented by a slightly inclined straight line that is slightly inclined from the point [b] to the point [c] in FIG.
- the high-pressure refrigerant that has flowed out of the first intermediate heat exchanger 21 flows into the second intermediate heat exchanger 22 via the first refrigerant flow control device 25a.
- the refrigerant flowing into the second intermediate heat exchanger 22 is further condensed while dissipating heat to the utilization side refrigerant circulating in the second utilization side refrigerant circuit B2, and becomes a high-pressure liquid refrigerant.
- the refrigerant change at this time is represented by a slightly inclined straight line that is slightly inclined from point [c] to point [d] in FIG.
- the refrigerant that has flowed out of the second intermediate heat exchanger 22 is throttled and expanded (depressurized) by the third refrigerant flow control device 25c, and enters a low-temperature and low-pressure gas-liquid two-phase state.
- the refrigerant change at this time is represented by the vertical line shown from the point [d] to the point [e] in FIG.
- the refrigerant in the gas-liquid two-phase state throttled by the third refrigerant flow control device 25c is conducted through the heat source side refrigerant pipe 2 and the first extension pipe 41 and flows into the outdoor unit 10.
- the refrigerant flows into the outdoor heat exchanger 13 through the heat source side refrigerant flow switching unit 50 (check valve 53).
- the outdoor heat exchanger 13 absorbs heat from the outdoor air and becomes a low-temperature / low-pressure vapor refrigerant.
- the refrigerant change at this time is represented by a straight line that is slightly inclined and shown from point [e] to point [a] in FIG.
- the low-temperature and low-pressure vapor refrigerant that has flowed out of the outdoor heat exchanger 13 returns to the compressor 11 via the four-way valve 12.
- both the first pump 26 and the second pump 27 are driven.
- the use side refrigerant heated by the heat source side refrigerant in the first intermediate heat exchanger 21 and the second intermediate heat exchanger 22 flows into the use side refrigerant flow switching unit 60a by the first pump 26 and the second pump 27.
- the usage-side refrigerant that has flowed into the usage-side refrigerant flow switching unit 60a passes through the fifth switching valve 66 and the sixth switching valve 67, is conducted through the usage-side refrigerant piping 3 and the third extension piping 43, and the indoor heat exchanger 31. Flows into each of the.
- the indoor heat exchanger 31 radiates heat to the room air and heats the air-conditioning target area such as the room where the indoor unit 30 is installed. Thereafter, the usage-side refrigerant that has flowed out of the indoor heat exchanger 31 is conducted through the fourth extension pipe 44, passes through the seventh switching valve 68 and the eighth switching valve 69, and merges at the usage-side refrigerant flow switching unit 60a. After being branched, it flows again into the first intermediate heat exchanger 21 and the second intermediate heat exchanger 22.
- the cooling main operation mode is a simultaneous cooling / heating operation mode in which the cooling load is larger, for example, in which three indoor units 30 perform cooling operation and one indoor unit 30 performs heating operation. is there.
- the three indoor units 30 that perform the cooling operation are the indoor unit 30a, the indoor unit 30b, and the indoor unit 30c from the left side of the paper, and the one indoor unit 30 that is on the right side of the paper that performs the heating operation is the indoor unit. It is shown as 30d.
- the fifth switching valve 66 connected to each of them is referred to as a fifth switching valve 66a to a fifth switching valve 66d
- the sixth switching valve 67 connected to each of them is a sixth switching valve.
- the seventh switching valve 68 connected to each of them is referred to as a seventh switching valve 68a to seventh switching valve 68d
- the eighth switching valve 69 connected to each of them is an eighth switching valve 69a to eighth switching valve 68d. It is shown as a switching valve 69d.
- the outdoor unit 10 uses the four-way valve 12 and the heat source side refrigerant discharged from the compressor 11 to the outdoor heat exchanger 13. Switch to allow inflow.
- the opening degree of the first refrigerant flow control device 25a is reduced, the second refrigerant flow control device 25b and the third refrigerant flow control device 25c are fully opened, and the first pump 26 and the second pump 27 are driven.
- the fifth switching valve 66a to the fifth switching valve 61c and the seventh switching valve 68a to the seventh switching valve 68c are closed, and the sixth switching valve 67a to the sixth switching valve are closed.
- the switching valve 67c and the eighth switching valve 69a to the eighth switching valve 69c are opened to switch the utilization side refrigerant between the second intermediate heat exchanger 22 and the indoor unit 30a to the indoor unit 30c.
- the switching valve 66d and the seventh switching valve 68d are opened, the sixth switching valve 67d and the eighth switching valve 69d are closed, and the use-side refrigerant circulates between the first intermediate heat exchanger 21 and the indoor unit 30d. Switch. In this state, the operation of the compressor 11 is started.
- the flow of the heat source side refrigerant and the use side refrigerant is the same as that in the first embodiment, and the description thereof is omitted.
- the heating main operation mode is a cooling and heating simultaneous operation mode in the case where the heating load is larger, for example, in which three indoor units 30 perform a heating operation and one indoor unit 30 performs a cooling operation. is there.
- the three indoor units 30 that perform the heating operation are the indoor unit 30a, the indoor unit 30b, and the indoor unit 30c from the left side of the sheet, and the one indoor unit 30 that performs the cooling operation on the right side of the sheet is the indoor unit. It is shown as 30d.
- the fifth switching valve 66 connected to each of them is referred to as a fifth switching valve 66a to a fifth switching valve 66d
- the sixth switching valve 67 connected to each of them is a sixth switching valve.
- the seventh switching valve 68 connected to each of them is referred to as a seventh switching valve 68a to seventh switching valve 68d
- the eighth switching valve 69 connected to each of them is an eighth switching valve 69a to eighth switching valve 68d. It is shown as a switching valve 69d.
- the outdoor unit 10 uses the four-way valve 12 and the heat source side refrigerant discharged from the compressor 11 to the outdoor heat exchanger 13. It switches so that it may flow into relay part 20c, without going through.
- the opening degree of the first refrigerant flow control device 25a is reduced, the second refrigerant flow control device 25b and the third refrigerant flow control device 25c are fully opened, and the first pump 26 and the second pump 27 are driven.
- the fifth switching valve 66a to the fifth switching valve 61c and the seventh switching valve 68a to the seventh switching valve 68c are opened, and the sixth switching valve 67a to the sixth switching valve 68c.
- the switching valve 67c and the eighth switching valve 69a to the eighth switching valve 69c are closed to switch the use side refrigerant between the first intermediate heat exchanger 21 and the indoor unit 30a to the indoor unit 30c.
- the switching valve 66d and the seventh switching valve 68d are closed, the sixth switching valve 67d and the eighth switching valve 69d are opened, and switching is performed so that the use-side refrigerant circulates between the second intermediate heat exchanger 22 and the indoor unit 30d. .
- the operation of the compressor 11 is started.
- the flow of the heat source side refrigerant and the use side refrigerant is the same as that in the first embodiment, and the description thereof is omitted.
- the first intermediate heat exchanger 21 is provided in each of the cooling only operation mode and the heating only operation mode.
- the second intermediate heat exchanger 22 and the first pump 26 and the second pump 27 can be used.
- the first intermediate heat exchanger 21, the second intermediate heat exchanger 22, the first pump 26 and the second pump 27 can be used. Can be reduced in size. That is, it can contribute to the compactness of the relay part 20c.
- FIG. FIG. 28 is a circuit diagram showing a circuit configuration of an air-conditioning apparatus 500 according to Embodiment 5 of the present invention. Based on FIG. 28, the configuration of the air conditioner 500 and the control operation of the use side refrigerant circuit B will be described.
- This air conditioner 500 is installed in a building, a condominium, etc. similarly to the air conditioner 100, the air conditioner 200, the air conditioner 300, and the air conditioner 400, and circulates the refrigerant (the heat source side refrigerant and the use side refrigerant).
- the refrigeration cycle heat source side refrigerant circuit and utilization side refrigerant circuit
- a cooling load and a heating load can be simultaneously supplied.
- differences from the first to fourth embodiments will be mainly described, and the same parts as those in the first to fourth embodiments will be denoted by the same reference numerals and the description thereof will be omitted. It shall be.
- the air conditioner 500 according to the fifth embodiment is based on the configuration of the air conditioner 100 according to the first embodiment, and controls the flow rate of the use side refrigerant circulating in the use side refrigerant circuit B.
- coolant flow control part 95 is provided.
- the first usage-side refrigerant flow rate control unit 90 is provided between the first intermediate heat exchanger 21 and the second intermediate heat exchanger 22 and the usage-side refrigerant flow switching unit 60, and particularly the first intermediate heat exchange.
- the flow rate of the use-side refrigerant flowing into the condenser 22 and the second intermediate heat exchanger 22 is controlled.
- the second usage-side refrigerant flow rate control unit 95 is provided between the usage-side refrigerant flow switching unit 60 and the indoor unit 30, and particularly controls the flow rate of the usage-side refrigerant supplied to the indoor unit 30.
- the first usage-side refrigerant flow control unit 90 includes two first temperature sensors 91 (first temperature sensor 91a and first temperature sensor 91b) and two second temperature sensors 92 (second temperature sensor 92a and second temperature). Sensor 92b) and two inverters 93 (inverter 93a and inverter 93b).
- the second usage-side refrigerant flow rate control unit 95 includes the indoor inflow side temperature sensors 96 (the indoor inflow side temperature sensor 96a to the indoor inflow side temperature sensor 96d) for the number of indoor units 30 and the indoor outflow for the number of indoor units 30.
- a side temperature sensor 97 (indoor outflow temperature sensor 97a to indoor outflow temperature sensor 97d) and flow control valves 98 (flow control valves 98a to 98d) for the number of indoor units 30 are configured.
- the second usage-side refrigerant flow rate control unit 95 is also controlled by the inverter 93.
- the 1st temperature sensor 91a is provided in the 1st utilization side refrigerant
- the 1st temperature sensor 91b is provided in the 2nd utilization side refrigerant
- the temperature information detected by the first temperature sensor 91 is sent to the inverter 93.
- the first temperature sensor 91 only needs to be able to detect the temperature of the usage-side refrigerant that conducts through the usage-side refrigerant pipe 3, and may be constituted by, for example, a thermometer or a thermistor.
- the 2nd temperature sensor 92a is provided in the 1st utilization side refrigerant
- electrically_connect is detected.
- the 2nd temperature sensor 92b is provided in the 2nd utilization side refrigerant
- electrically_connect is detected.
- the temperature information detected by the second temperature sensor 92 is sent to the inverter 93.
- the second temperature sensor 92 may be any sensor that can detect the temperature of the usage-side refrigerant that is conducted through the usage-side refrigerant pipe 3, and may be composed of, for example, a thermometer or a thermistor.
- the inverter 93a is connected to the first pump 26, adjusts the driving of the first pump 26, and controls the flow rate of the usage-side refrigerant circulating in the first usage-side refrigerant circuit B1.
- the inverter 93b is connected to the second pump 27, adjusts the driving of the second pump 27, and controls the flow rate of the usage-side refrigerant circulating in the second usage-side refrigerant circuit B2. That is, the inverter 93 adjusts the driving of the first pump 26 and the second pump 27 based on the temperature information from the first temperature sensor 91 and the second temperature sensor 92 and supplies the usage-side refrigerant that flows into the indoor unit 30. The flow rate is controlled.
- the indoor inflow side temperature sensor 96a to the indoor inflow side temperature sensor 96d are provided in the use side refrigerant pipe 3 between the first switching valve 61 and the flow rate control valve 98a to the flow rate control valve 98d, and are used to flow into the indoor unit 30.
- the temperature of the side refrigerant is detected.
- the temperature information detected by the indoor inflow side temperature sensor 96a to the indoor inflow side temperature sensor 96d is sent to a control device (not shown).
- the indoor inflow side temperature sensor 96a to the indoor inflow side temperature sensor 96d only need to be able to detect the temperature of the use side refrigerant that is conducted through the use side refrigerant pipe 3, and may be constituted by, for example, a thermometer or a thermistor. .
- the indoor outlet side temperature sensor 97a to the indoor outlet side temperature sensor 97d are provided in the usage side refrigerant pipe 3 between the indoor heat exchanger 31 and the second switching valve 62, and the temperature of the usage side refrigerant that has flowed out of the indoor unit 30. Is detected.
- the temperature information detected by the indoor outflow side temperature sensor 97a to the indoor outflow side temperature sensor 97d is sent to a control device (not shown).
- the indoor outlet side temperature sensor 97a to the indoor outlet side temperature sensor 97d may be any sensor that can detect the temperature of the usage-side refrigerant that is conducted through the usage-side refrigerant pipe 3, and may be composed of, for example, a thermometer or a thermistor. .
- the flow rate control valve 98a to the flow rate control valve 98d are provided in the use-side refrigerant pipe 3 between the indoor inflow side temperature sensor 96a to the indoor inflow side temperature sensor 96d and the indoor heat exchanger 31, and open and close to a control device (not shown). Is controlled to adjust the flow rate of the use-side refrigerant flowing into the indoor heat exchanger 31.
- the control device may be mounted on the inverter 93a and the inverter 93b, or may be provided separately from the inverter 93a and the inverter 93b.
- the inverter 93a and the inverter 93b controlled the drive of the 1st pump 26 and the 2nd pump 27 was demonstrated to the example, the inverter 93a and the inverter 93b are also controlled by a control apparatus, and the 1st pump 26 is controlled. In addition, the driving of the second pump 27 may be adjusted.
- the inverter 93a and the inverter 93b control the first pump 26 and the second pump 27 based on information from each temperature sensor, and adjust the flow rate of the usage-side refrigerant circulating in the usage-side refrigerant circuit B.
- the inverter 93 may control the utilization side refrigerant circuit B, for example, adjusting the air volume of the air blower provided in the indoor unit 30.
- a bypass pipe that bypasses the first pump 26 and the second pump 27 and a valve device that controls the flow rate of the use-side refrigerant that conducts the bypass pipe may be provided to control the use-side refrigerant circuit B. Furthermore, you may provide a some pump and may control the utilization side refrigerant circuit B with the number of the pumps to drive
- the inverter 93 starts a control operation according to the instruction. First, based on the temperature information detected by the indoor inflow side temperature sensor 96 and the indoor outflow side temperature sensor 97, the inverter 93 grasps the atmospheric conditions in the room where the instructed indoor unit 30 is installed. And the inverter 93 determines the flow volume of the utilization side refrigerant
- the inverter 93 monitors the temperature information detected by the indoor inflow side temperature sensor 96 and the indoor outflow side temperature sensor 97, and based on the temperature information detected by the first temperature sensor 91 and the second temperature sensor 92, The operations of the first pump 26 and the second pump 27 are adjusted as appropriate.
- the inverter 93 specifies the indoor unit 30 that performs the cooling operation, and controls the driving of the first pump 26 and the second pump 27 according to the number of operating indoor units 30.
- the use side refrigerant circuit B in the above-described cooling only operation mode will be described.
- the first pump 26 is stopped and the second pump 27 is driven to adjust the circulation amount of the utilization side refrigerant in the second utilization side refrigerant circuit B2 (Embodiment 1). 2 shown in FIG. 2 and FIG. 17 shown in Embodiment 3).
- the inverter 93b determines that it is necessary to further supply cooling air into the room or the like.
- the driving of the second pump 27 is controlled so as to increase the circulation amount of the use-side refrigerant in the refrigerant circuit B2.
- the inverter 93b determines that it is not necessary to further supply cooling air into the room, and the like in the second usage side refrigerant circuit B2.
- the driving of the second pump 27 is controlled so as to reduce the circulation amount of the usage-side refrigerant.
- the inverter 93b determines that it is necessary to further supply cooling air into the room, and the like in the second usage side refrigerant circuit B2.
- the driving of the second pump 27 is controlled so as to increase the circulation amount of the usage-side refrigerant.
- the inverter 93b determines that it is not necessary to further supply cooling air into the room, and the like in the second usage side refrigerant circuit B2.
- the driving of the second pump 27 is controlled so as to reduce the circulation amount of the usage-side refrigerant.
- the inverter 93 specifies the indoor unit 30 that performs the heating operation, and controls the driving of the first pump 26 and the second pump 27 according to the number of operating indoor units 30.
- the use side refrigerant circuit B in the heating only operation mode described above will be described.
- the first pump 26 is driven, the second pump 27 is stopped, and the circulation amount of the utilization side refrigerant in the first utilization side refrigerant circuit B1 is adjusted (in the first embodiment).
- the inverter 93a determines that it is not necessary to further supply the heating air into the room, and the first usage side The drive of the 1st pump 26 is controlled so that the circulation amount of the utilization side refrigerant
- the inverter 93a determines that it is necessary to further supply heating air into the room or the like, and in the first usage side refrigerant circuit B1 The drive of the first pump 26 is controlled so as to increase the circulation amount of the usage-side refrigerant.
- the inverter 93a determines that it is not necessary to further supply the heating air into the room or the like, and in the first usage side refrigerant circuit B1
- the drive of the first pump 26 is controlled so as to reduce the circulation amount of the usage-side refrigerant.
- the inverter 93a determines that it is necessary to further supply heating air into the room and the like in the first usage side refrigerant circuit B1.
- the driving of the second pump 27 is controlled so as to reduce the circulation amount of the usage-side refrigerant.
- the inverter 93 specifies the indoor unit 30 that performs the cooling operation or the heating operation, and controls the driving of the first pump 26 and the second pump 27 according to the number of operating indoor units 30.
- the use-side refrigerant is circulated in the first intermediate heat exchanger 21 (when at least one indoor unit 30 is performing the heating operation), and used for the second intermediate heat exchanger 22.
- the side refrigerant is circulated (a case where at least one indoor unit 30 is performing the cooling operation) will be described.
- the inverter 93a determines that the temperature information from the second temperature sensor 92a is higher than the predetermined temperature T5
- the heating air is further increased. Therefore, the first pump 26 is controlled so as to reduce the circulation amount of the use-side refrigerant in the first use-side refrigerant circuit B1.
- the inverter 93 determines that the temperature information from the second temperature sensor 92a is lower than the predetermined temperature T5
- the inverter 93 determines that it is necessary to further supply heating air into the room, and the first usage side refrigerant circuit.
- the first pump 26 is controlled so as to increase the circulation amount of the use-side refrigerant in B1.
- the second pump 27 is controlled so as to increase the circulation amount of the usage-side refrigerant in the second usage-side refrigerant circuit B2.
- the inverter 93 determines that the temperature information from the second temperature sensor 92b is lower than the predetermined temperature T6, the inverter 93 determines that it is not necessary to further supply cooling air into the room, and the second usage side refrigerant circuit B2
- the second pump 27 is controlled so as to reduce the circulation amount of the use-side refrigerant at.
- the inverter 93 can control the use-side refrigerant circuit B and can also control the heat source-side refrigerant circuit A.
- the inverter 93 switches the driving frequency of the compressor 11 and the four-way valve 12 based on the temperature information from the first temperature sensor 91 and the second temperature sensor 92, and the refrigerant flow control device 25 (or the refrigerant flow control device 86).
- the flow rate of the heat source side refrigerant circulating through the heat source side refrigerant circuit A is adjusted by controlling the opening degree and the opening degree of a blower (not shown) that supplies air to the outdoor heat exchanger 13.
- the inverter 93 starts a control operation in accordance with the instruction.
- the inverter 93 controls switching of the four-way valve 12 and determines the flow path of the heat source side refrigerant.
- the inverter 93 determines the drive frequency of the compressor 11, the rotation of the blower, and the opening degree of the refrigerant flow control device 25, and starts the operation according to the instruction.
- the inverter 93 controls the first usage side refrigerant flow rate control unit 90 and the second usage side refrigerant flow rate control unit 95 to adjust the flow rate of the usage side refrigerant circulating in the usage side refrigerant circuit B, and at the heat source side.
- the refrigerant circuit A By controlling the refrigerant circuit A, the flow rate of the heat-source-side refrigerant that flows into the first intermediate heat exchanger 21 and the second intermediate heat exchanger 22 is adjusted.
- the flow rate of the use-side refrigerant can be controlled according to the heat load of the indoor unit 30, so that the power of the first pump 26 and the second pump 27 can be reduced.
- the refrigerant flow control device for example, the throttle device in Patent Document 2
- noise and vibration generated from the indoor unit 30 can be reduced, and user convenience can be improved.
- the temperature of the refrigerant flowing into the indoor heat exchanger and the temperature of the refrigerant flowing out of the outdoor heat exchanger are detected, and the refrigerant flow control device is controlled based on these temperatures.
- the room temperature was adjusted.
- the use-side refrigerant circuit B can be controlled based on the temperature detected by each temperature sensor provided in the relay unit 20d to adjust the indoor temperature. Therefore, communication between the relay unit 20d and the indoor unit 30 is not necessary to adjust the indoor temperature, and simplification of control can be realized.
- a control device may be provided separately from the inverter 93, and this control device may perform various controls.
- a control device may be provided in each of the outdoor unit 10, the relay unit 20d, and the indoor unit 30, and the control of each device may be executed by the control devices communicating with each other.
- a temperature sensor that detects the temperature of the heat source side refrigerant may be provided in the heat source side refrigerant circuit A to adjust the flow rate of the heat source side refrigerant circulating in the heat source side refrigerant circuit A.
- the predetermined temperature (predetermined temperature T1 to predetermined temperature T6) shown in the fifth embodiment is, for example, a temperature designated by the user, a temperature preset in the air conditioner 500, or those temperatures and the indoor unit 30. It is a value determined by a correction temperature calculated by calculating with a value such as the number of rotations of the blower provided in the.
- the usage-side refrigerant circuit B may be controlled based on the information.
- the use-side refrigerant circuit B may be controlled based on a corrected temperature calculated by calculating with a value such as the number of rotations of the blower provided in the fan.
- Embodiment 5 the case where the flow rate control valve 98 is provided in the second usage-side refrigerant flow rate control unit 95 has been described as an example, but the present invention is not limited to this.
- a bypass pipe that connects the refrigerant inflow side pipe and the refrigerant outflow side pipe of the indoor heat exchanger 31, and a valve that controls the flow rate of the use side refrigerant that conducts the bypass pipe.
- You may comprise the apparatus and may comprise the 2nd utilization side refrigerant
- control operation described in the fifth embodiment can be applied to the first to fourth embodiments.
- the configuration for controlling the pump and the flow rate control valve using the temperature information has been described.
- a pressure sensor is provided, and the flow rate is adjusted according to the pressure difference at the inlet and outlet of the pump. The same effect can be obtained even if controlled.
- FIG. 29 is an installation schematic diagram of the air-conditioning apparatus according to Embodiment 6.
- the outdoor unit 10 is installed on the roof of a building 700.
- the relay unit 20 (including the relay unit 20a, the relay unit 20b, the relay unit 20c, and the relay unit 20d) is installed.
- the living space 711 provided on the first floor of the building 700 four indoor units 30 are installed.
- the relay unit 20 is installed in the shared space 722 and the shared space 723, and four indoor units 30 are installed in the living space 712 and the living space 713.
- the common spaces 721 to 723 refer to machine rooms, common hallways, lobbies, and the like provided on each floor of the building 700. That is, the shared space 721 to the shared space 723 are spaces other than the living space 711 to the living space 713 provided on each floor of the building 700.
- the relay unit 20 installed in the common space (common space 721 to common space 723) on each floor is connected to the outdoor unit 10 by the first extension pipe 41 and the second extension pipe 42 provided in the pipe installation space 730.
- the indoor units 30 installed in the living spaces (residence spaces 711 to 713) on each floor are connected to the relay unit 20 installed in the common space on each floor by the third extension pipe 43 and the fourth extension pipe 44, respectively. Has been.
- the air conditioner (the air conditioner 100, the air conditioner 200, the air conditioner 300, the air conditioner 400, or the air conditioner 500) installed in this way, the piping installed in the living space 711 to the living space 713 Since the use-side refrigerant such as water flows in the air, it is possible to prevent the heat-source-side refrigerant whose allowable concentration of the refrigerant leaking into the space is regulated from leaking into the living space 711 to the living space 713.
- the indoor unit 30 on each floor can be operated simultaneously with cooling and heating.
- the outdoor unit 10 and the relay unit 20 are provided in a place other than the living space, maintenance becomes easy.
- the relay unit 20 and the indoor unit 30 are separable, the indoor unit 30 and the third extension pipe are installed when the air conditioner is installed instead of the equipment that conventionally used the water refrigerant. 43 and the fourth extension pipe 44 can be reused.
- the outdoor unit 10 does not necessarily have to be installed on the roof of the building 700, and may be installed, for example, in a basement or a machine room on each floor.
- the present invention is not limited thereto, and various modifications and changes can be made without departing from the scope and spirit of the present invention. Moreover, it is good also as a form which provided the two three-way switching valve instead of the four-way valve 12 provided in the outdoor unit 10.
- the “unit” of the outdoor unit 10 and the indoor unit 30 does not necessarily mean that all the components are provided in the same housing or the outer wall of the housing. For example, even if the heat source side refrigerant flow switching unit 50 of the outdoor unit 10 is disposed at a location different from the housing in which the outdoor heat exchanger 13 is accommodated, such a configuration is included in the scope of the present invention.
- the use-side refrigerant flow switching unit 60 may be configured by providing two two-way switching valves instead of the three-way valves. According to such a configuration, the flow direction of the refrigerant passing through the two-way switching valve can always be a constant direction in any operation mode executed by the air conditioner 100, the air conditioner 200, and the air conditioner 300. Thus, the valve seal structure can be simplified.
- first pump 26 and the second pump 27 of the relay unit 20 are connected to the first intermediate heat exchanger 21 and the second intermediate heat exchanger 22.
- Such a configuration is included in the scope of the present invention even if it is disposed at a location different from the housing in which the housing is accommodated.
- a plurality of sets including the outdoor heat exchanger 13 and the compressor 11 are provided in the outdoor unit 10, and the refrigerant flowing out from each set is merged and conducted to the second extension pipe 42 to flow into the relay unit 20, The refrigerant that has flowed out of the relay unit 20 may be conducted to the first extension pipe 41 and branched to flow into each set.
- a strainer that captures dust or the like in the use side refrigerant in the use side refrigerant pipe 3 of the air conditioner 100, the air conditioner 200, the air conditioner 300, the air conditioner 400, and the air conditioner 500, or a use side refrigerant.
- the outdoor unit 10 is provided with the heat source side refrigerant flow switching unit 50, and the first intermediate heat exchanger 21 and the second intermediate heat exchanger 22 use the heat source side refrigerant circuit A and the use side refrigerant circuit.
- B and the counterflow type are shown as an example, but the present invention is not limited to this.
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Abstract
Description
実施の形態1.
図1は、本発明の実施の形態1に係る空気調和装置100の回路構成を示す回路図である。図1に基づいて、空気調和装置100の回路構成について説明する。この空気調和装置100は、ビルやマンション等に設置され、冷媒(熱源側冷媒及び利用側冷媒)を循環させる冷凍サイクル(熱源側冷媒回路及び利用側冷媒回路)を利用することで冷房負荷及び暖房負荷を同時に供給できるものである。なお、図1を含め、以下の図面では各構成部材の大きさの関係が実際のものとは異なる場合がある。
室外ユニット10は、圧縮機11と、流路切替手段である四方弁12と、室外熱交換器13と、が熱源側冷媒配管1で直列に接続されて構成されている。また、室外ユニット10には、第1接続配管4、第2接続配管5、逆止弁51、逆止弁52、逆止弁53、及び、逆止弁54で構成される熱源側冷媒流路切替部50が設けられている。この熱源側冷媒流路切替部50は、室内ユニット30が実行している運転に関わらず、中継部20に流入させる熱源側冷媒の流れを一定方向にする機能を有している。なお、熱源側冷媒流路切替部50を設けている場合を例に示しているが、熱源側冷媒流路切替部50を設けなくてもよい。
室内ユニット30には、室内熱交換器31が搭載されている。この室内熱交換器31は、第3延長配管43及び第4延長配管44を介して中継部20に設けられている利用側冷媒流路切替部60と接続するようになっている。この室内熱交換器31は、暖房運転時には凝縮器として機能し、冷房運転時には蒸発器として機能し、図示省略のファン等の送風機から供給される空気と利用側冷媒(この利用側冷媒については、以下で詳しく説明するものとする)との間で熱交換を行ない、空調対象域に供給するための暖房空気あるいは冷房空気を作成するものである。
中継部20には、第1中間熱交換器21と、冷媒流量制御装置25と、第2中間熱交換器22と、が順に熱源側冷媒配管2で直列に接続されて設けられている。また、中継部20には、第1ポンプ26と、第2ポンプ27と、利用側冷媒流路切替部60とが設けられている。そして、第1中間熱交換器21と、第1ポンプ26と、利用側冷媒流路切替部60と、を順に第1利用側冷媒配管3aで接続するとともに、第2中間熱交換器22と、第2ポンプ27と、利用側冷媒流路切替部60と、を順に第2利用側冷媒配管3bで接続している。また、第1利用側冷媒配管3a及び第2利用側冷媒配管3bは、第3延長配管43及び第4延長配管44と接続している。なお、以下の説明において、第1利用側冷媒配管3aと第2利用側冷媒配管3bとを、まとめて利用側冷媒配管3と称する場合がある。
図2は、空気調和装置100の全冷房運転モード時における冷媒の流れを示す冷媒回路図である。図3は、この全冷房運転モードでの熱源側冷媒の変遷を示すp-h線図(冷媒の圧力とエンタルピとの関係を示す線図)である。なお、図2では、太線で表された配管が冷媒(熱源側冷媒及び利用側冷媒)の循環する配管を示す。また、熱源側冷媒の流れ方向を実線矢印で、利用側冷媒の流れ方向を破線矢印で示している。さらに、図3に示す点[a]~点[d]の冷媒状態は、それぞれ図2に示す[a]~[d]での冷媒状態である。
この圧縮機11の冷媒圧縮過程は、周囲との熱の出入はないものとすると、図3の点[a]から点[b]に示す等エントロピ線で表される。圧縮機11から吐出された高温・高圧の冷媒は、四方弁12を通り、室外熱交換器13に流入する。そして、室外熱交換器13で室外空気に放熱しながら凝縮液化し、高圧液状冷媒となる。室外熱交換器13での冷媒の変化は、ほぼ圧力一定のもとで行われる。このときの冷媒変化は、室外熱交換器13の圧力損失を考慮すると、図3の点[b]から点[c]に示すやや傾いた水平に近い直線で表される。
図4は、空気調和装置100の全暖房運転モード時における冷媒の流れを示す冷媒回路図である。図5は、この全暖房運転モードでの熱源側冷媒の変遷を示すp-h線図(冷媒の圧力とエンタルピとの関係を示す線図)である。なお、図4では、太線で表された配管が冷媒(熱源側冷媒及び利用側冷媒)の循環する配管を示す。また、熱源側冷媒の流れ方向を実線矢印で、利用側冷媒の流れ方向を破線矢印で示している。さらに、図5に示す点[a]~点[d]の冷媒状態は、それぞれ図4に示す[a]~[d]での冷媒状態である。
この圧縮機11の冷媒圧縮過程は、図5の点[a]から点[b]に示す等エントロピ線で表される。圧縮機11から吐出された高温・高圧の冷媒は、四方弁12及び熱源側冷媒流路切替部50(逆止弁54)を介して、第2延長配管42を導通し、中継部20の第1中間熱交換器21に流入する。そして、第1中間熱交換器21に流入した冷媒は、第1利用側冷媒回路B1を循環する利用側冷媒に放熱しながら凝縮液化し、高圧の液状冷媒となる。このときの冷媒変化は、図5の点[b]から点[c]に示すやや傾いた水平に近い直線で表される。
図6は、空気調和装置100の冷房主体運転モード時における冷媒の流れを示す冷媒回路図である。図7は、この冷房主体運転モードでの熱源側冷媒の変遷を示すp-h線図(冷媒の圧力とエンタルピとの関係を示す線図)である。なお、図6では、太線で表された配管が冷媒(熱源側冷媒及び利用側冷媒)の循環する配管を示す。また、熱源側冷媒の流れ方向を実線矢印で、利用側冷媒の流れ方向を破線矢印で示している。さらに、図7に示す点[a]~点[e]の冷媒状態は、それぞれ図6に示す[a]~[e]での冷媒状態である。
この圧縮機11の冷媒圧縮過程は、図7の点[a]から点[b]に示す等エントロピ線で表される。圧縮機11から吐出された高温・高圧の冷媒は、四方弁12を通り、室外熱交換器13に流入する。そして、室外熱交換器13で室外空気に放熱しながら凝縮液化し、高圧の気液二相状態の冷媒となる。このときの冷媒変化は、図7の点[b]から点[c]に示すやや傾いた水平に近い直線で表される。
図8は、空気調和装置100の暖房主体運転モード時における冷媒の流れを示す冷媒回路図である。図9は、この暖房主体運転モードでの熱源側冷媒の変遷を示すp-h線図(冷媒の圧力とエンタルピとの関係を示す線図)である。なお、図8では、太線で表された配管が冷媒(熱源側冷媒及び利用側冷媒)の循環する配管を示す。また、熱源側冷媒の流れ方向を実線矢印で、利用側冷媒の流れ方向を破線矢印で示している。さらに、図9に示す点[a]~点[e]の冷媒状態は、それぞれ図8に示す[a]~[e]での冷媒状態である。
この圧縮機11の冷媒圧縮過程は、図9の点[a]から点[b]に示す等エントロピ線で表される。圧縮機11から吐出された高温・高圧の冷媒は、四方弁12及び熱源側冷媒流路切替部50(逆止弁54)を介して、第2延長配管42を導通し、中継部20の第1中間熱交換器21に流入する。そして、第1中間熱交換器21に流入した冷媒は、第1利用側冷媒回路B1を循環する利用側冷媒に放熱しながら凝縮液化し、高圧の液状冷媒となる。つまり、第1中間熱交換器21が凝縮器として機能するのである。このときの冷媒変化は、図9の点[b]から点[c]に示すやや傾いた水平に近い直線で表される。
つまり、施工に際しての制約を受けずに、中継部20を接続できるのである。
なお、図8で説明した暖房主体運転モードと同様の動作については説明を省略するものとする。
圧縮機11から吐出された高温・高圧の冷媒は、四方弁12を通り、室外熱交換器13に流入する。そして、室外熱交換器13で室外空気に放熱しながら凝縮液化し、高圧の気液二相状態の冷媒となる。このときの冷媒変化は、図14の点[b]から点[c]に示すやや傾いた水平に近い直線で表される。
図15、本発明の実施の形態2に係る空気調和装置200の回路構成を示す回路図である。図15に基づいて、空気調和装置200の回路構成について説明する。この空気調和装置200は、空気調和装置100と同様にビルやマンション等に設置され、冷媒(熱源側冷媒及び利用側冷媒)を循環させる冷凍サイクル(熱源側冷媒回路及び利用側冷媒回路)を利用することで冷房負荷及び暖房負荷を同時に供給できるものである。なお、実施の形態2では実施の形態1との相違点を中心に説明し、実施の形態1と同一部分には、同一符号を付して説明を省略するものとする。
つまり、中継部20aのコンパクト化に寄与できる。
図16、本発明の実施の形態3に係る空気調和装置300の回路構成を示す回路図である。図16に基づいて、空気調和装置300の回路構成について説明する。この空気調和装置300は、空気調和装置100及び空気調和装置200と同様にビルやマンション等に設置され、冷媒(熱源側冷媒及び利用側冷媒)を循環させる冷凍サイクル(熱源側冷媒回路及び利用側冷媒回路)を利用することで冷房負荷及び暖房負荷を同時に供給できるものである。なお、実施の形態3では実施の形態1及び実施の形態2との相違点を中心に説明し、実施の形態1及び実施の形態2と同一部分には、同一符号を付して説明を省略するものとする。
この圧縮部バイパス管85には、圧縮部バイパス管85を導通する熱源側冷媒の流量を制御する冷媒流量制御装置86が設けられている。
図17は、空気調和装置300の全冷房運転モード時における冷媒の流れを示す冷媒回路図である。図18は、この冷房主体運転モードでの熱源側冷媒の変遷を示すp-h線図(冷媒の圧力とエンタルピとの関係を示す線図)である。なお、図17では、太線で表された配管が冷媒(熱源側冷媒及び利用側冷媒)の循環する配管を示す。また、熱源側冷媒の流れ方向を実線矢印で、利用側冷媒の流れ方向を破線矢印で示している。さらに、図18に示す点[a]~点[e]の冷媒状態は、それぞれ図17に示す[a]~[d]での冷媒状態である。この全冷房運転モード時における利用側冷媒回路Bの利用側冷媒の流れについては実施の形態1と同様につき説明を省略する。
圧縮機11から吐出された高温・高圧の冷媒は、四方弁12を通り、室外熱交換器13に流入する。そして、室外熱交換器13で室外空気に放熱しながら凝縮液化し、高圧液状冷媒となる。このときの冷媒変化は、室外熱交換器13の圧力損失を考慮すると、図18の点[b]から点[c]に示すやや傾いた水平に近い直線で表される。
図19は、空気調和装置300の全暖房運転モード時における冷媒の流れを示す冷媒回路図である。図20は、この全暖房運転モードでの熱源側冷媒の変遷を示すp-h線図(冷媒の圧力とエンタルピとの関係を示す線図)である。なお、図19では、太線で表された配管が冷媒(熱源側冷媒及び利用側冷媒)の循環する配管を示す。また、熱源側冷媒の流れ方向を実線矢印で、利用側冷媒の流れ方向を破線矢印で示している。さらに、図20に示す点[a]~点[e]の冷媒状態は、それぞれ図19に示す[a]~[e]での冷媒状態である。この全暖房運転モード時における利用側冷媒回路Bの利用側冷媒の流れについては実施の形態1と同様につき説明を省略する。
圧縮機11から吐出された高温・高圧の冷媒は、四方弁12及び熱源側冷媒流路切替部50(逆止弁54)を介して、第2延長配管42を導通し、中継部20の第1中間熱交換器21に流入する。そして、第1中間熱交換器21に流入した冷媒は、第1利用側冷媒回路B1を循環する利用側冷媒に放熱しながら凝縮液化し、高圧の液状冷媒となる。このときの冷媒変化は、図20の点[b]から点[c]に示すやや傾いた水平に近い直線で表される。
図21は、空気調和装置300の冷房主体運転モード時における冷媒の流れを示す冷媒回路図である。図22は、この冷房主体運転モードでの熱源側冷媒の変遷を示すp-h線図(冷媒の圧力とエンタルピとの関係を示す線図)である。なお、図21では、太線で表された配管が冷媒(熱源側冷媒及び利用側冷媒)の循環する配管を示す。また、熱源側冷媒の流れ方向を実線矢印で、利用側冷媒の流れ方向を破線矢印で示している。さらに、図22に示す点[a]~点[f]の冷媒状態は、それぞれ図21に示す[a]~[f]での冷媒状態である。
また、中継部20の利用側冷媒流路切替部60では、第1切替弁61a~第1切替弁61c及び第2切替弁62a~第2切替弁62cを第2中間熱交換器22と室内ユニット30a~室内ユニット30cとの間を利用側冷媒が循環するように切り替えるとともに、第1切替弁61d及び第2切替弁62dを第1中間熱交換器21と室内ユニット30dとの間を利用側冷媒が循環するように切り替える。この状態で、圧縮機11の運転を開始する。
圧縮機11から吐出された高温・高圧の冷媒は、四方弁12を通り、室外熱交換器13に流入する。そして、室外熱交換器13で室外空気に放熱しながら凝縮液化し、高圧の気液二相状態の冷媒となる。このときの冷媒変化は、図22の点[b]から点[c]に示すやや傾いた水平に近い直線で表される。
図23は、空気調和装置300の暖房主体運転モード時における冷媒の流れを示す冷媒回路図である。図24は、この暖房主体運転モードでの熱源側冷媒の変遷を示すp-h線図(冷媒の圧力とエンタルピとの関係を示す線図)である。なお、図23では、太線で表された配管が冷媒(熱源側冷媒及び利用側冷媒)の循環する配管を示す。また、熱源側冷媒の流れ方向を実線矢印で、利用側冷媒の流れ方向を破線矢印で示している。さらに、図24に示す点[a]~点[e]の冷媒状態は、それぞれ図23に示す[a]~[e]での冷媒状態である。
圧縮機11から吐出された高温・高圧の冷媒は、四方弁12及び熱源側冷媒流路切替部50(逆止弁52)を介して、第2延長配管42を導通し、中継部20の第1中間熱交換器21に流入する。そして、第1中間熱交換器21に流入した冷媒は、第1利用側冷媒回路B1を循環する利用側冷媒に放熱しながら凝縮液化し、高圧の液状冷媒となる。このときの冷媒変化は、図24の点[b]から点[c]に示すやや傾いた水平に近い直線で表される。
図25、本発明の実施の形態4に係る空気調和装置400の回路構成を示す回路図である。図25に基づいて、空気調和装置400の回路構成について説明する。この空気調和装置400は、空気調和装置100、空気調和装置200及び空気調和装置300と同様にビルやマンション等に設置され、冷媒(熱源側冷媒及び利用側冷媒)を循環させる冷凍サイクル(熱源側冷媒回路及び利用側冷媒回路)を利用することで冷房負荷及び暖房負荷を同時に供給できるものである。なお、実施の形態4では実施の形態1~実施の形態3との相違点を中心に説明し、実施の形態1~実施の形態3と同一部分には、同一符号を付して説明を省略するものとする。
図26は、空気調和装置400の全冷房運転モード時における熱源側冷媒の変遷を示すp-h線図(冷媒の圧力とエンタルピとの関係を示す線図)である。図25及び図26に基づいて、空気調和装置400が実行する全冷房運転モードについて、全冷房運転モード時における冷媒(熱源側冷媒及び利用側冷媒)の流れとともに説明する。
この圧縮機11の冷媒圧縮過程は、周囲との熱の出入はないものとすると、図26の点[a]から点[b]に示す等エントロピ線で表される。圧縮機11から吐出された高温・高圧の冷媒は、四方弁12を通り、室外熱交換器13に流入する。そして、室外熱交換器13で室外空気に放熱しながら凝縮液化し、高圧の液状冷媒となる。室外熱交換器13での冷媒の変化は、ほぼ圧力一定のもとで行われる。このときの冷媒変化は、室外熱交換器13の圧力損失を考慮すると、図26の点[b]から点[c]に示すやや傾いた水平に近い直線で表される。
図27は、空気調和装置400の全暖房運転モード時における熱源側冷媒の変遷を示すp-h線図(冷媒の圧力とエンタルピとの関係を示す線図)である。図25及び図27に基づいて、空気調和装置400が実行する全暖房運転モードについて、全暖房運転モード時における冷媒(熱源側冷媒及び利用側冷媒)の流れとともに説明する。
この圧縮機11の冷媒圧縮過程は、図27の点[a]から点[b]に示す等エントロピ線で表される。圧縮機11から吐出された高温・高圧の冷媒は、四方弁12及び熱源側冷媒流路切替部50(逆止弁54)を介して、第2延長配管42を導通し、中継部20cの第2冷媒流量制御装置25bを介して第1中間熱交換器21に流入する。そして、第1中間熱交換器21に流入した冷媒は、第1利用側冷媒回路B1を循環する利用側冷媒に放熱しながら凝縮液化し、高圧の気液二相状態の冷媒となる。このときの冷媒変化は、図27の点[b]から点[c]に示すやや傾いた水平に近い直線で表される。
この冷房主体運転モードとは、たとえば3台の室内ユニット30が冷房運転を行ない、1台の室内ユニット30が暖房運転を行なうような、冷房負荷の方が大きい場合における冷暖同時運転モードのことである。なお、図25では、冷房運転を行なう3台の室内ユニット30を、紙面左側から室内ユニット30a、室内ユニット30b、室内ユニット30cとし、暖房運転を行なう紙面右側の1台の室内ユニット30を室内ユニット30dとして図示している。また、室内ユニット30a~室内ユニット30dに応じて、それぞれに接続する第5切替弁66を第5切替弁66a~第5切替弁66dとし、それぞれに接続する第6切替弁67を第6切替弁67a~第6切替弁67dとし、それぞれに接続する第7切替弁68を第7切替弁68a~第7切替弁68dとし、それぞれに接続する第8切替弁69を第8切替弁69a~第8切替弁69dとして図示している。
この暖房主体運転モードとは、たとえば3台の室内ユニット30が暖房運転を行ない、1台の室内ユニット30が冷房運転を行なうような、暖房負荷の方が大きい場合における冷暖同時運転モードのことである。なお、図25では、暖房運転を行なう3台の室内ユニット30を、紙面左側から室内ユニット30a、室内ユニット30b、室内ユニット30cとし、冷房運転を行なう紙面右側の1台の室内ユニット30を室内ユニット30dとして図示している。また、室内ユニット30a~室内ユニット30dに応じて、それぞれに接続する第5切替弁66を第5切替弁66a~第5切替弁66dとし、それぞれに接続する第6切替弁67を第6切替弁67a~第6切替弁67dとし、それぞれに接続する第7切替弁68を第7切替弁68a~第7切替弁68dとし、それぞれに接続する第8切替弁69を第8切替弁69a~第8切替弁69dとして図示している。
図28、本発明の実施の形態5に係る空気調和装置500の回路構成を示す回路図である。図28に基づいて、空気調和装置500の構成及び利用側冷媒回路Bの制御動作について説明する。この空気調和装置500は、空気調和装置100、空気調和装置200、空気調和装置300及び空気調和装置400と同様にビルやマンション等に設置され、冷媒(熱源側冷媒及び利用側冷媒)を循環させる冷凍サイクル(熱源側冷媒回路及び利用側冷媒回路)を利用することで冷房負荷及び暖房負荷を同時に供給できるものである。なお、実施の形態5では実施の形態1~実施の形態4との相違点を中心に説明し、実施の形態1~実施の形態4と同一部分には、同一符号を付して説明を省略するものとする。
そして、インバータ93は、室内流入側温度センサ96及び室内流出側温度センサ97が検知した温度情報を監視しつつ、第1温度センサ91及び第2温度センサ92が検知した温度情報に基づいて、第1ポンプ26及び第2ポンプ27の動作を適宜調整する。
まず、インバータ93は、冷房運転を実行する室内ユニット30を特定し、室内ユニット30の運転台数に応じて、第1ポンプ26及び第2ポンプ27の駆動を制御する。ここでは、上述した全冷房運転モード時における利用側冷媒回路Bについて説明するものとする。全冷房運転モードでは、第1ポンプ26を停止し、第2ポンプ27を駆動させて、第2利用側冷媒回路B2の利用側冷媒の循環量を調整するようになっている(実施の形態1で示した図2及び実施の形態3で示した図17参照)。
まず、インバータ93は、暖房運転を実行する室内ユニット30を特定し、室内ユニット30の運転台数に応じて、第1ポンプ26及び第2ポンプ27の駆動を制御する。ここでは、上述した全暖房運転モード時における利用側冷媒回路Bについて説明するものとする。全冷房運転モードでは、第1ポンプ26を駆動させ、第2ポンプ27を停止し、第1利用側冷媒回路B1の利用側冷媒の循環量を調整するようになっている(実施の形態1で示した図4及び実施の形態3で示した図19参照)。
まず、インバータ93は、冷房運転又は暖房運転を実行する室内ユニット30を特定し、室内ユニット30の運転台数に応じて、第1ポンプ26及び第2ポンプ27の駆動を制御する。ここでは、第1中間熱交換器21に利用側冷媒を循環させている場合(少なくとも1台の室内ユニット30が暖房運転を実行している場合)、及び、第2中間熱交換器22に利用側冷媒を循環させている場合(少なくとも1台の室内ユニット30が冷房運転を実行している場合)について説明する。
図29は、実施の形態6における空気調和装置の設置概略図である。この実施の形態6においては、実施の形態1~実施の形態5に示した空気調和装置のビルへの設置方法の一例を示す。図29に示すように、室外ユニット10は、ビル700の屋上に設置されている。ビル700の1階に設けられた共用空間721には、中継部20(中継部20a、中継部20b、中継部20c及び中継部20dも含む)が設置されている。そして、ビル700の1階に設けられた居住空間711には、4台の室内ユニット30が設置されている。
Claims (17)
- 圧縮機、室外熱交換器、複数台の中間熱交換器、及び、各中間熱交換器の間に設けられた冷媒流量制御装置が直列に接続される熱源側冷媒回路と、
前記複数台の中間熱交換器のそれぞれと複数の室内熱交換器が並列に接続される複数の利用側冷媒回路と、を備え、
前記圧縮機及び前記室外熱交換器は、室外ユニットに設けられ、
前記複数台の中間熱交換器及び冷媒流量制御装置は、中継部に設けられ、
前記複数台の室内熱交換器は、複数台の室内ユニットのそれぞれに設けられ、
前記複数台の中間熱交換器において、
前記熱源側冷媒回路を循環する熱源側冷媒と前記利用側冷媒回路を循環する利用側冷媒とを熱交換させる
ことを特徴とする空気調和装置。 - 圧縮機、室外熱交換器、複数台の中間熱交換器、及び、各中間熱交換器の間に設けた第1冷媒流量制御装置、前記複数台の中間熱交換器のうち上流側に位置する第1中間熱交換器の入口側に設けた第2冷媒流量制御装置、及び、前記複数台の中間熱交換器のうち下流側に位置する第2中間熱交換器の出口側に設けた第3冷媒流量制御装置が直列に接続される熱源側冷媒回路と、
前記複数台の中間熱交換器のそれぞれと複数の室内熱交換器が並列に接続される複数の利用側冷媒回路と、を備え、
前記圧縮機及び前記室外熱交換器は、室外ユニットに設けられ、
前記複数台の中間熱交換器、前記第1冷媒流量制御装置、前記第2冷媒流量制御装置、及び、前記第3冷媒流量制御装置は、中継部に設けられ、
前記複数台の室内熱交換器は、室内ユニットのそれぞれに設けられ、
前記複数台の中間熱交換器において、
前記熱源側冷媒回路を循環する熱源側冷媒と前記利用側冷媒回路を循環する利用側冷媒とを熱交換させる
ことを特徴とする空気調和装置。 - 前記熱源側冷媒回路において、
前記中継部に設けた前記複数台の中間熱交換器のうち少なくとも1台をバイパスするバイパス配管と、
前記バイパス配管に設置され、このバイパス配管を流れる熱源側冷媒の流量を制御するバイパス冷媒流量制御手段と、を設けた
ことを特徴とする請求項1又は2に記載の空気調和装置。 - 前記熱源側冷媒回路において、
前記中継部の上流側に位置する第1中間熱交換器の入口側に設けた気液分離器と、
前記気液分離器で分離された液状冷媒を前記第1中間熱交換器の出口側にバイパスする液状冷媒バイパス配管と、
前記液状冷媒バイパス配管に設置され、この液状冷媒バイパス配管を流れる熱源側冷媒の流量を制御する液状冷媒流量制御装置と、を設けた
ことを特徴とする請求項1又は2に記載の空気調和装置。 - 圧縮機、室外熱交換器、複数台の中間熱交換器、及び、各中間熱交換器の間に設けられ、熱源側冷媒の減圧時の膨張動力を回収する膨張動力回収部及びその膨張動力を用いて熱源側冷媒を圧縮する圧縮部からなる膨張装置冷媒流量制御装置が直列に接続された熱源側冷媒回路と、
前記複数台の中間熱交換器のそれぞれと複数の室内熱交換器が並列に接続される複数の利用側冷媒回路と、を備え、
前記圧縮機及び前記室外熱交換器は、室外ユニットに設けられ、
前記複数台の中間熱交換器及び前記膨張装置冷媒流量制御装置は、中継部に設けられ、 前記複数台の室内熱交換器は、複数台の室内ユニットのそれぞれに設けられ、
前記複数台の中間熱交換器において、
前記熱源側冷媒回路を循環する熱源側冷媒と前記利用側冷媒回路を循環する利用側冷媒とを熱交換させる
ことを特徴とする空気調和装置。 - 前記熱源側冷媒回路における前記圧縮部の上流側と下流側を接続して前記圧縮部をバイパスする圧縮部バイパス管と、
前記圧縮部バイパス管に設置され、この圧縮部バイパス管を流れる熱源側冷媒の流量を制御する冷媒流量制御装置と、を設けた
ことを特徴とする請求項5に記載の空気調和装置。 - 前記中継部と前記複数の室内ユニットのそれぞれとは、
2本の延長配管で接続される
ことを特徴とする請求項1、2及び5のいずれか一項に記載の空気調和装置。 - 前記中継部に設けた前記複数の利用側冷媒回路を選択的に切り替え可能な利用側冷媒流路切替部を前記中継部に設け、
前記利用側冷媒流路切替部は、
前記複数台の中間熱交換器のいずれか1つを選択した前記室内熱交換器に接続させることで前記複数の利用側冷媒回路を選択的に切り替える
ことを特徴とする請求項7に記載の空気調和装置。 - 前記中継部に設けた前記複数台の中間熱交換器では、
前記熱源側冷媒回路を循環する熱源側冷媒と前記利用側冷媒回路を循環する利用側冷媒とを対向流としている
ことを特徴とする請求項1、2及び5のいずれか一項に記載の空気調和装置。 - 前記中継部に、
前記利用側冷媒回路を循環する利用側冷媒の流量を制御する利用側冷媒流量制御部を設けた
ことを特徴とする請求項1、2及び5のいずれか一項に記載の空気調和装置。 - 前記利用側冷媒流量制御部は、
前記室内ユニットに流入する利用側冷媒の温度及び前記室内ユニットから流出する利用側冷媒の温度のうち少なくとも1つに基づいて前記室内ユニットに供給する利用側冷媒の流量を調整する
ことを特徴とする請求項10に記載の空気調和装置。 - 前記利用側冷媒流量制御部は、
前記複数台の中間熱交換器に流入する利用側冷媒の温度及び前記複数台の中間熱交換器から流出する利用側冷媒の温度のうち少なくとも1つに基づいて前記複数台の中間熱交換器に供給する利用側冷媒の流量を調整する
ことを特徴とする請求項10に記載の空気調和装置。 - 前記利用側冷媒回路を循環させる利用側冷媒に、水及び不凍液の少なくとも1つを使用している
ことを特徴とする請求項1、2及び5のいずれか一項に記載の空気調和装置。 - 前記熱源側冷媒回路を循環させる熱源側冷媒に、自然冷媒又は地球温暖化係数がフロン冷媒よりも小さい冷媒を使用している
ことを特徴とする請求項1、2及び5のいずれか一項に記載の空気調和装置。 - 前記複数台の中間熱交換器において、
前記熱源側冷媒は、超臨界状態で凝縮することなく、前記利用側冷媒を加熱する
ことを特徴とする請求項1、2及び5のいずれか一項に記載の空気調和装置。 - 前記室内ユニットは、
ビルの各階に設けられた居住空間に設置され、
前記室外ユニット及び前記中継部は、
前記居住空間以外に設置される
ことを特徴とする請求項1、2及び5のいずれか一項に記載の空気調和装置。 - 前記中継部は、
前記ビルに設けられた共用空間に設置される
ことを特徴とする請求項16に記載の空気調和装置。
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CN2008801289327A CN102016442B (zh) | 2008-04-30 | 2008-11-17 | 空气调节装置 |
US12/990,568 US9212825B2 (en) | 2008-04-30 | 2008-11-17 | Air conditioner |
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EP (1) | EP2284456B1 (ja) |
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JPWO2009133644A1 (ja) | 2011-08-25 |
CN102016442A (zh) | 2011-04-13 |
US9212825B2 (en) | 2015-12-15 |
EP2284456A4 (en) | 2015-03-04 |
EP2284456A1 (en) | 2011-02-16 |
US20110113802A1 (en) | 2011-05-19 |
JP5188572B2 (ja) | 2013-04-24 |
EP2284456B1 (en) | 2017-05-10 |
CN102016442B (zh) | 2013-06-26 |
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