WO2007105604A1 - 空気調和装置 - Google Patents
空気調和装置 Download PDFInfo
- Publication number
- WO2007105604A1 WO2007105604A1 PCT/JP2007/054587 JP2007054587W WO2007105604A1 WO 2007105604 A1 WO2007105604 A1 WO 2007105604A1 JP 2007054587 W JP2007054587 W JP 2007054587W WO 2007105604 A1 WO2007105604 A1 WO 2007105604A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- refrigerant
- pipe
- unit
- pressure gas
- indoor
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B15/00—Sorption machines, plants or systems, operating continuously, e.g. absorption type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/005—Arrangement or mounting of control or safety devices of safety devices
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/04—Refrigeration circuit bypassing means
-
- 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
- F25B2400/13—Economisers
-
- 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
- F25B2500/00—Problems to be solved
- F25B2500/19—Calculation of parameters
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/21—Refrigerant outlet evaporator temperature
-
- 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/04—Refrigerant level
Definitions
- the present invention relates to a refrigerant circuit for an air conditioner and an air conditioner including the refrigerant circuit.
- Patent Document 1 Japanese Patent Laid-Open No. 3-186170
- Patent Document 1 a multi-air conditioner that can be operated simultaneously with cooling and heating reaches the outdoor unit cooling / heating selection unit when performing refrigerant quantity determination operation in all-room cooling operation. Since the high-pressure gas pipe is closed on the cooling / heating selection side, the refrigerant condenses and accumulates in the pipe, which may increase detection errors.
- An object of the present invention is to reduce the pressure of the high-pressure gas pipe during the refrigerant amount determination operation of the multi-air conditioner that can be operated simultaneously with cooling and heating, and to prevent liquid refrigerant from being accumulated in the high-pressure gas pipe due to condensation.
- An air conditioner is an air conditioner that performs refrigerant amount determination operation for determining the amount of refrigerant in the refrigerant circuit, and includes a heat source unit, a utilization unit, an expansion mechanism, A first gas refrigerant pipe, a second gas refrigerant pipe, a liquid refrigerant pipe, a switching mechanism, a bypass circuit, a bypass circuit opening / closing means, and a control unit are provided.
- the heat source unit has compression means for compressing the refrigerant gas and heat source side heat exchange.
- the usage unit has usage side heat exchange.
- the first gas refrigerant pipe extends from the discharge side of the compression means to the utilization unit.
- the second gas refrigerant pipe extends from the suction side of the compression means to the utilization unit.
- Liquid refrigerant piping It extends from the heat source side heat exchanger to the utilization unit.
- the switching mechanism can switch between the first state and the second state.
- the first state is a state in which the refrigerant flowing in the liquid refrigerant pipe is evaporated in the use side heat exchanger and then flows into the second gas refrigerant pipe.
- the second state is a state in which the refrigerant flowing through the first gas refrigerant pipe is condensed in the use side heat exchanger and then flows into the liquid refrigerant pipe.
- the bypass circuit bypasses the first gas refrigerant pipe and the second gas refrigerant pipe.
- the bypass circuit opening / closing means is provided on the bypass circuit and opens / closes the bypass circuit.
- the controller opens the bypass circuit opening / closing means before performing the refrigerant quantity determination operation.
- This air conditioner has two gas lines of refrigerant piping, and the switching mechanism freely switches between the first state (cooling state) and the second state (heating state) to freely perform cooling operation and heating operation. Can be set.
- the refrigerant quantity determination operation is performed by setting all the rooms (all use units) to the first state (cooling state) in the shelf structure (cooling / heating selection unit). Since the first gas refrigerant pipe (high pressure gas pipe) from the heat source unit to the switching mechanism is closed, the refrigerant condenses and accumulates in the pipe, which may increase the detection error.
- a bypass circuit opening / closing means for bypassing the first gas refrigerant pipe and the second gas refrigerant pipe is provided, and the bypass circuit opening / closing means (bypass valve) is opened during the refrigerant amount determination operation.
- An air conditioner according to a second invention is the air conditioner according to the first invention, wherein the bypass circuit opening / closing means is provided in the heat source unit.
- the bypass circuit opening / closing means is provided in the heat source unit. Therefore, a bypass circuit can be provided in the refrigerant circuit without performing piping work for the bypass circuit at the time of construction. For this reason, it is possible to reduce the labor and cost involved in the construction.
- An air conditioner according to a third invention is the air conditioner according to the first invention or the second invention, and further includes a switching unit.
- the switching unit is the heat source unit and the utilization unit. Another unit.
- the switching unit has a switching mechanism.
- the bypass circuit opening / closing means is provided in the switching unit.
- a bypass circuit opening / closing means is provided in the switching unit.
- the refrigerant hardly flows through the first gas refrigerant pipe only by providing the bypass circuit opening / closing means in the heat source unit. For this reason, the temperature of the gas refrigerant in the pipe changes due to the inflow heat of the outside air force, the refrigerant density may change, and the detection error may increase.
- a bypass circuit opening / closing means for biasing the first gas refrigerant pipe and the second gas refrigerant pipe is provided in the switching unit, and by using this together, a low-pressure gas is introduced into the first gas refrigerant pipe. It makes it easier for the refrigerant to flow. For this reason, it is possible to suppress the temperature change of the gas refrigerant in the pipe due to the inflow heat from the outside air, and the detection error can be reduced.
- a bypass circuit can be provided in the refrigerant circuit without the need for piping work for the bypass circuit. For this reason, it is possible to reduce the labor and cost involved in the construction.
- An air conditioner according to a fourth aspect of the present invention is the air conditioner according to any of the first to third aspects of the present invention, further comprising a temperature detecting means.
- the temperature detection means detects the refrigerant temperature in the first gas refrigerant pipe and outputs a refrigerant temperature detection value.
- the control unit corrects the determined refrigerant amount determined by the refrigerant amount determination operation based on the detected refrigerant temperature value.
- This air conditioner has a bypass circuit that bypasses the first gas refrigerant pipe and the second gas refrigerant pipe to equalize the refrigerant gas pressure distribution in the pipe, so that the inside of the first gas refrigerant pipe The refrigerant is in the flow. For this reason, the temperature of the gas refrigerant in the pipe changes due to the inflow heat from the outside air, the refrigerant density may change, and the detection error may increase.
- the detection error can be reduced by providing temperature detection means in the first gas refrigerant pipe and correcting the refrigerant density in the pipe using the refrigerant temperature detection value. For this reason, more accurate refrigerant quantity determination operation is possible.
- An air conditioner according to a fifth invention is the air conditioner according to the fourth invention, wherein the temperature detecting means is provided in the switching unit.
- This air conditioner is provided with temperature detecting means on the first gas refrigerant pipe in the switching unit.
- the temperature detecting means can be provided on the first gas refrigerant pipe without providing the temperature detecting means in the refrigerant communication pipe at the time of construction. For this reason, it is possible to reduce the labor and cost involved in the construction.
- An air conditioner according to a sixth aspect of the present invention is the air conditioner according to the fourth aspect or the fifth aspect of the present invention, wherein the temperature detecting device is provided in the heat source unit.
- temperature detecting means is provided on the first gas refrigerant pipe in the heat source unit. Therefore, the temperature detecting means can be provided on the first gas refrigerant pipe without providing the temperature detecting means in the refrigerant communication pipe at the time of construction. For this reason, it is possible to reduce the labor and cost involved in the construction. Further, when used in combination with the temperature detecting means in the switching unit of the fifth invention, the refrigerant density in the pipe can be corrected with higher accuracy.
- a bypass circuit opening / closing means that bypasses the first gas refrigerant pipe and the second gas refrigerant pipe is provided, and the bypass is performed during the refrigerant amount determination operation.
- the circuit opening / closing means By opening the circuit opening / closing means, the pressure difference between the first gas refrigerant pipe and the second gas refrigerant pipe is reduced, and the accumulation of liquid refrigerant due to condensation in the first gas refrigerant pipe is prevented. . For this reason, highly accurate refrigerant quantity determination operation becomes possible.
- the bypass circuit can be provided in the refrigerant circuit without performing bypass piping work at the time of construction. For this reason, it is possible to reduce the labor and cost involved in the construction.
- a bypass circuit opening / closing means for bypassing the first gas refrigerant pipe and the second gas refrigerant pipe is provided in the switching unit, and by using this together, the first gas refrigerant pipe is provided in the first gas refrigerant pipe.
- the low-pressure gas refrigerant is easy to flow. For this reason, it is possible to suppress the temperature change of the gas refrigerant in the pipe due to the inflow heat of the outside air force, and the detection error can be reduced.
- the bypass circuit can be provided in the refrigerant circuit without performing the piping work for the bypass circuit at the time of construction. For this reason, it is possible to reduce the labor and cost involved in the construction.
- the temperature detection means is provided in the first gas refrigerant pipe, and the detection error is reduced by correcting the refrigerant density in the pipe using the refrigerant temperature detection value. Can be made. For this reason, more accurate refrigerant quantity determination operation is possible.
- the temperature detecting means can be provided on the first gas refrigerant pipe without providing the temperature detecting means on the refrigerant communication pipe at the time of construction. For this reason, it is possible to reduce the labor and cost involved in the construction.
- the temperature detecting means can be provided on the first gas refrigerant pipe without providing the temperature detecting means on the refrigerant communication pipe at the time of construction. For this reason, it is possible to reduce the labor and cost involved in the construction. Further, by using together with the temperature detecting means in the switching unit of the fifth invention, the refrigerant density in the pipe can be corrected with higher accuracy.
- FIG. 1 is a schematic configuration diagram of an air conditioner according to an embodiment of the present invention.
- FIG. 2 is a control block diagram of the air conditioner.
- FIG. 3 Flow chart of test operation mode.
- FIG. 4 Flow chart of refrigerant automatic charging operation.
- FIG. 5 is a schematic diagram showing the state of refrigerant flowing in the refrigerant circuit in the refrigerant quantity determination operation (illustration of a four-way switching valve and the like is omitted).
- FIG. 6 Flow chart of pipe volume judgment operation.
- FIG. 7 is a Mollier diagram showing the refrigeration cycle of the air conditioner in the pipe volume judgment operation for the liquid refrigerant communication pipe.
- FIG. 8 is a Mollier diagram showing the refrigeration cycle of the air conditioner in the pipe volume judgment operation for the gas refrigerant communication pipe.
- FIG. 9 is a flowchart of initial refrigerant quantity detection operation.
- FIG. 10 is a flowchart of a refrigerant leak detection operation mode.
- V3 1st bypass opening / closing valve (Bypass circuit opening / closing means)
- T8 1st high pressure gas piping temperature sensor (temperature detection means)
- FIG. 1 is a schematic configuration diagram of an air-conditioning apparatus 1 according to one embodiment of the present invention.
- the air conditioner 1 is an apparatus used for air conditioning in a room such as a building by performing a vapor compression refrigeration cycle operation.
- the air conditioner 1 mainly includes an outdoor unit 2 as one heat source unit, and indoor units 3a to 3c as a plurality of (three in this embodiment) usage units connected in parallel.
- Connection units 4a to 4c provided corresponding to the indoor units 3a to 3c
- a first refrigerant communication pipe group 5 for connecting the outdoor unit 2 and the connection units 4a to 4c
- the connection units 4a to 4c and the indoors and a second refrigerant communication pipe group 7 for connecting the units 3a to 3c.
- the first refrigerant communication pipe group 5 is composed of a first liquid refrigerant communication pipe 51, a high-pressure gas refrigerant communication pipe 52, and a low-pressure gas refrigerant communication pipe 53
- the second refrigerant communication pipe group 7 is a second liquid refrigerant communication pipe.
- the piping 71a to 71c and the second gas refrigerant communication piping 72a to 72c are configured.
- the air conditioner 1 performs a cooling operation for a certain air-conditioned space and performs a heating operation for another air-conditioned space, so that the indoor units 3a to 3c are installed. It is configured to enable simultaneous cooling and heating according to the requirements of the air-conditioned space.
- the vapor compression refrigerant circuit of the air conditioner 1 of the present embodiment 10 is configured by connecting the outdoor unit 2, the indoor units 3a to 3c, the connection units 4a to 4c, the first refrigerant communication pipe group 5, and the second refrigerant communication pipe group 7. .
- the indoor units 3a to 3c are installed in a ceiling of a room such as a building or suspended, or installed on a wall surface of the room.
- the indoor units 3a to 3c are connected to the connection units 4a to 4c via the second refrigerant communication pipe group 7, and constitute a part of the refrigerant circuit 10.
- the configuration of the indoor units 3a to 3c will be described. Since the indoor unit 3a and the indoor units 3b and 3c have the same configuration, only the configuration of the indoor unit 3a will be described here, and the configuration of the indoor units 3b and 3c will be described in each part of the indoor unit 3a. Xb and Xc are attached instead of Xa, and the description of each part is omitted.
- the force S corresponds to the indoor fan 32a of the indoor unit 3a and the indoor fans 32b and 32c of the indoor units 3b and 3c.
- the indoor unit 3a mainly has an indoor side refrigerant circuit 30a that constitutes a part of the refrigerant circuit 10.
- This indoor refrigerant circuit 30a mainly has an indoor expansion valve V9a as an expansion mechanism and an indoor heat exchanger 3la as a use side heat exchanger.
- the indoor expansion valve V9a is an electric expansion valve connected to the liquid side of the indoor heat exchanger 31a in order to adjust the flow rate of the refrigerant flowing through the indoor refrigerant circuit 30a.
- the indoor heat exchanger ⁇ 31a is a cross-fin type 'and' tube heat exchanger composed of heat transfer tubes and a large number of fins, and functions as a refrigerant evaporator during cooling operation to transfer indoor air. It is a heat exchanger that cools and heats indoor air by functioning as a refrigerant condenser during heating operation.
- the indoor unit 3a has an indoor fan 32a as a blower fan that sucks indoor air into the unit and exchanges heat with the refrigerant in the indoor heat exchanger 31a, and then supplies the air as indoor air to the room. ing.
- the indoor fan 32a is a fan that can vary the air volume Wr of air supplied to the indoor heat exchanger 31a.
- the indoor fan 32a is a centrifugal fan or multiblade driven by a motor 33a that also serves as a DC fan motor. Fan etc.
- the indoor unit 3a is provided with various sensors.
- Indoor heat exchanger 31a On the liquid side, a liquid temperature sensor T9a that detects the temperature of the refrigerant (that is, the refrigerant temperature corresponding to the condensation temperature Tc during heating operation or the evaporation temperature Te during cooling operation) is provided.
- a gas side temperature sensor TlOa for detecting the refrigerant temperature Teo is provided on the gas side of the indoor heat exchanger 31a.
- an indoor temperature sensor Tl la is provided for detecting the temperature of the indoor air flowing into the unit (that is, the indoor temperature Tr).
- the indoor unit 3a includes an indoor side control unit 34a that controls the operation of each unit constituting the indoor unit 3a.
- the indoor side control unit 34a includes a microcomputer, a memory, and the like provided for controlling the indoor unit 3a, and a remote controller (not shown) for individually operating the indoor unit 3a. Control signals etc. can be exchanged between them, and control signals etc. can be exchanged between the outdoor unit 2 and the connection units 4a to 4c via the transmission line 8a.
- the outdoor unit 2 is installed outside a building or the like, and is connected to the connection units 4a to 4c via the first refrigerant communication pipe group 5, and constitutes the refrigerant circuit 10.
- the outdoor unit 2 mainly has an outdoor refrigerant circuit 20 that constitutes a part of the refrigerant circuit 10.
- This outdoor refrigerant circuit 20 mainly includes a compressor 21, a four-way switching valve VI, an outdoor heat exchanger 22 as a heat source side heat exchanger, an outdoor expansion valve V2 as an expansion mechanism, an accumulator 23, and a temperature control.
- the compressor 21 is a compressor capable of changing the operating capacity, and in the present embodiment, is a positive displacement compressor driven by a motor 21a whose rotational speed Rm is controlled by an inverter. . In the present embodiment, only one compressor 21 is provided, but the present invention is not limited to this, and two or more compressors may be connected in parallel according to the number of indoor units connected.
- the four-way switching valve VI is a valve provided to allow the outdoor heat exchange 22 to function as an evaporator and a condenser.
- the four-way selector valve VI is connected to the refrigerant gas side of the outdoor heat exchanger 22, the suction side accumulator 23 of the compressor 21, the discharge side of the compressor 21, and the decompression circuit 28.
- the outdoor heat exchange functions as a condenser
- the discharge side of the compressor 21 and the refrigerant gas side of the outdoor heat exchange are connected, and the accumulator 23 and the decompression circuit 28 on the suction side of the compressor 21 are connected.
- the outdoor heat exchanger 22 functions as an evaporator
- the refrigerant heat side of the outdoor heat exchanger and the accumulator 23 on the suction side of the compressor 21 are connected and the discharge side of the compressor 21 is connected.
- the decompression circuit 28 are connected.
- Outdoor heat exchange is a heat exchanger that can function as a refrigerant evaporator and a refrigerant condenser, and in this embodiment, a cross-fin type fin that exchanges heat with the refrigerant using air as a heat source. 'And' tube type heat exchange.
- the outdoor heat exchanger 22 has its gas side connected to the four-way selector valve VI and its liquid side connected to the first liquid refrigerant communication pipe 51.
- the outdoor expansion valve V2 is an electric expansion valve connected to the liquid side of the outdoor heat exchange 22 in order to adjust the pressure and flow rate of the refrigerant flowing in the outdoor refrigerant circuit 20.
- the outdoor unit 2 has an outdoor fan 25 as a blower fan for sucking outdoor air into the unit, exchanging heat with the refrigerant in the outdoor heat exchanger 22, and then discharging the air outside.
- This outdoor fan 25 is a fan that can vary the air volume Wo supplied to the outdoor heat exchanger ⁇ 22.
- the outdoor fan 25 is a propeller fan or the like driven by a motor 25a that also has a DC fan motor power. is there.
- the accumulator 23 is connected between the four-way selector valve VI and the compressor 21, and removes excess refrigerant generated in the refrigerant circuit 10 in accordance with fluctuations in the operating load of the indoor units 3a to 3c. It is a container that can be stored.
- the accumulator 23 is connected to the connection units 4a to 4c via the low-pressure gas side closing valve V6 and the low-pressure gas refrigerant communication pipe 53.
- the supercooler 24 is a double-pipe heat exchanger, and is provided to cool the refrigerant that is condensed in the outdoor heat exchanger 22 and then sent to the indoor expansion valves V9a to V9c. It has been.
- the supercooler 24 is connected between the outdoor expansion valve V2 and the liquid side closing valve V4.
- a second bypass refrigerant circuit 6 is provided as a cooling source for the subcooler 24.
- the part of the refrigerant circuit 10 excluding the second bypass refrigerant circuit 6 will be referred to as the main refrigerant circuit for convenience.
- the second bypass refrigerant circuit 6 includes a compressor 21 that branches a part of the refrigerant sent from the outdoor heat exchanger 22 to the indoor expansion valves V9a to V9c via the connection units 4a to 4c. It is connected to the main refrigerant circuit so as to return to the suction side. Specifically, the second bypass refrigerant circuit 6 uses the outdoor heat exchanger and the subcooler 24 to transfer a part of the refrigerant sent from the outdoor expansion valve V2 to the indoor expansion valves V9a to V9c via the connection units 4a to 4c.
- the branch circuit 61 connected so as to branch the position force between the compressor 21 and the second bypass refrigerant circuit 6 side of the subcooler 24, and the compressor 21 so as to return to the suction side of the compressor 21.
- a junction circuit 62 connected to the suction side.
- the branch circuit 61 is provided with a bypass expansion valve V7 for adjusting the flow rate of the refrigerant flowing through the second bypass refrigerant circuit 6.
- the bypass expansion valve V7 also has an electric expansion valve force.
- the refrigerant sent from the outdoor heat exchanger 22 to the indoor expansion valves V9a to V9c through the connection units 4a to 4c is second bypassed after being depressurized by the bypass expansion valve V7 in the supercooler 24. Cooled by the refrigerant flowing through the refrigerant circuit 6. That is, the capacity of the subcooler 24 is controlled by adjusting the opening of the bypass expansion valve V7.
- the first bypass refrigerant circuit 27 bypasses the piping between the high pressure gas side closing valve V5 and the discharge side of the compressor 21 and the piping between the low pressure gas side closing valve V6 and the accumulator 23. There is a circuit. On the first bypass refrigerant circuit 27, a first bypass on-off valve V3 is provided.
- the first bypass on-off valve V3 is composed of an electromagnetic valve capable of circulating and blocking the refrigerant.
- the decompression circuit 28 has a capillary tube C 1 and is connected to the four-way selector valve VI and the accumulator 23.
- Liquid side shutoff valve V4, high pressure gas side shutoff valve V5, and low pressure gas side shutoff valve V6 are external devices and pipes (specifically, first liquid refrigerant communication pipe 51, high pressure gas refrigerant communication pipe 52, and low pressure gas It is a valve provided at the connection port with the gas refrigerant communication pipe 53).
- the liquid side shut-off valve V4 is connected to the outdoor heat exchange via the supercooler 24 and the outdoor expansion valve V2.
- the high-pressure gas side shut-off valve V5 is connected to the discharge side of the compressor 21.
- the low-pressure gas side closing valve V6 is connected to the suction side of the compressor 21 via the accumulator 23.
- the first high-pressure gas on-off valve V8 is provided on a pipe on the high-pressure gas side where the discharge-side force of the compressor 21 is also branched, and is capable of flowing and blocking the high-pressure gas refrigerant to the high-pressure gas refrigerant communication pipe 52. Valve force.
- the outdoor unit 2 is provided with various sensors. Specifically, the outdoor unit 2 includes a suction pressure sensor P1 that detects the suction pressure Ps of the compressor 21, a discharge pressure sensor P2 that detects the discharge pressure Pd of the compressor 21, and the compressor 21. A suction temperature sensor T1 for detecting the suction temperature Ts and a discharge temperature sensor T2 for detecting the discharge temperature Td of the compressor 21 are provided. The suction temperature sensor T1 is provided at a position between the accumulator 23 and the compressor 21.
- the outdoor heat exchanger 22 has a heat exchange temperature for detecting the temperature of the refrigerant flowing in the outdoor heat exchanger 22 (that is, the refrigerant temperature corresponding to the condensation temperature Tc during cooling operation or the evaporation temperature Te during heating operation).
- a liquid side temperature sensor T4 for detecting the refrigerant temperature Tco is provided on the liquid side of the outdoor heat exchanger 22.
- a liquid pipe temperature sensor T5 for detecting the temperature of the refrigerant (that is, the liquid pipe temperature Tip) is provided at the outlet of the subcooler 24 on the main refrigerant circuit side.
- An outdoor temperature sensor T6 for detecting the temperature of the outdoor air flowing into the unit (that is, the outdoor temperature Ta) is provided on the outdoor air inlet side of the outdoor unit 2.
- the junction circuit 62 of the second bypass refrigerant circuit 6 is provided with a binos temperature sensor T7 for detecting the temperature of the refrigerant flowing through the outlet of the subcooler 24 on the second bypass refrigerant circuit 6 side.
- the high-pressure gas pipe between the high-pressure gas side closing valve V5 and the first high-pressure gas on / off valve V8 has a first high-pressure gas pipe temperature sensor T8 that detects the refrigerant temperature (that is, the first high-pressure gas pipe temperature Thl).
- suction temperature sensor Tl, discharge temperature sensor ⁇ 2, heat exchange temperature sensor ⁇ 3, liquid side temperature sensor ⁇ 4, liquid pipe temperature sensor ⁇ 5, outdoor temperature sensor ⁇ 6, bypass temperature sensor ⁇ 7, and first high pressure gas piping temperature Sensor 8 is also a thermistor.
- the outdoor unit 2 also has an outdoor control unit 26 that controls the operation of each unit constituting the outdoor unit 2.
- the outdoor control unit 26 includes a microcomputer provided to control the outdoor unit 2, a memory, an inverter circuit that controls the motor 21a, and the like. Control signals and the like are exchanged between the indoor side control units 34a to 34c of the indoor units 3a to 3c and the connection side control units 44a to 44c of the connection units 4a to 4c described later via the transmission line 8a. Is getting ready to do. That is, the control unit that controls the overall operation of the air conditioner 1 by the indoor side control units 34a to 34c, the connection side control units 44a to 44c, the outdoor side control unit 26, and the transmission line 8a that connects the control units. 8 is configured.
- the control unit 8 can receive detection signals from various sensors PI, P2, T1 to T8, T9a to T9c, Tl Oa to T10c, Tl la to Tl lc, and T12a to T12c.
- Various devices and valves 21, 25, 32a to 32c, V1 to V3, V7, V8, V9a to V9c, V10a to V10c, Vl la to Vl lc, V12a ⁇ Vl 2c, VI 3a ⁇ Vl 3c are connected so that they can be controlled.
- the control unit 8 is connected to a warning display unit 9 that also has a LED force for notifying that a refrigerant leak has been detected in the refrigerant leak detection operation described later.
- FIG. 2 is a control block diagram of the air conditioner 1.
- connection units 4a to 4c are installed together with the indoor units 3a to 3c in a room such as a building.
- the connection units 4a to 4c, together with the first refrigerant communication pipe group 5 and the second refrigerant communication pipe group 7, are interposed between the indoor units 3a to 3c and the outdoor unit 2, and constitute a part of the refrigerant circuit 10. It is made.
- connection unit 4a to 4c Since the connection unit 4a and the connection units 4b and 4c have the same configuration, only the configuration of the connection unit 4a will be described here, and the configuration of the connection unit 4b and 4c will be described in each part of the connection unit 4a.
- the symbols Yb and Yc are used instead of the symbols Ya, and descriptions of each part are omitted.
- the subcooler 41a of the connection unit 4a corresponds to the subcoolers 41b and 41c of the connection units 4b and 4c.
- connection unit 4a forms part of the refrigerant circuit 10 and includes a connection-side refrigerant circuit 40a.
- the connection-side refrigerant circuit 40a mainly includes a supercooler 41a, a decompression circuit 42a, a third no-pass refrigerant circuit 43a, a low pressure gas on / off valve V10a, and a second high pressure gas on / off valve VI la.
- the subcooler 41a sends a part of the liquid refrigerant returned to the first liquid refrigerant communication pipe 51 to the supercooler 41a through the decompression circuit 42a described later when the indoor units 3a to 3c perform the cooling and heating simultaneous operation.
- a part of the liquid refrigerant introduced into the supercooler 41a evaporates by heat exchange and returns to the outdoor refrigerant circuit 20 through the low-pressure gas refrigerant communication pipe 53.
- a pressure reducing circuit opening / closing valve VI 2a and a capillary tube C2a are connected in series.
- the third bypass refrigerant circuit 43a is a circuit that bypasses the high-pressure gas refrigerant communication pipe 52 and the low-pressure gas refrigerant communication pipe 53.
- a second bypass on-off valve VI 3a is provided on the third binos refrigerant circuit 43a.
- the second bypass on-off valve VI 3a is an electromagnetic valve capable of circulating and blocking the refrigerant.
- the low-pressure gas on-off valve VlOa is connected to the low-pressure gas refrigerant communication pipe 53, and is an electromagnetic valve capable of flowing and blocking refrigerant.
- the second high-pressure gas on-off valve VI la is an electromagnetic valve that is connected to the high-pressure gas refrigerant communication pipe 52 and can flow and shut off the refrigerant.
- connection unit 4a opens the low-pressure gas on-off valve V10a and closes the second high-pressure gas on-off valve VIla.
- the connection unit 4a sends the liquid refrigerant flowing in from the first liquid refrigerant communication pipe 51 to the indoor expansion valve V9a of the indoor refrigerant circuit 30a, and is depressurized by the indoor expansion valve V9a, in the indoor heat exchanger 31a. It can function to return the evaporated gas refrigerant to the low-pressure gas refrigerant communication pipe 53.
- connection unit 4a closes the low-pressure gas on-off valve VlOa and opens the second high-pressure gas on-off valve VIla.
- the connection unit 4a sends the high-pressure gas refrigerant flowing in from the high-pressure gas refrigerant communication pipe 52 to the gas side of the indoor heat exchanger 31a in the indoor refrigerant circuit 30a, and V is supplied to the indoor heat exchanger 31a.
- the condensed liquid refrigerant can function to return to the first liquid refrigerant communication pipe 51.
- connection unit 4a is provided with a second high-pressure gas pipe temperature sensor T12a for detecting the temperature of the refrigerant (that is, the second high-pressure gas pipe temperature Th2) on the high-pressure gas refrigerant flow path.
- the second high-pressure gas pipe temperature sensor Tl 2a is also a thermistor.
- the connection unit 4a is a connection that controls the operation of each part constituting the connection unit 4a.
- a side control unit 44a is provided.
- the connection-side control unit 44a includes a microcomputer and a memory provided to control the connection unit 4a, and exchanges control signals and the like with the indoor-side control unit 34a of the indoor unit 3a. It is getting ready to be done.
- the outdoor refrigerant circuit 20 and the indoor refrigerant circuits 30a to 30c are connected via the connection refrigerant circuits 40a to 40c, so that the refrigerant circuit 10 of the air conditioner 1 is configured. Speak.
- the air conditioner 1 of the present embodiment for example, it is possible to perform a so-called cooling / heating simultaneous operation such that the indoor unit 3c performs a cooling operation while the indoor unit 3a performs a cooling operation. ing.
- the first refrigerant communication pipe group 5 and the second refrigerant communication pipe group 7 are refrigerant pipes that are installed on site when the air conditioner 1 is installed at the installation location such as a building. Those with various lengths and pipe diameters are used according to the installation conditions such as the combination of the indoor unit and the connecting unit. For this reason, for example, when a new air conditioner 1 is installed, the length of the first refrigerant communication pipe group 5 and the second refrigerant communication pipe group 7 may be used to calculate the refrigerant charge amount. However, the information management is complicated. When the existing unit is used to update an indoor unit, an outdoor unit or a connection unit, the length of the first refrigerant communication pipe group 5 and the second refrigerant communication pipe group 7 can be Information may be lost.
- the indoor refrigerant circuits 30a to 30c, the outdoor refrigerant circuit 20, the connection refrigerant circuits 40a to 40c, the first refrigerant communication pipe group 5, and the second refrigerant communication pipe group 7 The refrigerant circuit 10 of the air conditioner 1 is configured by being connected.
- the refrigerant circuit 10 is composed of the second bypass refrigerant circuit 6 and the main refrigerant circuit excluding the second bypass refrigerant circuit 6.
- the air conditioner 1 according to the present embodiment includes the control unit 8 including the indoor side control units 34a to 34c, the connection side control units 44a to 44c, and the outdoor side control unit 26.
- the switching valve VI and the first high-pressure gas on-off valve V8 and the low-pressure gas on-off valve VlOa and the second high-pressure gas on-off valve Vila in the connection units 4a to 4c are used to switch between cooling operation, heating operation, and simultaneous cooling / heating operation.
- the outdoor unit 2, the indoor units 3a to 3c, and the connection unit are connected according to the operation load of each indoor unit 3a to 3c. It is now possible to control each device of G 4a ⁇ 4c!
- the components of the outdoor unit 2, the indoor units 3a to 3c, and the connection units 4a to 4c are controlled according to the operation load of each indoor unit 3a to 3c.
- Normal operation mode and after installation of components of the air conditioner 1 Specifically, not limited to after installation of the first device, for example after modification or addition of components such as indoor units (Including after repairing the malfunction of the test) and the test run mode for performing the test operation, and after the test run is finished and the normal operation is started, whether or not the refrigerant leaks from the refrigerant circuit 10 is determined.
- the outdoor unit 2 In the normal operation mode, mainly the cooling operation for cooling all the indoor units 3a to 3c according to the cooling / heating load of the indoor units 3a to 3c, and all the Indoor unit 3a Heating and heating operation for performing the 3c, while part of the indoor unit 3a ⁇ 3c performs the cooling operation other indoor units are included and simultaneous heating and cooling operation for performing heating operation.
- the outdoor heat exchanger 22 of the outdoor unit 2 functions as an evaporator due to the air conditioning load of the entire indoor units 3a to 3c (evaporation operation state)
- the outdoor unit It can be divided into the case where the outdoor heat exchanger 22 of unit 2 is operated by functioning as a condenser (condensation operation state).
- the cooling and heating simultaneous operation mentioned here is specifically an operation in which the indoor unit 3a performs the cooling operation and the remaining indoor units 3b and 3c perform the heating operation, for example.
- the automatic refrigerant charging operation for charging the refrigerant into the refrigerant circuit 10
- the piping for detecting the volumes of the first refrigerant communication pipe group 5 and the second refrigerant communication pipe group 7.
- the volume determination operation and the initial refrigerant amount detection operation for detecting the initial refrigerant amount after the constituent devices are installed or after the refrigerant circuit 10 is filled with the refrigerant are included.
- the four-way switching valve VI is switched to the state shown by the solid line in FIG. 1 so that the outdoor heat exchange functions as a condenser. .
- the outdoor expansion valve V2 is fully opened.
- the liquid side closing valve V4, the high pressure gas side closing valve V5, and the low pressure gas side closing valve V6 are opened, and the first high pressure gas on / off valve V8 is closed.
- the indoor expansion valves V9a to V9c have a refrigerant superheat degree SHr at the outlets of the indoor heat exchangers 31a to 31c (that is, the gas side of the indoor heat exchangers 31a to 31c).
- the opening degree is adjusted to be constant at the superheat target value SHrs!
- the degree of superheat S Hr of the refrigerant at the outlets of the indoor heat exchangers 31a to 31c is also detected by the liquid temperature sensors T9a to T9c as the refrigerant temperature value detected by the gas side temperature sensors T10a to T10c.
- the refrigerant temperature value detected by the gas side temperature sensors T10a to Tl Oc is detected by subtracting the saturation temperature value of the refrigerant.
- a temperature sensor that detects the temperature of the refrigerant flowing in each of the indoor heat exchangers 31 a to 31 C is provided, and the refrigerant corresponding to the evaporation temperature Te detected by this temperature sensor a temperature value, by subtracting the refrigerant temperature value force is detected by the gas side temperature sensor T10a ⁇ T10c, Yo is also possible to detect the degree of superheat SHr of the refrigerant definitive the outlet of the indoor heat exchange 31 a to 31 C ⁇ .
- the opening degree of the bypass expansion valve V7 is adjusted so that the superheat degree SHb of the refrigerant at the outlet of the second bypass refrigerant circuit 6 side of the supercooler 24 becomes the superheat degree target value SHbs. It has been.
- the superheat degree SHb of the refrigerant at the outlet of the second bypass refrigerant circuit 6 side of the supercooler 24 is obtained by changing the suction pressure Ps of the compressor 21 detected by the suction pressure sensor P1 to the evaporation temperature Te. It is detected by converting to a corresponding saturation temperature value and subtracting the saturation temperature value of the refrigerant from the refrigerant temperature value detected by the bypass temperature sensor T7.
- the second bypass refrigerant circuit 6 of the supercooler 24 6 The second bypass refrigerant circuit 6 side of the subcooler 24 is provided by subtracting the refrigerant temperature value detected by the bypass temperature sensor T7 from the refrigerant temperature value detected by the temperature sensor.
- the superheat degree SHb of the refrigerant at the outlet of the refrigerant may be detected.
- connection units 4a to 4c the second high pressure gas on / off valves Vlla to Vllc are closed and the low pressure gas on / off valves V10a to V10c are opened.
- the indoor heat exchangers 31a to 31c of the indoor units 3a to 3c function as an evaporator, and the indoor heat exchangers 31a to 31c of the indoor units 3a to 3c and the suction side of the compressor 21 of the outdoor unit 2 Are connected via the low-pressure gas refrigerant communication pipe 53. Further, the pressure reducing circuit on / off valves V12a to V12c are closed.
- the low-pressure gas refrigerant is sucked into the compressor 21 and compressed to become a high-pressure gas refrigerant.
- the high-pressure gas refrigerant is sent to the outdoor heat exchanger 22 via the four-way switching valve VI, and is condensed by exchanging heat with the outdoor air supplied by the outdoor fan 25. It becomes.
- this high-pressure liquid refrigerant passes through the outdoor expansion valve V2, flows into the supercooler 24, and is further cooled by exchanging heat with the refrigerant flowing through the second bypass refrigerant circuit 6, and enters a supercooled state. Become.
- a part of the high-pressure liquid refrigerant condensed in the outdoor heat exchange 22 is branched into the second bypass refrigerant circuit 6, and after being reduced by the bypass expansion valve V7, is returned to the suction side of the compressor 21. It is.
- a part of the refrigerant passing through the bypass expansion valve V7 is evaporated by being reduced to near the suction pressure Ps of the compressor 21.
- the refrigerant flowing from the bypass expansion valve V7 of the second bypass refrigerant circuit 6 toward the suction side of the compressor 21 also passes through the subcooler 24 and passes through the outdoor heat exchanger 22 on the main refrigerant circuit side to the room. Heat exchange is performed with the high-pressure liquid refrigerant sent to the units 3a to 3c.
- the high-pressure liquid refrigerant in a supercooled state is sent to the indoor units 3a to 3c via the liquid side closing valve V4, the first liquid refrigerant communication pipe 51, and the connection units 4a to 4c. .
- the high-pressure liquid refrigerant sent to the indoor units 3a to 3c is reduced to near the suction pressure Ps of the compressor 21 by the indoor expansion valves V9a to V9c, and becomes a low-pressure gas-liquid two-phase refrigerant.
- 31a ⁇ 31c heat exchange with room air in indoor heat exchange ⁇ 31a ⁇ 31c And evaporates into a low-pressure gas refrigerant.
- the low-pressure gas refrigerant is sent to the low-pressure gas refrigerant communication pipe 53 through the low-pressure gas on / off valves V10a to V10c of the connection units 4a to 4c.
- This low-pressure gas refrigerant is sent to the outdoor unit 2 via the low-pressure gas refrigerant communication pipe 53 and flows into the accumulator 23 through the low-pressure gas side closing valve V6.
- the low-pressure gas refrigerant that has flowed into the accumulator 23 is again sucked into the compressor 21.
- the four-way switching valve VI is switched to the state shown by the broken line in FIG. 1 so that the outdoor heat exchange functions as an evaporator and the high-pressure gas refrigerant.
- the high-pressure gas refrigerant compressed and discharged by the compressor 21 is supplied to the indoor units 3a to 3c through the connecting pipe 52.
- the outdoor expansion valve V2 is adjusted in opening degree to reduce the refrigerant flowing into the outdoor heat exchanger 22 to a pressure at which the refrigerant can be evaporated in the outdoor heat exchanger 22 (that is, the evaporation pressure Pe).
- the liquid side closing valve V4, the high pressure gas side closing valve V5, and the low pressure gas side closing valve V6 are opened, and the bypass expansion valve V7 and the first high pressure gas on / off valve V8 are opened.
- the indoor expansion valves V9a to V9c are supercooled by the refrigerant supercooling degree S Cr at the outlets of the indoor heat exchangers 31a to 31c (that is, the liquid side of the indoor heat exchangers 31a to 31c).
- the degree of opening is adjusted to be constant at the target value SCrs!
- the degree of refrigerant supercooling SCr at the outlets of the indoor heat exchangers 31a to 31c is converted to the saturation temperature value corresponding to the condensation temperature Tc by converting the discharge pressure Pd of the compressor 21 detected by the discharge pressure sensor P2.
- the refrigerant is detected by subtracting the refrigerant temperature value detected by the saturation temperature value power liquid temperature sensor T9a to T9c.
- a temperature sensor is provided for detecting the temperature of the refrigerant flowing in each of the indoor heat exchangers 31a to 31c, and corresponds to the condensation temperature Tc detected by this temperature sensor.
- the subcooling degree SCr of the refrigerant at the outlets of the indoor heat exchangers 31a to 31c may be detected by subtracting the refrigerant temperature value from the liquid temperature sensors T9a to T9d. .
- connection units 4a to 4c when the low pressure gas on / off valves V10a to V10c are closed and the second high pressure gas on / off valves Vl la to Vl lc are opened, the indoor heat exchangers of the indoor units 3a to 3c 31a-31c will be in the state which functions as a condenser. Further, the pressure reducing circuit on / off valves V12a to V12c are in an open state.
- the low-pressure gas refrigerant is sucked into the compressor 21 and compressed to become a high-pressure gas refrigerant. It is sent to the high-pressure gas refrigerant communication pipe 52 via the switching valve VI and the high-pressure gas side closing valve V5.
- the high-pressure gas refrigerant sent to the high-pressure gas refrigerant communication pipe 52 is sent to the connection units 4a to 4c.
- the high-pressure gas refrigerant sent to the connection units 4a to 4c is sent to the indoor units 3a to 3c through the second high-pressure gas on / off valves Vl la to Vl lc.
- the high-pressure gas refrigerant sent to the indoor units 3a to 3c is subjected to heat exchange with indoor air in the indoor heat exchangers 31a to 31c to be condensed into high-pressure liquid refrigerant, and then the indoor expansion valve V9a to When passing through V9c, the pressure is reduced according to the opening of the indoor expansion valves V9a to V9c.
- the refrigerant that has passed through the indoor expansion valves V9a to V9c is sent to the subcoolers 41a to 41c of the connection units 4a to 4c.
- This supercooled refrigerant liquid is sent to the outdoor unit 2 via the first liquid refrigerant communication pipe 51, and further reduced in pressure via the liquid side closing valve V4 and the outdoor expansion valve V2, and then outdoor. It flows into the heat exchanger 22.
- the low-pressure gas-liquid two-phase refrigerant flowing into the outdoor heat exchanger 22 exchanges heat with the outdoor air supplied by the outdoor fan 25 to evaporate into a low-pressure gas refrigerant.
- the low-pressure gas refrigerant that has flowed into the accumulator 23 is again sucked into the compressor 21.
- the indoor unit 3a is in a cooling operation and the indoor units 3b and 3c are in a heating / cooling simultaneous operation, depending on the air conditioning load of the entire indoor units 3a to 3c.
- An operation for causing the outdoor heat exchange of the outdoor unit 2 to function as an evaporator (evaporation operation) will be described.
- the four-way switching valve V 1 is switched to the state indicated by the broken line in FIG.
- the high-pressure gas refrigerant compressed and discharged in the compressor 21 is supplied to the two indoor units 3b and 3c that function as a generator and are heated through the high-pressure gas refrigerant communication pipe 52.
- the bypass expansion valve V7 is closed, and the first high-pressure gas on-off valve V8 is open.
- the indoor expansion valve V9a is, for example, the degree of superheat of the indoor heat exchanger 31a (specifically, the refrigerant temperature detected by the liquid side temperature sensor T9a and the gas side temperature sensor TlOa).
- the degree of opening is adjusted according to the cooling load of the indoor unit 3a, such as by adjusting the degree of opening based on the temperature difference from the refrigerant temperature.
- connection unit 4a the second high pressure gas on / off valve VIla is closed and the low pressure gas on / off valve VlOa is opened.
- a compressor 2 1 a suction side of the indoor heat ⁇ 31a and the outdoor unit 2 of the indoor unit 3a is a low-pressure gas refrigerant communication pipe 53 Connected.
- the pressure reducing circuit on-off valve V12a is in a closed state.
- the indoor expansion valves V9b and V9c have a refrigerant supercooling degree SCr at the outlet of the indoor heat exchangers 3 lb and 31c (that is, the liquid side of the indoor heat exchangers 31b and 31c).
- the degree of opening is adjusted to be constant at the supercooling degree target value SCrs! /
- connection units 4b and 4c the low pressure gas on / off valves VlOb and VlOc are closed and the second high pressure gas on / off valves VI lb and Vl lc are opened.
- the indoor heat exchanges 31b and 31c of the indoor units 3b and 3c function as a condenser.
- the pressure reducing circuit on / off valves V12b and V12c are in an open state.
- the high-pressure gas refrigerant compressed and discharged by the compressor 21 is sent to the high-pressure gas refrigerant communication pipe 52 through the high-pressure gas side closing valve V5.
- the high-pressure gas refrigerant sent to the high-pressure gas refrigerant communication pipe 52 is sent to the indoor units 3b and 3c through the connection units 4b and 4c and the second high-pressure gas on / off valves VI lb and Vl lc.
- the high-pressure gas refrigerant sent to the indoor units 3b and 3c exchanges heat with indoor air in the indoor heat exchangers 31b and 31c to condense into a high-pressure liquid refrigerant, and then the indoor expansion valve When passing through V9b and V9c, the pressure is reduced according to the opening of the indoor expansion valves V9b and V9c. .
- room air is heated and supplied indoors.
- the refrigerant that has passed through the indoor expansion valves V9b and V9c is sent to the subcoolers 41b and 4lc of the connection units 4b and 4c to be supercooled.
- the supercooled refrigerant liquid is sent to the first liquid refrigerant communication pipe 51, and a part of the liquid refrigerant sent to the first liquid refrigerant communication pipe 51 is sent to the connection unit 4a. Then, the refrigerant sent to the connection unit 4a is sent to the indoor expansion valve V9a of the indoor unit 3a.
- the refrigerant sent to the indoor expansion valve V9a is decompressed by the indoor expansion valve V9a and then evaporated by exchanging heat with indoor air in the indoor heat exchanger 31a to become a low-pressure gas refrigerant.
- room air is cooled and supplied indoors. Then, the low-pressure gas refrigerant is sent to the connection unit 4a.
- the low-pressure gas refrigerant sent to the connection unit 4a is sent to the outdoor unit 2 through the low-pressure gas on-off valve V 1 Oa and the low-pressure gas refrigerant communication pipe 53, and via the low-pressure gas side shut-off valve V6. It flows into the accumulator 23. Then, the low-pressure gas refrigerant flowing into the accumulator 23 is sucked into the compressor 21 again.
- the remaining refrigerant excluding the refrigerant sent from the first liquid refrigerant communication pipe 51 to the connection unit 4a and the indoor unit 3a is sent to the outdoor heat exchanger 22 through the liquid side shut-off valve V4 of the outdoor unit 2. And is evaporated in the outdoor heat exchanger 22 to become a low-pressure gas refrigerant. This gas refrigerant is sucked into the compressor 21 via the four-way selector valve VI and the accumulator 23.
- the indoor units 3a to 3c for example, in the cooling and heating simultaneous operation mode in which the indoor units 3a and 3b are cooled and the indoor unit 3c is heated, depending on the air conditioning load of the entire indoor units 3a to 3c,
- the operation (condensation operation) that allows the outdoor heat exchange of the outdoor unit 2 to function as a condenser will be described.
- the four-way switching valve VI is switched to the state shown by the solid line in FIG. 1 so that the outdoor heat exchange functions as a condenser and the compressor 21 is connected to the indoor unit 3c through the high-pressure gas refrigerant communication pipe 52.
- the high-pressure gas refrigerant compressed and discharged in is supplied.
- the indoor expansion valves V9a and V9b are, for example, the degree of superheat of the indoor heat exchangers 31a and 31b (specifically, the refrigerant temperatures detected by the liquid side temperature sensors T9a and T9b).
- the opening degree is adjusted according to the cooling load of each indoor unit 3a, 3b, for example, the opening degree is adjusted based on the temperature and the temperature difference between the refrigerant temperature detected by the gas side temperature sensors TlOa, TlOb).
- connection units 4a and 4b the second high pressure gas on / off valves VIla and Vl lb are closed and the low pressure gas on / off valves VlOa and VlOb are opened.
- the indoor heat exchanges 31 & , 3 lb of the indoor units 3a, 3b function as an evaporator, and the indoor heat exchange ⁇ 31a, 31b of the indoor units 3a, 3b and the suction side of the compressor 21 of the outdoor unit 2 And are connected via a low-pressure gas refrigerant communication pipe 53. Further, the pressure reducing circuit on / off valves V12a and V12b are closed.
- the indoor expansion valve V9c is, for example, the degree of supercooling of the indoor heat exchanger 31c (specifically, the refrigerant temperature detected by the liquid side temperature sensor T9c and the gas side temperature sensor TlOc The opening degree is adjusted according to the heating load of the indoor unit 3c.
- connection unit 4c the low pressure gas on / off valve VlOc is closed and the second high pressure gas on / off valve Vl lc is opened.
- the indoor heat exchanger 31 C of the indoor unit 3c functions as a condenser.
- the pressure reducing circuit on-off valve V12c is in an open state.
- the high-pressure gas refrigerant compressed and discharged by the compressor 21 is sent to the outdoor heat exchange through the four-way switching valve VI and communicated with the high-pressure gas refrigerant through the high-pressure gas side closing valve V5. Also sent to pipe 52.
- the high-pressure gas refrigerant sent to the outdoor heat exchange is condensed in the outdoor heat exchange to become a liquid refrigerant. Then, the liquid refrigerant is sent to the first liquid refrigerant communication pipe 51 through the liquid side closing valve V4.
- the high-pressure gas refrigerant sent to the high-pressure gas refrigerant communication pipe 52 is sent to the connection unit 4c.
- the high-pressure gas refrigerant sent to the connection unit 4c is sent to the indoor heat exchanger 31c of the indoor unit 3c through the second high-pressure gas on / off valve Vl lc.
- the high-pressure gas refrigerant sent to the indoor heat exchanger 31c is condensed by exchanging heat with indoor air in the indoor heat exchanger 31c of the indoor unit 3c.
- indoor air It is heated and supplied indoors.
- the refrigerant condensed in the indoor heat exchanger 31c passes through the indoor expansion valve V9c and is then sent to the connection unit 4c.
- the refrigerant sent to the connection unit 4c is sent to the first liquid refrigerant communication pipe 51 and merged with the refrigerant sent to the first liquid refrigerant communication pipe 51 through the liquid-side closing valve V4.
- the refrigerant flowing through the first liquid refrigerant communication pipe 51 is sent to the indoor expansion valves V9a and V9b of the indoor units 3a and 3b via the connection units 4a and 4b.
- the low-pressure gas refrigerant sent to the connection units 4a and 4b is sent to the low-pressure gas refrigerant communication pipe 53 through the low-pressure gas on-off valves VlOa and VlOb.
- the low-pressure gas refrigerant sent through the low-pressure gas refrigerant communication pipe 53 is sucked into the compressor 21 via the low-pressure gas side closing valve V6 and the accumulator 23.
- control unit 8 (more specifically, the indoor side control units 34a to 34a functioning as normal operation control means for performing normal operation including cooling operation and heating operation).
- 34c connection side control units 44a to 44c, outdoor side control unit 26, and transmission lines 8a) connecting the control units 34a to 34c, 44a to 44c, 26.
- Fig. 3 is a flowchart of the test operation mode.
- the test operation mode first, the automatic refrigerant charging operation in step S1 is performed, then the pipe volume determination operation in step S2 is performed, and further, the initial refrigerant amount detection operation in step S3 is performed. .
- the outdoor unit 2 pre-filled with the refrigerant, the indoor units 3a to 3c, and the connection units 4a to 4c are installed at an installation location such as a building, and the first refrigerant communication pipe group 5 and the second cooling unit are installed.
- the refrigerant that is insufficient according to the volume of the first refrigerant communication pipe group 5 and the second refrigerant communication pipe group 7 is entered into the refrigerant circuit 10.
- Step SI Automatic refrigerant charging operation
- liquid side shut-off valve V4, the high-pressure gas side shut-off valve V5, and the low-pressure gas side shut-off valve V6 of the outdoor unit 2 are opened, and the refrigerant previously filled in the outdoor unit 2 is filled in the refrigerant circuit 10.
- FIG. 4 is a flowchart of the automatic refrigerant charging operation.
- Step S11 Refrigerant amount judgment operation
- the refrigerant circuit 10 When an instruction to start the automatic refrigerant charging operation is issued, the refrigerant circuit 10 is in a state where the four-way switching valve VI of the outdoor unit 2 is indicated by a solid line in FIG. 1 and the indoor expansion valves V9a to V9a to V9c, low pressure gas on / off valve V10a to V10c of connection unit 4a to 4c, and outdoor expansion valve V2 are open, the first high pressure gas on / off valve V8 of outdoor unit 2 and the second high pressure of connection unit 4a to 4c The gas on-off valves Vl la to Vl lc are closed, the compressor 21, the outdoor fan 25, and the indoor fans 32a to 32c are activated to forcibly cool all the indoor units 3a to 3c.
- the high-pressure gas refrigerant compressed and discharged by the compressor 21 is disposed in the flow path from the compressor 21 to the outdoor heat exchange functioning as a condenser.
- the outdoor heat exchanger 22 functioning as a condenser is in a gas state by heat exchange with the outdoor air.
- the high-pressure refrigerant that changes phase from liquid to liquid flows (see the hatched and black hatched areas in Fig.
- valve V9a to V9c outdoor expansion High-pressure liquid refrigerant flows through the valve V2, the part on the main refrigerant circuit side of the subcooler 24 and the first liquid refrigerant communication pipe 51
- the flow path from the outdoor heat exchanger 22 to the bypass expansion valve V7 (See the section from the outdoor heat exchanger 22 to the indoor expansion valves V9a to V9c and the bypass expansion valve V7 in the black hatched area in Fig.
- the portion of the indoor heat exchange 31a to 31c that functions as an evaporator And a portion of the subcooler 24 on the second bypass refrigerant circuit 6 side flows a low-pressure refrigerant that changes phase from a gas-liquid two-phase state to a gas state due to heat exchange with room air or the like (the lattice-like shape in FIG. 5).
- the indoor heat exchangers 31a to 3lc and the supercooler 24 in the flow path from the indoor heat exchangers 31a to 31c to the compressor 21,
- the high-pressure gas side and low-pressure gas side flow paths of the connection units 4a to 4c (the third bypass refrigerant circuit 43a to 43c
- the high-pressure gas refrigerant communication pipe 52, the low-pressure gas refrigerant communication pipe 53, the first bypass refrigerant circuit 27, and the flow path including the accumulator 23 and the second bypass refrigerant circuit 6 side partial pressure of the supercooler 24 are also included in the compressor.
- the low-pressure gas refrigerant flows through the flow path up to 21 (the hatched portion in Fig.
- FIG. 5 is the portion from the indoor heat exchangers 31a to 31c to the compressor 21 (the connection units 4a to 4c and the high-pressure Gas refrigerant communication pipe 52 and low-pressure gas refrigerant communication pipe 53), and the partial force on the second bypass refrigerant circuit 6 side of the supercooler 24 is also referred to the section up to the compressor 21).
- FIG. 5 is a schematic diagram showing the state of the refrigerant flowing in the refrigerant circuit 10 in the refrigerant quantity determination operation (illustration of the four-way switching valve VI and the like is omitted).
- the following device control is performed to shift to an operation for stabilizing the state of the refrigerant circulating in the refrigerant circuit 10.
- the indoor expansion valves V9a to V9c are controlled (hereinafter referred to as superheat control) so that the superheat degree SHr of the indoor heat exchanger 31 & ⁇ 31c functioning as an evaporator becomes constant, and the evaporation pressure Pe is
- the operating capacity of the compressor 21 is controlled so as to be constant (hereinafter referred to as evaporation pressure control), and the outdoor fan 25 exchanges the outdoor heat so that the refrigerant condensing pressure Pc in the outdoor heat exchanger 22 becomes constant.
- the subcooler controls the air volume Wo of the outdoor air supplied to the cooler 22 (hereinafter referred to as condensing pressure control) so that the temperature of the refrigerant sent from the supercooler 24 to the indoor expansion valves V9a to V9c is constant.
- condensing pressure control controls the air volume Wo of the outdoor air supplied to the cooler 22 so that the temperature of the refrigerant sent from the supercooler 24 to the indoor expansion valves V9a to V9c is constant.
- the indoor fans 32a to 32c Keep air volume Wr of room air supplied to ⁇ 31c constant.
- the evaporation pressure control is performed in the indoor heat exchangers 31a to 31c functioning as an evaporator in a gas-liquid two-phase state force by a heat exchange with room air, and a force that does not change into a gas state.
- Inside the indoor heat exchangers 31a to 31c through which the low-pressure refrigerant flows (refer to the portion corresponding to the indoor heat exchangers 31a to 31c in the grid-shaped hatched and hatched portions in FIG. 5;
- the amount of refrigerant in (1) is a force that greatly affects the evaporation pressure Pe of the refrigerant.
- the evaporating pressure Pe of the refrigerant in the indoor heat exchangers 31a to 31c is made constant, The state of the refrigerant flowing in the evaporator section C is stabilized. That is, a state in which the amount of refrigerant in the evaporator C changes mainly by the evaporation pressure Pe is created.
- the refrigerant temperature values (corresponding to the evaporation temperature Te) detected by the liquid side temperature sensors T9a to T9c of the indoor heat exchangers 31a to 31c are saturated.
- the operating capacity of the compressor 21 is controlled so that this pressure value becomes constant at the low pressure target value Pes (that is, control for changing the rotational speed Rm of the motor 2 la is performed). This is realized by increasing or decreasing the refrigerant circulation amount Wc flowing in the refrigerant circuit 10.
- the compressor 21 detected by the suction pressure sensor P1 which is an operation state quantity equivalent to the refrigerant pressure at the refrigerant evaporating pressure Pe in the force indoor heat exchangers 31a to 31c, is not employed in this embodiment.
- the operating capacity of the machine 21 may be controlled, and the refrigerant temperature value (corresponding to the evaporation temperature Te) detected by the liquid side temperature sensors T9a to T9c of the indoor heat exchangers 31a to 31c is the low pressure target value Tes.
- the operating capacity of the compressor 21 may be controlled so as to be constant.
- the refrigerant pipe including the low-pressure gas refrigerant communication pipe 53 and the accumulator 23 from the indoor heat exchangers 31a to 31c to the compressor 21 hatchched hatched lines in FIG. 5.
- the state of the refrigerant flowing through the indoor heat exchangers 31a to 31c to the compressor 21 (hereinafter referred to as gas refrigerant circulation part D) is also stable, mainly in the gas refrigerant circulation part D
- the amount of refrigerant in the gas refrigerant circulation section D is changed by the evaporation pressure Pe (that is, the suction pressure Ps), which is an operation state quantity equivalent to the refrigerant pressure. Create a state to become.
- Condensation pressure control is also performed in the outdoor heat exchanger ⁇ 22 in which high-pressure refrigerant flows while the gas state force changes to a liquid state due to heat exchange with the outdoor air (hatched hatched and blackened in Fig. 5).
- the condenser part A see the part corresponding to the outdoor heat exchanger 22 (hereinafter referred to as the condenser part A), and this is the force that greatly affects the refrigerant condensing pressure Pc.
- the condensation pressure Pc of the refrigerant in the condenser part A changes more greatly than the influence of the outdoor temperature Ta, by controlling the air volume Wo of the indoor air supplied from the outdoor fan 25 to the outdoor heat exchange by the motor 25a,
- the refrigerant condensing pressure Pc in the outdoor heat exchanger 22 is kept constant, and the state of the refrigerant flowing in the condenser section A is stabilized.
- the refrigerant in the condenser A is mainly controlled by the degree of supercooling SCo on the liquid side of the outdoor heat exchanger 22 (hereinafter referred to as the outlet of the outdoor heat exchanger 22 in the description of the refrigerant amount determination operation). It creates a state where the amount changes.
- the compressor 21 detected by the discharge pressure sensor P2 which is an operation state quantity equivalent to the refrigerant condensation pressure Pc in the outdoor heat exchanger 22, is used.
- the temperature of the refrigerant flowing through the outdoor heat exchanger 22 that is, the condensation temperature Tc detected by the heat exchange temperature sensor T3.
- the flow path from the outdoor heat exchange to the indoor expansion valves V9a to V9c (the outdoor expansion valve V2 and the part on the main refrigerant circuit side of the subcooler 24 and the first liquid refrigerant).
- High-pressure liquid refrigerant flows through the flow path from the outdoor heat exchanger 22 to the bypass expansion valve V7 of the second bypass refrigerant circuit 6 and the indoor expansion from the outdoor heat exchanger 22
- the pressure of the refrigerant in the parts up to the valves V9a to V9c and the bypass expansion valve V7 (refer to the black hatched part in FIG. 5, hereinafter referred to as the liquid refrigerant circulation part B) is also stable, and the liquid refrigerant circulation part B becomes liquid. It is sealed with the refrigerant and becomes stable.
- the liquid pipe temperature control is performed in the refrigerant pipe including the first liquid refrigerant communication pipe 51 extending from the supercooler 24 to the indoor expansion valves V9a to V9c (in the liquid refrigerant circulation section B shown in FIG. This is because the density of the refrigerant in the cooler 24 force also does not change! (Refer to the parts from the indoor expansion valve V9a to V9c).
- the capacity control of the subcooler 24 is performed by controlling the temperature Tip of the refrigerant detected by the liquid pipe temperature sensor T5 provided at the outlet of the main refrigerant circuit of the subcooler 24.
- the flow rate of the refrigerant flowing through the second bypass refrigerant circuit 6 is increased or decreased so that the liquid pipe temperature target value Tips is constant, and the refrigerant flowing through the main refrigerant circuit side of the subcooler 24 and the second bypass refrigerant circuit 6 side are adjusted. This is realized by adjusting the amount of heat exchanged with the flowing refrigerant.
- the flow rate of the refrigerant flowing through the second bypass refrigerant circuit 6 is increased or decreased by adjusting the opening of the bypass expansion valve V7. In this manner, liquid pipe temperature control is realized in which the refrigerant temperature in the refrigerant pipe including the first liquid refrigerant communication pipe 51 extending from the supercooler 24 to the indoor expansion valves V9a to V9c is constant.
- the refrigerant temperature Tco at the outlet of the outdoor heat exchanger 22 due to the increase in the amount of refrigerant caused by filling the refrigerant in the refrigerant circuit 10 (that is, excess refrigerant at the outlet of the outdoor heat exchanger 22).
- SCo degree of cooling
- the change in the refrigerant temperature Tco at the outlet of the outdoor heat exchanger 22 is caused by the refrigerant pipes from the subcooler 24 to the indoor expansion valves V9a to V9c including the first liquid refrigerant communication pipe 51 in the liquid refrigerant circulation part B. It will be in a state that does not affect.
- the superheat degree control is performed because the amount of refrigerant in the evaporator section C greatly affects the dryness of the refrigerant at the outlets of the indoor heat exchangers 31 & to 31c.
- the refrigerant superheat degree SHr at the outlets of the indoor heat exchangers 31a to 31c is controlled by controlling the opening degree of the indoor expansion valves V9a to V9c, so that the gas side of the indoor heat exchangers 31a to 31c (hereinafter referred to as refrigerant amount determination operation).
- the refrigerant superheat degree SHr is constant at the superheat degree target value SHrs (that is, the gas refrigerant at the outlets of the indoor heat exchangers 31a to 31c is superheated), The state of the refrigerant flowing through is stabilized.
- the state of the refrigerant circulating in the refrigerant circuit 10 is stabilized, and the distribution of the refrigerant amount in the refrigerant circuit 10 becomes constant.
- Refrigerant amount in the refrigerant circuit 10 when the refrigerant begins to be charged It is possible to create a state in which this change mainly appears as a change in the amount of refrigerant in the outdoor heat exchanger 22 (hereinafter, this operation is referred to as a refrigerant amount determination operation).
- control unit 8 (more specifically, the indoor side control units 34a to 34c, the connection side control units 44a to 44c, the outdoor side, which functions as a refrigerant amount determination operation control unit that performs the refrigerant amount determination operation.
- the control unit 26 and the transmission lines 8a) connecting the control units 34a to 34c, 44a to 44c, 26 perform the process of step S11.
- the constituent devices are abnormally stopped when performing the refrigerant amount determination operation described above prior to the processing of step S11. It is necessary to fill the refrigerant until the amount of refrigerant does not fall.
- step S12 additional refrigerant charging is performed in the refrigerant circuit 10 while performing the above-described refrigerant amount determination operation.
- the additional charging of the refrigerant in step S12 is performed by the control unit 8 functioning as the refrigerant amount calculating means.
- the refrigerant amount in the refrigerant circuit 10 is calculated from the refrigerant flowing through the refrigerant circuit 10 at the time or the operation state quantity of the component equipment.
- the refrigerant quantity calculating means calculates the refrigerant quantity in the refrigerant circuit 10 by dividing the refrigerant circuit 10 into a plurality of parts and calculating the refrigerant quantity for each of the divided parts. More specifically, for each of the divided parts, a relational expression between the refrigerant amount of each part and the operating state quantity of the refrigerant flowing through the refrigerant circuit 10 or the component device is set, and these relational expressions are used. Thus, the refrigerant amount of each part can be calculated.
- the refrigerant circuit 10 has a state in which the four-way switching valve VI is shown by the solid line in FIG.
- the discharge side of the compressor 21 is connected to the gas side of the outdoor heat exchanger 22, and
- the compressor 21 part and the compressor 21 The part up to the outdoor heat exchanger 22 (hereinafter referred to as the high pressure gas pipe part E) including the four-way switching valve V 1 (not shown in FIG.
- liquid refrigerant communication pipe part B3 The part that combines the liquid side refrigerant flow path and the second liquid refrigerant communication pipes 71a to 71c (hereinafter referred to as liquid refrigerant communication pipe part B3) and the liquid refrigerant distribution part B from the first liquid refrigerant communication pipe 51 to the room Part of the gas refrigerant circulation part D including the expansion valves V9a to V9c and the indoor heat exchangers 31a to 31c (i.e., the evaporator part C) up to the second gas refrigerant communication pipes 72a to 72c (hereinafter referred to as indoor units) Part F) and the high-pressure gas refrigerant communication pipe 52 in the gas refrigerant circulation part D and the high-pressure gas side refrigerant flow path (third bypass cooling in the connection units 4a to 4c).
- Part of the medium circuit 43a to 43c including the second bypass on-off valve VI 3a to V13c on the high pressure gas side (hereinafter referred to as the high pressure gas refrigerant communication pipe part G1) and the gas refrigerant circulation part D
- Low pressure gas refrigerant communication pipe 53 and second gas refrigerant communication pipe 72a to 72c and low pressure gas side refrigerant flow path in connection units 4a to 4c (second bypass on-off valve on the low pressure gas side of third bypass refrigerant circuits 43a to 43c VI 3a to Vl 3c) hereinafter referred to as low-pressure gas refrigerant communication pipe part G2
- gas refrigerant circulation part D high-pressure gas side shut-off valve V5 (not shown in FIG.
- First bypass refrigerant circuit 27 and first bypass refrigerant circuit 27 to four-way switching valve VI and first bypass refrigerant circuit 27 to ac The part including the compressor 23 including the mulator 23 (hereinafter referred to as the second low-pressure gas pipe part I) and the liquid refrigerant circulation part B from the high-temperature side liquid pipe part B1 to the bypass expansion valve V7 and the supercooler It is divided into parts near the second low-pressure gas pipe part (hereinafter referred to as second bypass circuit part J) including the part on the second bypass refrigerant circuit 6 side of 24, and a relational expression is set for each part.
- the combined portion of the high-pressure gas refrigerant communication pipe part G1 and the low-pressure gas refrigerant communication pipe part G2 is referred to as the gas refrigerant communication pipe part G.
- the relational expressions set for each part will be described.
- the relational expression between the refrigerant amount Mogl in the high-pressure gas pipe E and the operating state quantity of the refrigerant or the component device flowing through the refrigerant circuit 10 is, for example,
- Mogl Vogl X pd This is expressed as a functional expression obtained by multiplying the volume Vogl of the high-pressure gas pipe E of the outdoor unit 2 by the refrigerant density pd in the high-pressure gas pipe E.
- the volume Vogl of the high-pressure gas pipe E is a known value of the front force at which the outdoor unit 2 is installed at the installation location, and is stored in the memory of the control unit 8 in advance.
- the density of the refrigerant in the high-pressure gas pipe E can be obtained by converting the discharge temperature Td and the discharge pressure Pd.
- the relational expression between the refrigerant amount Mc in the condenser part A and the operation state quantity of the refrigerant flowing through the refrigerant circuit 10 or the component device is, for example,
- Mc kc l X Ta + kc2 X Tc + kc3 X SHm + kc4 X Wc
- the outdoor temperature Ta, the condensation temperature Tc, the compressor discharge superheat degree SHm, the refrigerant circulation rate Wc, the saturated liquid density pc of the refrigerant in the outdoor heat exchanger 22, and the refrigerant density p at the outlet of the outdoor heat exchanger 22 It is expressed as a function expression of co.
- the parameters kcl to kc7 in the above relational expression are obtained by regression analysis of the results of tests and detailed simulations, and are stored in the memory of the control unit 8 in advance.
- the compressor discharge superheat degree SHm is the refrigerant superheat degree on the discharge side of the compressor.
- the discharge pressure Pd is converted into the refrigerant saturation temperature value, and the discharge temperature Td force is subtracted from the refrigerant saturation temperature value.
- the saturated liquid density pc of the refrigerant can be obtained by converting the condensation temperature Tc.
- the refrigerant density p co at the outlet of the outdoor heat exchanger is obtained by converting the condensation pressure Pc obtained by converting the condensation temperature Tc and the refrigerant temperature Tco.
- the relational expression between the refrigerant amount Moll in the high temperature side liquid pipe part B1 and the operating state quantity of the refrigerant flowing through the refrigerant circuit 10 or the component device is, for example,
- the relational expression between the refrigerant amount Mol2 in the low temperature side liquid pipe part B2 and the operation state quantity of the refrigerant flowing through the refrigerant circuit 10 or the component device is, for example,
- t is expressed as a functional expression obtained by multiplying the volume Vol2 of the low temperature side liquid pipe portion B2 of the outdoor unit 2 by the refrigerant density p lp in the low temperature side liquid pipe portion B2.
- the volume Vol 2 of the low temperature side liquid pipe section B2 is also a known value of the front force at which the outdoor unit 2 is installed at the installation location, and is stored in the memory of the control section 8 in advance.
- the refrigerant density p lp in the low temperature side liquid pipe section B2 is the refrigerant density at the outlet of the subcooler 24, and is converted by converting the condensation pressure Pc and the refrigerant temperature Tip at the outlet of the subcooler 24. can get.
- the volume Vlp of the part that combines the first liquid refrigerant communication pipe 51 and the liquid side refrigerant flow paths of the connection units 4a to 4c and the second liquid refrigerant communication pipes 71a to 71c is added to the volume Vlp of the refrigerant in the liquid refrigerant communication pipe B3. It is expressed as a function equation multiplied by the density p lp (that is, the refrigerant density at the outlet of the supercooler 24).
- Vlp is the volume Vlp 1 of the portion where the first liquid refrigerant communication pipe 51 and the second liquid refrigerant communication pipes 71a to 71c are combined, and the volume Vlp 2 of the liquid side refrigerant flow path of the connection units 4a to 4c. It is divided into.
- the volume Vlpl of the first liquid refrigerant communication pipe 51 and the second liquid refrigerant communication pipes 71a to 71c combined is the air conditioner 1 between the first liquid refrigerant communication pipe 51 and the second liquid refrigerant communication pipes 71a to 71c. Because it is a refrigerant pipe that is installed at the site when installing the building at the installation location such as a building, the information power such as the pipe diameter is input.
- the information power of these input first liquid refrigerant communication pipes 51 and second liquid refrigerant communication pipes 71a to 71c is also calculated by the control unit 8, or as described later, It is calculated using the operation result of the volume determination operation. Further, the volume Vlp2 of the liquid side refrigerant flow path of the connection units 4a to 4c is a known value of the front force at which the connection units 4a to 4c are installed at the installation location, and is stored in the memory of the control unit 8 in advance. ing.
- Mr krl XTlp + kr2 X AT + kr3 X SHr + kr4 XWr + kr5
- the refrigerant temperature Tlp at the outlet of the supercooler 24, the temperature difference ⁇ obtained by subtracting the evaporation temperature Te from the room temperature Tr, the superheat degree SHr of the refrigerant at the outlet of the indoor heat exchangers 31a to 31c, and the indoor fans 32a to 32a It is expressed as a function expression of the air volume Wr of 32c.
- the parameters krl to kr5 in the above relational expression are obtained by regression analysis of the results of tests and detailed simulations, and are stored in the memory of the control unit 8 in advance.
- the relational expression of the refrigerant amount Mr is set corresponding to each of the three indoor units 3a to 3c, and the refrigerant amount Mr of the indoor unit 3a, the refrigerant amount Mr of the indoor unit 3b, and the indoor unit are set. By adding the refrigerant amount Mr of 3c, the total refrigerant amount of the indoor unit F is calculated.
- relational expressions having different values of the parameters krl to kr5 are used.
- the gas refrigerant communication pipe section G is divided into a high pressure gas refrigerant communication pipe section G1 and a low pressure gas refrigerant communication pipe section G2.
- the refrigerant amount Mgp in the gas refrigerant communication pipe section G is the refrigerant in the high pressure gas refrigerant communication pipe section G1. This is the sum of the amount Mgph and the amount of refrigerant Mgpl in the low-pressure gas refrigerant communication pipe section G2.
- the volume Vgp of the gas refrigerant communication pipe G is a value obtained by adding the volume Vgph of the high pressure gas refrigerant communication pipe G1 and the volume Vgpl of the low pressure gas refrigerant communication pipe G2.
- Vgp Vgph + Vgpl
- the relational expression between the refrigerant amount Mgph in the high-pressure gas refrigerant communication pipe section Gl and the operating state quantity of the refrigerant flowing through the refrigerant circuit 10 or the component equipment is, for example,
- Mgph Vgph X p gph
- the high-pressure gas refrigerant communication pipe 52 and the high-pressure gas-side refrigerant flow path in the connection units 4a to 4c (including the second bypass on-off valves V13a to V13c on the high-pressure gas side of the third bypass refrigerant circuits 43a to 43c) It is expressed as a function equation by multiplying the volume Vgph of the combined part by the density of refrigerant pgph in the high-pressure gas refrigerant communication pipe part G1.
- Vgph contacts high pressure gas refrigerant
- the volume Vgphl of the piping 52 and the volume Vgph2 of the high pressure gas side refrigerant flow path in the connection units 4a to 4c (including the second bypass open / close valves V13a to V13c on the high pressure gas side of the third bypass refrigerant circuits 43a to 43c) And divided.
- the volume Vgpl of the high-pressure gas refrigerant communication pipe 52 is the same as that of the first liquid refrigerant communication pipe 51 and the second liquid refrigerant communication pipes 71a to 71c.
- the refrigerant density p gph in the high-pressure gas refrigerant communication pipe section G1 is equal to the refrigerant density ps on the suction side of the compressor 21, the high-pressure gas side shut-off valve V5 and the first high-pressure gas on-off valve V8 in the outdoor unit 2.
- the refrigerant density p oh in the high-pressure gas side piping between the two, the refrigerant density p bsh in the high-pressure gas side refrigerant flow path in the connection units 4a to 4c, and the outlets of the indoor heat exchangers 31a to 31c (that is, This is the average value of the refrigerant density p eo in the second gas refrigerant communication pipes 72a to 72c).
- the refrigerant density ps is obtained by converting the suction pressure Ps and the suction temperature Ts.
- the density p oh of the refrigerant can be obtained by converting the first high pressure gas pipe temperature Thl.
- the density P bsh of the cooling medium can be obtained by converting the second high-pressure gas pipe temperature Th2.
- the density p eo of the refrigerant is obtained by converting the evaporation pressure Pe that is a conversion value of the evaporation temperature Te and the outlet temperature Teo of the indoor heat exchangers 31a to 31c.
- the volume Vgp2 of the high pressure gas side refrigerant flow path (including the second bypass on / off valves V13a to V13c on the high pressure gas side of the third bypass refrigerant circuits 43a to 43c) in the connection units 4a to 4c is -4c is a known value of the front force to be installed at the installation location, and is stored in the memory of the control unit 8 in advance.
- the relational expression between the refrigerant quantity Mgpl in the low-pressure gas refrigerant communication pipe section G2 and the operating state quantity of the refrigerant flowing through the refrigerant circuit 10 or the component equipment is, for example,
- the low-pressure gas refrigerant communication pipe 53, the second gas refrigerant communication pipe 72a to 72c, and the low-pressure gas side refrigerant flow path in the connection units 4a to 4c (the second bypass opening and closing on the low-pressure gas side of the third bypass refrigerant circuits 43a to 43c) The volume of the part combined with the valves VI 3a to Vl 3c) Vgpl It is expressed as a function equation multiplied by the refrigerant density p gpl in the refrigerant communication pipe section G2.
- Vgpl is the volume Vgpll of the portion of the low-pressure gas refrigerant communication pipe 53 and the second gas refrigerant communication pipes 72a to 72c, and the low-pressure gas side refrigerant flow path (third bypass refrigerant in the connection units 4a to 4c). This is divided into the volume Vgpl2 of the second bypass on-off valves V13a to V13c on the low pressure gas side of the circuits 43a to 43c.
- the volume of the part that combines the low pressure gas refrigerant communication pipe 53 and the second gas refrigerant communication pipe 72a to 72c Vgpll is the part that combines the first liquid refrigerant communication pipe 51 and the second liquid refrigerant communication pipe 71a to 71c and
- the low-pressure gas refrigerant communication pipe 53 and the second gas refrigerant communication pipes 72a to 72c are refrigerants that are installed on-site when the air conditioner 1 is installed in a building or other location. Since this is a pipe, input the value calculated locally based on the information such as the pipe diameter, or input the information such as the pipe diameter on the spot and input these low-pressure gas refrigerant communication pipes.
- the refrigerant density p gpl in the low pressure gas refrigerant communication pipe section G2 is equal to the refrigerant density ps on the suction side of the compressor 21 and the outlets of the indoor heat exchangers 31a to 31c (that is, the second gas refrigerant communication pipe). It is the average value of the refrigerant density p eo at the inlets 72a to 72c).
- the refrigerant density ps is obtained by converting the suction pressure Ps and the suction temperature Ts.
- the refrigerant density p eo is obtained by converting the evaporation pressure Pe and the indoor heat exchangers 31a to 31c, which are conversion values of the evaporation temperature Te. It is obtained by converting the outlet temperature Teo.
- the volume Vgpl2 of the low pressure gas side refrigerant flow path (including the second bypass open / close valves V13a to V13c on the low pressure gas side of the third bypass refrigerant circuits 43a to 43c) in the connection units 4a to 4c is connected to the connection unit 4a.
- ⁇ 4c is also a known value of the pre-installation force at the installation location, and is stored in the memory of the control unit 8 in advance.
- the relational expression between the refrigerant amount Mog2 in the first low-pressure gas pipe section H and the operating state quantity of the refrigerant flowing through the refrigerant circuit 10 or the component device is, for example,
- volume Vog2 of the first low-pressure gas pipe H in the outdoor unit 2 is expressed as a functional expression obtained by multiplying the volume Vog2 of the first low-pressure gas pipe H in the outdoor unit 2 by the refrigerant density poh in the first low-pressure gas pipe H.
- the volume Vog2 of the first low-pressure gas pipe section H is a known value of the pre-force that is shipped to the installation location, and is stored in advance in the memory of the control section 8. Is remembered.
- the relational expression between the amount of refrigerant Mog3 in the second low-pressure gas pipe part I and the operating state quantity of the refrigerant or the component device flowing through the refrigerant circuit 10 is, for example,
- volume Vog3 of the second low-pressure gas pipe section I in the outdoor unit 2 is expressed as a functional expression obtained by multiplying the volume Vog3 of the second low-pressure gas pipe section I in the outdoor unit 2 by the refrigerant density p s in the second low-pressure gas pipe section I.
- the volume Vog3 of the second low-pressure gas pipe section I has a known value for the pre-force shipped to the installation location, and is stored in the memory of the control section 8 in advance.
- Mob kobl X co + kob2 X ps + kob3 X Pe + kob4
- volume Vob of the second bypass circuit portion J is a known value before the outdoor unit 2 is installed at the installation location, and is stored in the memory of the control unit 8 in advance.
- the saturated liquid density pe in the portion of the subcooler 24 on the second bypass circuit side is obtained by converting the suction pressure Ps or the evaporation temperature Te.
- the amount of refrigerant related to the outdoor units Mogl, Mc, Moll, Mol2, Mog2, Mog3, and Mob is a cooler for each part corresponding to each of multiple outdoor units.
- the relational expression of the medium amount is set, and the total refrigerant amount of the outdoor unit is calculated by adding the refrigerant amount of each part of the plurality of outdoor units.
- the relational expression for the amount of refrigerant in each part with different meter values is used.
- the refrigerant flowing through the refrigerant circuit 10 in the refrigerant quantity judgment operation or the operating state quantity of the component device is calculated.
- the refrigerant amount of the refrigerant circuit 10 can be calculated.
- step S12 Since this step S12 is repeated until the condition for determining whether the refrigerant amount is appropriate in step S13, which will be described later, is satisfied, the refrigerant is charged until the additional charging of the refrigerant is started and the force is completed. Using the relational expression for each part of circuit 10, the amount of refrigerant in each part is calculated.
- the refrigerant amount Mo in the outdoor unit 2 is calculated by calculating the refrigerant amounts Mogl, Mc, Moll, Mol 2, Mog2, Mog3, and Mob of each part in the outdoor unit 2 described above. .
- control unit that functions as a refrigerant amount calculating means for calculating the refrigerant amount in each part of the refrigerant circuit 10 from the refrigerant flowing in the refrigerant circuit 10 or the operation state quantity of the constituent devices in the automatic refrigerant charging operation.
- step 8 the process of step S12 is performed.
- the refrigerant amount in the refrigerant circuit 10 gradually increases.
- the amount of refrigerant to be charged in the refrigerant circuit 10 after additional charging of the refrigerant may be defined as the refrigerant amount of the entire refrigerant circuit 10. Can not.
- the indoor units 3a to 3c, and the connection units 4a to 4c that is, the refrigerant circuit 10 excluding the first refrigerant communication pipe group 5 and the second refrigerant communication pipe group 7
- the optimum refrigerant amount of the outdoor unit 2 in the normal operation mode can be known in advance, so this refrigerant amount is stored in advance in the memory of the control unit 8 as the charging target value Ms, and the refrigerant is calculated using the above relational expression.
- Refrigerant circuit in automatic filling operation 10 Refrigerant amount in the outdoor unit 2 in which the refrigerant flowing in the circuit 10 or the operating state quantity force of the component equipment is calculated Mo, refrigerant amount in the indoor units 3a-3c Mr, refrigerant amount in the connection units 4a-4c Mbs The value of the refrigerant amount obtained by adding the above and so on. It is sufficient to perform additional charging of the refrigerant until the charging target value Ms is reached.
- Step S13 is filled with the refrigerant amount value obtained by adding the refrigerant amount Mo of the outdoor unit 2 to the refrigerant amount Mr of the indoor units 3a to 3c and the refrigerant amount Mbs of the connection units 4a to 4c in the automatic refrigerant charging operation.
- This is a process of determining whether or not the amount of refrigerant charged in the refrigerant circuit 10 by additional charging of the refrigerant is appropriate by determining whether or not the target value Ms has been reached.
- step S13 the refrigerant amount value obtained by adding the refrigerant amount Mo of the outdoor unit 2, the refrigerant amount Mr of the indoor units 3a to 3c, and the refrigerant amount Mbs of the connection units 4a to 4c is the filling target value Ms.
- the process of step S13 is repeated until the charging target value Ms is reached.
- the degree of supercooling SCo at the outlet of the outdoor heat exchanger 22 mainly tends to increase, and the outdoor heat exchange occurs.
- the refrigerant amount Mc in the vessel 22 increases, and the refrigerant amount in other parts tends to be kept almost constant.
- the filling target value Ms is set as a value corresponding only to the cooling medium amount Mo of the outdoor unit 2, which is not the outdoor unit 2, the indoor units 3a to 3c, and the connection units 4a to 4c, or It may be set as a value corresponding to the refrigerant amount Mc of the outdoor heat exchanger 22, and additional refrigerant charging may be performed until the charging target value Ms is reached.
- Step S2 Pipe volume judgment operation
- step S1 When the above-described automatic refrigerant charging operation in step S1 is completed, the process proceeds to the pipe volume determination operation in step S2.
- the control unit 8 performs the processing from step S21 to step S25 shown in FIG.
- FIG. 6 is a flow chart of the pipe volume judgment operation.
- Step S21 Pipe volume determination operation and volume calculation for liquid refrigerant communication pipe
- step S21 the indoor unit 100% operation and condensation are performed in the same manner as the refrigerant amount determination operation in step S11 in the above-described automatic refrigerant charging operation.
- the refrigerant temperature at the outlet of the main refrigerant circuit side of the subcooler 24 in the liquid pipe temperature control is set as the first target value Tlpsl, which is the liquid pipe temperature target value Tips for the T1 P.
- the steady state is the first state (see the refrigeration cycle indicated by the line including the broken line in Fig. 7).
- FIG. 7 is a Mollier diagram showing the refrigeration cycle of the air conditioner 1 in the pipe volume determination operation for the liquid refrigerant communication pipe.
- the refrigerant temperature T lp at the outlet of the main refrigerant circuit side of the subcooler 24 in the liquid pipe temperature control is stabilized at the first target value Tlpsl
- other equipment control that is, condensation pressure control
- the conditions of superheat degree control and evaporation pressure control are not changed (that is, without changing the superheat degree target value SHrs and low pressure target value Tes), and the liquid pipe temperature target value Tips is the first target value.
- the second target value Tlps2, which is different from Tlpsl, is changed to a stable second state (see the refrigeration cycle indicated by the solid line in Fig. 7).
- the second target value Tlps2 is a temperature higher than the first target value Tlpsl.
- the equipment control conditions other than the liquid pipe temperature control are not changed, so that the refrigerant amount Mogl in the high pressure gas pipe E, the first low pressure gas pipe H Amount of refrigerant at Mog2, amount of refrigerant at second low-pressure gas pipe I g3, the refrigerant amount Mgph in the high-pressure gas refrigerant communication pipe part Gl, and the refrigerant quantity Mgpl in the low-pressure gas refrigerant communication pipe part G2 are kept almost constant, and the refrigerant reduced from the liquid refrigerant communication pipe part B3 is the condenser part A.
- the high temperature side liquid pipe part Bl, the low temperature side liquid pipe part B2, the indoor unit part F, and the second bypass circuit part J are moved. That is, the refrigerant amount Mc in the condenser part A, the refrigerant amount Moll in the high temperature side liquid pipe part B1, the refrigerant quantity Mol2 in the low temperature side liquid pipe part B2, and the indoor unit part by the amount of refrigerant reduced from the liquid refrigerant communication pipe part B3
- the refrigerant quantity Mr in F and the refrigerant quantity Mob in the second bypass circuit section J will increase.
- control unit 8 (more specifically, the indoor side control) that functions as a pipe volume determination operation control means for performing a pipe volume determination operation for calculating the volume Mlp of the liquid refrigerant communication pipe unit B3.
- control unit 8 (more specifically, the indoor side control) that functions as a pipe volume determination operation control means for performing a pipe volume determination operation for calculating the volume Mlp of the liquid refrigerant communication pipe unit B3.
- step S22 the liquid cooling medium is utilized by utilizing the phenomenon that the refrigerant is decreased from the liquid refrigerant communication pipe section B3 and moves to the other part of the refrigerant circuit 10 due to the change from the first state to the second state. Calculate the volume Vlp of the connecting piping section B3.
- the amount of refrigerant that has decreased from the liquid refrigerant communication piping section B3 and moved to the other part of the refrigerant circuit 10 by the pipe volume determination operation described above is defined as the refrigerant increase / decrease amount ⁇ Mlp, and each amount between the first and second states.
- refrigerant amount Mogl refrigerant amount Mog2, refrigerant amount Mog3, refrigerant amount Mgp h, and refrigerant amount Mgpl are almost constant
- the refrigerant increase / decrease amount ⁇ Mlp is, for example,
- ⁇ Mlp — ( ⁇ Mc + ⁇ Moll + ⁇ ⁇ 12 + ⁇ Mr + ⁇ Mob)
- the volume Vlp of the liquid refrigerant communication pipe section B3 is calculated by dividing the value of ⁇ Mlp by the refrigerant density change ⁇ lp between the first and second states in the liquid refrigerant communication pipe section B3. be able to. Note that the refrigerant increase / decrease amount ⁇ Mlp has little effect on the calculation result, but in the above function equation, the refrigerant amount Mogl And the amount of refrigerant Mog2 is included.
- Vlp ⁇ Mlp / ⁇ lp
- the volume Vlp2 of the liquid side refrigerant flow path of the connection units 4a to 4c is a known value of the front force at which the connection units 4a to 4c are installed at the installation location.
- a Mc, ⁇ ⁇ 11, ⁇ ⁇ 12, A Mr, and A Mob represent the refrigerant amount in the first state and the refrigerant amount in the second state by using the relational expressions for the respective parts of the refrigerant circuit 10 described above. Is obtained by subtracting the amount of refrigerant in the second state.
- the density change amount ⁇ p ip calculates the refrigerant density at the outlet of the subcooler 24 in the first state and the refrigerant density at the outlet of the subcooler 24 in the second state, and further calculates the refrigerant density in the second state. Density force of the pressure is obtained by subtracting the refrigerant density in the first state.
- the volume Vlp of the liquid refrigerant communication pipe section B3 can be calculated from the refrigerant flowing through the refrigerant circuit 10 in the first and second states or the operating state quantity of the component equipment. I'll do it.
- the state is changed so that the second target value Tlps2 in the second state is higher than the first target value Tlpsl in the first state, and the refrigerant in the low temperature side liquid pipe section B2 is changed.
- the amount of refrigerant in the other part is increased by moving to this part, and the volume Vlp of the increased force liquid refrigerant communication pipe part B3 is calculated, but the second target value Tlps2 in the second state is the first Change the state so that the temperature is lower than the first target value Tlpsl in the state, and move the refrigerant from the other part to the liquid refrigerant communication pipe part B3 to reduce the amount of refrigerant in the other part. Calculate the volume Vlp of the liquid refrigerant communication pipe B3 from the decrease.
- the liquid refrigerant communication that calculates the volume Vlp of the liquid refrigerant communication pipe section B3 from the refrigerant flowing in the refrigerant circuit 10 in the pipe volume determination operation for the liquid refrigerant communication pipe section B3 or the operating state quantity of the component equipment.
- the control unit 8 that functions as pipe volume calculation means for piping Processing in step S22 is performed.
- Steps S23 and S24 Pipe volume judgment operation for gas refrigerant communication pipe and calculation of volume
- step S23 the piping for the gas refrigerant communication pipe G including the indoor unit 100% operation, condensing pressure control, liquid pipe temperature control, superheat degree control, and evaporation pressure control. Perform volume judgment operation.
- the low pressure target value Pes of the suction pressure Ps of the compressor 21 in the evaporation pressure control is set to the first target value Pesl
- the state in which the refrigerant amount determination operation is stabilized at the first target value Pesl is set to the first state ( (Refer to the refrigeration cycle indicated by the line including the dashed line in Figure 8).
- the low pressure target value of the suction pressure Ps of the compressor 21 in the evaporation pressure control From the first state where Pes is stable at the first target value Pesl, the conditions of other equipment control, ie, liquid tube temperature control, condensing pressure control, and superheat degree control, remain unchanged (ie, liquid tube temperature Without changing the target value Tips and superheat target value SHrs), the low pressure target value Pes is changed to the second target value Pes2, which is different from the first target value Pesl, to achieve a stable second state (Fig. 8). (Refer to the refrigeration cycle shown by the solid line only).
- the second target value Pes2 is a pressure lower than the first target value Pesl.
- the refrigerant in the gas refrigerant communication pipe section G since the density of the refrigerant in the gas refrigerant communication pipe section G is reduced by changing from the stable state in the first state to the second state, the refrigerant in the gas refrigerant communication pipe section G in the second state The amount Mgp will decrease compared to the amount of refrigerant in the first state. Then, the refrigerant decreased from the gas refrigerant communication pipe part G moves to the other part of the refrigerant circuit 10.
- the refrigerant amount Mo gl in the high-pressure gas pipe E and the refrigerant in the high-temperature side liquid pipe Bl The amount of refrigerant Mol, the refrigerant amount Mol 2 in the low-temperature side liquid pipe section B2, and the refrigerant quantity Mlp in the liquid refrigerant communication pipe section B3 are kept almost constant, and the refrigerant decreased from the gas refrigerant communication pipe section G is the first low pressure It moves to the gas pipe part H, the second low-pressure gas pipe part I, the condenser part A, the indoor unit part F, and the second bypass circuit part J.
- the amount of refrigerant Mog2 in the first low-pressure gas pipe H, the amount of refrigerant Mog3 in the second low-pressure gas pipe I, and the amount of refrigerant in the condenser A by the amount of refrigerant reduced from the gas refrigerant communication pipe G Mc, the refrigerant quantity Mr in the indoor unit part F, and the refrigerant quantity Mob in the second bypass circuit part J will increase.
- control unit 8 (more specifically, functioning as a pipe volume determination operation control means for performing a pipe volume determination operation for calculating the volume Vgp of the gas refrigerant communication pipe unit G.
- Step S2 3 by the indoor side control unit 34a to 34c, the connection side control unit 44a to 44c, the outdoor side control unit 26, and the transmission line 8a) connecting each control unit 34a to 34c, 44a to 44c, 26 It is performed as a process.
- step S24 by changing from the first state to the second state, the gas refrigerant communication piping part G force also uses the phenomenon that the refrigerant decreases and moves to the other part of the refrigerant circuit 10 to connect the gas refrigerant.
- Pipe volume G volume Vgp is calculated.
- the amount of refrigerant that has decreased from the gas refrigerant communication pipe G and moved to the other part of the refrigerant circuit 10 by the pipe volume determination operation described above is defined as refrigerant increase / decrease amount ⁇ Mgp, and each part between the first and second states.
- a Mc, A Mog2, A Mog3, ⁇ ⁇ , and ⁇ Mob (Here, the refrigerant amount Mogl, the refrigerant amount Moll, the refrigerant amount Mol2, and the refrigerant amount Mlp are kept almost constant. Therefore, the refrigerant increase / decrease amount ⁇ Mgp is, for example,
- a Mgp -(A Mc + A Mog2 + A Mog3 + A Mr + A Mob)
- the functional force It is possible to calculate the functional force. Then, by dividing the value of ⁇ Mgp by the refrigerant density change ⁇ pgp between the first and second states in the gas refrigerant communication piping section G, the volume Vgp of the gas refrigerant communication piping section G is calculated. can do. Note that, although the calculation result of the refrigerant increase / decrease amount ⁇ Mgp is hardly affected, the refrigerant quantity Mogl, the refrigerant quantity Moll, and the refrigerant quantity Mol2 may be included in the above-described functional expression.
- a Mc, A Mog2, A Mog3, A Mr, and ⁇ Mob are the amounts of refrigerant in the first state and the cooling amount in the second state, using the relational expressions for each part of the refrigerant circuit 10 described above.
- the amount of refrigerant in the second state is calculated by subtracting the amount of refrigerant in the second state and subtracting the amount of refrigerant in the first state.
- the density change amount ⁇ p gp is obtained on the suction side of the compressor 21 in the first state.
- Refrigerant density ps, refrigerant density poh in the high-pressure gas side pipe V5 between the high-pressure gas side shut-off valve V5 and the first high-pressure gas on-off valve V8 in the outdoor unit 2, and the connection units 4a to 4c The average density between the refrigerant density p bsh in the high-pressure gas side refrigerant flow path and the refrigerant density p eo at the outlets of the indoor heat exchangers 31a to 31c is calculated, and the average density force in the second state is calculated. It is obtained by subtracting the density.
- the volume Vgp of the gas refrigerant communication pipe section G can be calculated from the refrigerant flowing through the refrigerant circuit 10 in the first and second states or the operating state quantity of the component equipment using the arithmetic expression as described above. .
- the volume Vgp2 of the high pressure gas side refrigerant flow path and the low pressure gas side refrigerant flow path (including the third bypass refrigerant circuit 43a to 43c part) in the connection units 4a to 4c is the same as that of the connection units 4a to 4c. Since the pre-force is a known value, it is subtracted from the volume Vgp of the gas refrigerant communication pipe G obtained by calculation, so that the air conditioner 1 is installed on site when it is installed at the installation location such as a building.
- the volume V gpl of the portion that combines the high-pressure gas refrigerant communication pipe 52, the low-pressure gas refrigerant communication pipe 53, and the second gas refrigerant communication pipes 72a to 72c, which are refrigerant pipes to be used, can be obtained.
- the state change is performed such that the second target value Pes2 in the second state is lower than the first target value Pesl in the first state and the pressure is changed, and the gas refrigerant communication pipe section G
- the amount of refrigerant in the other part is increased by moving the refrigerant to the other part, and this increasing force is calculated as the volume Vlp of the gas refrigerant communication pipe G.
- the second target value in the second state Change the state so that Pes2 is at a pressure higher than the first target value Pesl in the first state! ⁇ Refrigerant amount in the other part by moving the refrigerant from the other part to the gas refrigerant communication pipe part G Calculate the volume Vlp of the gas refrigerant communication pipe G from this decrease.
- step S24 for the gas refrigerant communication pipe for calculating the volume Vgp of the gas refrigerant communication pipe section G from the refrigerant flowing in the refrigerant circuit 10 in the pipe volume determination operation for the gas refrigerant communication pipe section G or the operating state quantity of the component equipment.
- step S25 whether or not the result of the pipe volume determination operation is valid, that is, the liquid refrigerant communication pipe section B3 calculated by the pipe volume calculation means. It is determined whether or not the volume Vlp of the gas and the volume Vg p of the gas refrigerant communication pipe G are appropriate.
- ⁇ 1 and ⁇ 2 are values that can be varied based on the minimum value and the maximum value of the pipe volume ratio in a feasible combination of the heat source unit and the utilization unit.
- step S2 that is effective for the pipe volume determination operation is completed, and if the volume ratio VlpZVgp does not satisfy the above numerical range, The pipe volume determination operation and the volume calculation process in steps S21 to S24 are performed again.
- step S25 is performed by the control unit 8 functioning as a validity determination means for determining whether or not the volume Vgp is appropriate.
- the pipe volume determination operation for the liquid refrigerant communication pipe section B3 (steps S21 and S22) is performed first, and then the pipe volume determination operation for the gas refrigerant communication pipe section G (step S23 and S24) are performed, but the pipe volume determination operation for the gas refrigerant communication pipe section G may be performed first.
- step S25 when the result of the pipe volume determination operation in steps S21 to S24 is determined a plurality of times as inappropriate, or more simply, the volume Vlp of the liquid refrigerant communication pipe section B3 6 and the volume Vgp of the gas refrigerant communication pipe part G.
- steps S21 to S24 although not shown in FIG.
- refrigerant communication pipe part K Pressure loss force in the part that combines B3 and gas refrigerant communication pipe part G (hereinafter referred to as refrigerant communication pipe part K) Estimate the pipe length of refrigerant communication pipe part K, and the estimated pipe length and average volume ratio Shifts to the process of calculating the volume Vlp of the liquid refrigerant communication pipe B3 and the volume Vgp of the gas refrigerant communication pipe G, and the volume Vlp of the liquid refrigerant communication pipe B3 and the volume Vgp of the gas refrigerant communication pipe G Let's get it.
- the length of the refrigerant communication pipe section K does not include information such as the pipe diameter.
- the volume Vlp of the liquid refrigerant communication pipe section B3 and the volume Vgp of the gas refrigerant communication pipe section G are unknown.
- the pipe volume determination operation is performed to calculate the volume Vlp of the liquid refrigerant communication pipe section B3 and the volume Vgp of the gas refrigerant communication pipe section G.
- it has a function to calculate the volume Vlp of the liquid refrigerant communication pipe B3 and the volume Vgp of the gas refrigerant communication pipe G by inputting information such as the length of the refrigerant communication pipe K and the pipe diameter. This function may be used in combination.
- the function of calculating the volume Vlp of the liquid refrigerant communication pipe section B3 and the volume Vgp of the gas refrigerant communication pipe section G using the above-described pipe volume judgment operation and the operation result is not used, and the refrigerant communication pipe section K If only the function to calculate the volume Vlp of the liquid refrigerant communication piping part B3 and the volume Vgp of the gas refrigerant communication piping part G is used by inputting information such as the tube diameter, the above-mentioned validity judgment The means (step S25) may be used to determine whether or not the input information such as the length of the refrigerant communication pipe section K is appropriate.
- Step S3 Initial refrigerant quantity detection operation
- FIG. 9 is a flowchart of the initial refrigerant quantity detection operation.
- Step S31 Refrigerant amount judgment operation
- step S31 similar to the refrigerant amount determination operation in step S11 of the refrigerant automatic charging operation described above, the indoor unit 100% operation, the condensation pressure control, the liquid pipe temperature control, the superheat degree control, and the The refrigerant quantity determination operation including the evaporation pressure control is performed.
- the liquid pipe temperature target value Tlps in the liquid pipe temperature control, the superheat degree target value SHrs in the superheat degree control, and the low pressure target value Pes in the evaporation pressure control are, in principle, the step S 11 of the automatic refrigerant charging operation. The same value as the target value in the refrigerant quantity determination operation is used.
- control unit 8 functioning as the refrigerant amount determination operation control means for performing the refrigerant amount determination operation including the indoor unit total number operation, the condensation pressure control, the liquid pipe temperature control, the superheat degree control, and the evaporation pressure control. Then, the process of step S31 is performed.
- the refrigerant amount determination operation is performed while the control unit 8 functioning as the refrigerant amount calculation means while flowing through the refrigerant circuit 10 in the initial refrigerant amount detection operation in step S32.
- the amount of refrigerant in 10 is calculated.
- the amount of refrigerant in the refrigerant circuit 10 is calculated using a relational expression between the amount of refrigerant in each part of the refrigerant circuit 10 and the operating state amount of the refrigerant flowing through the refrigerant circuit 10 or the constituent devices.
- the volume Vlp of the liquid refrigerant communication pipe section B3 and the volume Vgp of the gas refrigerant communication pipe section G which were unknown after the installation of the components of the air conditioner 1, are calculated by the pipe volume determination operation described above. Therefore, by multiplying the volume Vgp of the liquid refrigerant communication pipe B3 and the volume Vgp of the gas refrigerant communication pipe G by the refrigerant density, the amount of refrigerant in the liquid refrigerant communication pipe B3 Mlp And the refrigerant amount Mgp of the gas refrigerant communication pipe part G, and by adding the refrigerant amounts of the other parts, the initial refrigerant amount of the refrigerant circuit 10 as a whole can be detected.
- This initial refrigerant amount is used as the reference refrigerant amount Mi of the refrigerant circuit 10 as a reference for determining the presence or absence of leakage from the refrigerant circuit 10 in the refrigerant leakage detection operation described later. Then, it is stored in the memory of the control unit 8 as state quantity storage means.
- control unit 8 functions as refrigerant amount calculation means for calculating the refrigerant amount of each part of the refrigerant circuit 10 from the refrigerant flowing in the refrigerant circuit 10 in the initial refrigerant amount detection operation or the operation state quantity of the constituent devices.
- the process of step S32 is performed.
- FIG. 10 is a flowchart of the refrigerant leak detection operation mode.
- Step S41 Refrigerant amount judgment operation
- the operation mode is automatically or manually changed from the normal operation mode to the refrigerant leakage detection operation mode.
- Switching is performed, and the refrigerant quantity determination operation including the total indoor unit operation, the condensation pressure control, the liquid pipe temperature control, the superheat degree control, and the evaporation pressure control is performed in the same manner as the refrigerant quantity determination operation in the initial refrigerant quantity detection operation.
- the liquid pipe temperature target value Tlps in the liquid pipe temperature control, the superheat degree target value SHrs in the superheat degree control, and the low pressure target value Pes in the evaporation pressure control are, in principle, the refrigerant quantity in the initial refrigerant quantity detection operation. The same value as the target value in step S31 of judgment operation is used.
- This refrigerant quantity determination operation is performed for each refrigerant leak detection operation.For example, if the condensation pressure Pc is different, outdoor heat exchange is performed depending on the operating conditions such as refrigerant leakage. Even when the refrigerant temperature Tco fluctuates at the outlet, the liquid pipe temperature control ensures that the refrigerant temperature Tip in the liquid refrigerant communication pipe section B3 is kept constant at the same liquid pipe temperature target value Tips. Become.
- control unit 8 functioning as the refrigerant quantity determination operation control means for performing the refrigerant quantity determination operation including the indoor unit total number operation, the condensation pressure control, the liquid pipe temperature control, the superheat degree control, and the evaporation pressure control, performs step S41. Is performed.
- the control unit 8 that functions as the refrigerant quantity calculation means while performing the refrigerant quantity judgment operation described above, the operation state quantity power of the refrigerant flowing through the refrigerant circuit 10 or the component device in the refrigerant leakage detection operation in step S42 is also the refrigerant.
- the refrigerant amount in the refrigerant circuit 10 is calculated using a relational expression between the refrigerant amount of each part of the refrigerant circuit 10 and the operating state quantity of the refrigerant flowing through the refrigerant circuit 10 or the component device.
- the air conditioner is Since the volume Vlp of the liquid refrigerant communication pipe section B3 and the volume Vgp of the gas refrigerant communication pipe section G, which were unknown after the installation of the component device 1, is calculated, they are known. Multiplying the volume Vlp of the connecting pipe B3 and the volume Vgp of the gas refrigerant connecting pipe G by the refrigerant density, the refrigerant amount Mlp of the liquid refrigerant connecting pipe B3 and the refrigerant amount Mgp of the gas refrigerant connecting pipe G And the refrigerant amount M of the entire refrigerant circuit 10 can be calculated by adding the refrigerant amounts of the other parts.
- the liquid refrigerant communication pipe section B3 since the temperature Tip of the refrigerant in the liquid refrigerant communication pipe section B3 is kept constant at the same liquid pipe temperature target value Tips by the liquid pipe temperature control, the liquid refrigerant communication pipe The refrigerant amount Mlp in the part B3 is kept constant even when the refrigerant temperature Tco fluctuates at the outlet of the outdoor heat exchanger 22 regardless of the operating condition of the refrigerant leak detection operation.
- control unit 8 that functions as a refrigerant amount calculating means that calculates the refrigerant amount in each part of the refrigerant circuit 10 from the refrigerant flowing in the refrigerant circuit 10 in the refrigerant leakage detection operation or the operation state quantity of the constituent devices, The process of step S42 is performed.
- Steps S43, S44 Judgment of appropriateness of refrigerant amount, warning display
- the refrigerant amount M of the entire refrigerant circuit 10 calculated in step S42 described above is the reference refrigerant amount MU detected in the initial refrigerant amount detection operation when refrigerant leakage from the refrigerant circuit 10 occurs. If the refrigerant leaks from the refrigerant circuit 10 and becomes V, in this case, it becomes almost the same value as the reference refrigerant amount Mi.
- step S43 it is determined whether or not refrigerant has leaked. If it is determined in step S43 that no refrigerant leaks from the refrigerant circuit 10, the refrigerant leak detection operation mode is terminated.
- step S43 if it is determined in step S43 that refrigerant has leaked from the refrigerant circuit 10, the process proceeds to step S44 to notify that refrigerant leak has been detected. After displaying the warning on the warning display unit 9, the refrigerant leakage detection operation mode is terminated.
- the refrigerant amount determination means for detecting the presence or absence of refrigerant leakage by determining whether or not the refrigerant amount in the refrigerant circuit 10 is appropriate while performing the refrigerant amount determination operation in the refrigerant leakage detection operation mode.
- the processing of steps S42 to S44 is performed by the control unit 8 that functions as one refrigerant leakage detection means.
- the control unit 8 includes the refrigerant amount determination operation unit, the refrigerant amount calculation unit, the refrigerant amount determination unit, the pipe volume determination operation unit, the pipe volume calculation unit, and the validity determination.
- the refrigerant amount determination system for determining the suitability of the refrigerant amount filled in the refrigerant circuit 10 is configured by functioning as the means and the state quantity accumulation unit.
- the high pressure gas refrigerant communication pipe G1 from the outdoor unit 2 to the connection units 4a to 4c is closed when performing the refrigerant amount determination operation with the indoor units 3a to 3c in all the rooms being in the cooling operation state.
- the refrigerant condenses and accumulates in the piping, which may increase detection errors. Therefore, the first bypass refrigerant circuit 27 and the third bypass refrigerant circuits 43a to 43c that bypass the high-pressure gas refrigerant communication pipe section G1 and the low-pressure gas refrigerant communication pipe section G2 are provided, and the first bypass refrigerant circuit 43a to 43c is provided during the refrigerant amount determination operation.
- the first bypass on / off valve V3 and the third bypass on / off valve are provided in the outdoor unit 2 and in the connection units 4a to 4c.
- the first bypass on-off valve V3 is installed in the outdoor unit 2, and the third bypass on-off valve is installed in the connection units 4a to 4c.
- the low-pressure gas refrigerant also flows into the high-pressure gas refrigerant communication pipe section G1.
- the temperature change of the gas refrigerant can be minimized, and the detection error can be reduced.
- a bypass circuit can be provided in the refrigerant circuit 10 without performing bypass piping work during construction. For this reason, it is possible to reduce the labor and cost involved in the construction.
- the air conditioner 1 also includes a first high pressure gas pipe temperature sensor T8 in the heat source unit in the high pressure gas refrigerant communication pipe section G1, and second high pressure gas pipe temperature sensors T12a to T in the connection units 4a to 4c. T12c is installed.
- the refrigerant density in the pipe can be corrected with higher accuracy.
- the temperature detecting means can be provided in the refrigerant circuit 10 without providing the temperature sensor in the high-pressure gas refrigerant pipe at the time of construction. For this reason, it is possible to reduce the labor and cost for the construction.
- the present invention is applied to the air conditioner including one outdoor unit.
- the present invention is not limited thereto, and the present invention is applied to an air conditioner including a plurality of outdoor units. May be applied.
- a water-cooled or ice heat storage type outdoor unit that uses an air-cooled outdoor unit that uses outside air as a heat source may be used as the outdoor unit 2 of the air conditioner 1.
- the first bypass refrigerant circuit 27 is provided on the outdoor unit 2 side, and the third bypass refrigerant circuits 43a to 43c are provided on the connection units 4a to 4c side. It may be only on the outdoor unit 2 side or on the connection unit 4a-4c side May be good.
- the first high pressure gas pipe temperature sensor T8 is provided on the outdoor unit 2 side and the second high pressure gas pipe temperature sensors T12a to T12c are provided on the connection units 4a to 4c side as temperature sensors. May be only on the outdoor unit 2 side, or may be only on the connection boots 4a to 4c side. Further, the temperature sensor may not be provided.
- the outdoor conditioner 26, the indoor control units 34a to 34c, and the connection control units 44a to 44c exchange control signals via the transmission line 8a, and the air conditioner 1 as a whole.
- the control unit that controls the entire air conditioner 1 may be provided in the outdoor unit 2 or in the indoor units 3a to 3c. Alternatively, it may be provided in the connection units 4a to 4c, or a single unit may be provided as a control unit.
- the air conditioner according to the present invention reduces the pressure difference between the first gas refrigerant communication pipe and the second gas refrigerant communication pipe, and prevents liquid refrigerant from being accumulated due to condensation in the first gas refrigerant communication pipe. Therefore, the refrigerant amount determination operation with high accuracy is possible, and the refrigerant circuit of the air conditioner and the air conditioner equipped with the refrigerant circuit are useful.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Air Conditioning Control Device (AREA)
Abstract
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN2007800080112A CN101395436B (zh) | 2006-03-10 | 2007-03-08 | 空调装置 |
ES07738077.2T ES2646190T3 (es) | 2006-03-10 | 2007-03-08 | Acondicionador de aire |
AU2007225803A AU2007225803B2 (en) | 2006-03-10 | 2007-03-08 | Air conditioner |
EP07738077.2A EP1998124B1 (en) | 2006-03-10 | 2007-03-08 | Air conditioner |
US12/281,064 US20090031739A1 (en) | 2006-03-10 | 2007-03-08 | Air conditioner |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2006065932A JP3963192B1 (ja) | 2006-03-10 | 2006-03-10 | 空気調和装置 |
JP2006-065932 | 2006-03-10 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2007105604A1 true WO2007105604A1 (ja) | 2007-09-20 |
Family
ID=38498631
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2007/054587 WO2007105604A1 (ja) | 2006-03-10 | 2007-03-08 | 空気調和装置 |
Country Status (8)
Country | Link |
---|---|
US (1) | US20090031739A1 (ja) |
EP (1) | EP1998124B1 (ja) |
JP (1) | JP3963192B1 (ja) |
KR (1) | KR100960539B1 (ja) |
CN (1) | CN101395436B (ja) |
AU (1) | AU2007225803B2 (ja) |
ES (1) | ES2646190T3 (ja) |
WO (1) | WO2007105604A1 (ja) |
Families Citing this family (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2009079842A (ja) * | 2007-09-26 | 2009-04-16 | Mitsubishi Electric Corp | 冷凍サイクル装置およびその制御方法 |
JP5186951B2 (ja) * | 2008-02-29 | 2013-04-24 | ダイキン工業株式会社 | 空気調和装置 |
JP5200996B2 (ja) * | 2009-02-24 | 2013-06-05 | ダイキン工業株式会社 | ヒートポンプシステム |
JP5764736B2 (ja) * | 2010-11-30 | 2015-08-19 | パナソニックIpマネジメント株式会社 | 冷凍装置 |
WO2014061132A1 (ja) * | 2012-10-18 | 2014-04-24 | ダイキン工業株式会社 | 空気調和装置 |
US9696078B2 (en) | 2013-11-20 | 2017-07-04 | Mitsubishi Electric Corporation | Refrigeration cycle apparatus |
US10119738B2 (en) | 2014-09-26 | 2018-11-06 | Waterfurnace International Inc. | Air conditioning system with vapor injection compressor |
EP3348934B1 (en) * | 2015-09-11 | 2021-10-27 | Hitachi-Johnson Controls Air Conditioning, Inc. | Air conditioner |
WO2018101439A1 (ja) * | 2016-11-30 | 2018-06-07 | ダイキン工業株式会社 | 配管径の決定方法、配管径の決定装置、および冷凍装置 |
CN110651163B (zh) * | 2018-04-26 | 2020-08-18 | 日立江森自控空调有限公司 | 空调机 |
US11592215B2 (en) | 2018-08-29 | 2023-02-28 | Waterfurnace International, Inc. | Integrated demand water heating using a capacity modulated heat pump with desuperheater |
JP6984048B2 (ja) * | 2019-01-16 | 2021-12-17 | 三菱電機株式会社 | 空気調和機 |
JP7079226B2 (ja) * | 2019-07-12 | 2022-06-01 | ダイキン工業株式会社 | 冷媒漏洩報知装置及び冷媒漏洩報知装置を備えた冷凍サイクルシステム |
KR20210096522A (ko) * | 2020-01-28 | 2021-08-05 | 엘지전자 주식회사 | 공기 조화 장치 |
JP7406165B2 (ja) * | 2020-05-08 | 2023-12-27 | ダイキン工業株式会社 | 冷凍サイクルシステム、熱源ユニット、および冷凍サイクル装置 |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0363468A (ja) * | 1989-07-31 | 1991-03-19 | Daikin Ind Ltd | 空気調和装置の運転制御装置 |
JPH03186170A (ja) * | 1989-12-13 | 1991-08-14 | Hitachi Ltd | 冷凍装置及び冷凍装置における冷媒量表示方法 |
JP2002340436A (ja) * | 2001-05-18 | 2002-11-27 | Fujitsu General Ltd | 多室形空気調和機 |
JP2004332961A (ja) * | 2003-04-30 | 2004-11-25 | Samsung Electronics Co Ltd | 空気調和装置 |
JP2006058007A (ja) * | 2004-06-11 | 2006-03-02 | Daikin Ind Ltd | 空気調和装置 |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5237833A (en) * | 1991-01-10 | 1993-08-24 | Mitsubishi Denki Kabushiki Kaisha | Air-conditioning system |
JP3186170B2 (ja) * | 1992-02-13 | 2001-07-11 | 井関農機株式会社 | 脱穀扱胴の展開装置 |
JP3291753B2 (ja) * | 1992-04-08 | 2002-06-10 | ダイキン工業株式会社 | 冷凍装置の冷媒充填量検知装置 |
JP3063468B2 (ja) * | 1993-07-02 | 2000-07-12 | 神鋼電機株式会社 | アンダカットマシンの切削部の位置決め方法 |
KR100437805B1 (ko) * | 2002-06-12 | 2004-06-30 | 엘지전자 주식회사 | 냉난방 동시형 멀티공기조화기 및 그 제어방법 |
KR100447204B1 (ko) * | 2002-08-22 | 2004-09-04 | 엘지전자 주식회사 | 냉난방 동시형 멀티공기조화기 및 그 제어방법 |
KR100459184B1 (ko) * | 2002-08-24 | 2004-12-03 | 엘지전자 주식회사 | 냉난방 동시형 멀티공기조화기 |
JP3719246B2 (ja) * | 2003-01-10 | 2005-11-24 | ダイキン工業株式会社 | 冷凍装置及び冷凍装置の冷媒量検出方法 |
KR100688171B1 (ko) * | 2004-12-29 | 2007-03-02 | 엘지전자 주식회사 | 냉난방 동시형 멀티 공기조화기 및 냉매 회수방법 |
JP4093275B2 (ja) * | 2006-03-20 | 2008-06-04 | ダイキン工業株式会社 | 空気調和装置 |
-
2006
- 2006-03-10 JP JP2006065932A patent/JP3963192B1/ja active Active
-
2007
- 2007-03-08 US US12/281,064 patent/US20090031739A1/en not_active Abandoned
- 2007-03-08 CN CN2007800080112A patent/CN101395436B/zh active Active
- 2007-03-08 EP EP07738077.2A patent/EP1998124B1/en active Active
- 2007-03-08 AU AU2007225803A patent/AU2007225803B2/en active Active
- 2007-03-08 ES ES07738077.2T patent/ES2646190T3/es active Active
- 2007-03-08 KR KR1020087023156A patent/KR100960539B1/ko not_active IP Right Cessation
- 2007-03-08 WO PCT/JP2007/054587 patent/WO2007105604A1/ja active Application Filing
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0363468A (ja) * | 1989-07-31 | 1991-03-19 | Daikin Ind Ltd | 空気調和装置の運転制御装置 |
JPH03186170A (ja) * | 1989-12-13 | 1991-08-14 | Hitachi Ltd | 冷凍装置及び冷凍装置における冷媒量表示方法 |
JP2002340436A (ja) * | 2001-05-18 | 2002-11-27 | Fujitsu General Ltd | 多室形空気調和機 |
JP2004332961A (ja) * | 2003-04-30 | 2004-11-25 | Samsung Electronics Co Ltd | 空気調和装置 |
JP2006058007A (ja) * | 2004-06-11 | 2006-03-02 | Daikin Ind Ltd | 空気調和装置 |
Non-Patent Citations (1)
Title |
---|
See also references of EP1998124A4 * |
Also Published As
Publication number | Publication date |
---|---|
KR100960539B1 (ko) | 2010-06-03 |
AU2007225803B2 (en) | 2009-12-24 |
CN101395436A (zh) | 2009-03-25 |
EP1998124B1 (en) | 2017-10-04 |
US20090031739A1 (en) | 2009-02-05 |
KR20080097475A (ko) | 2008-11-05 |
JP3963192B1 (ja) | 2007-08-22 |
EP1998124A1 (en) | 2008-12-03 |
ES2646190T3 (es) | 2017-12-12 |
CN101395436B (zh) | 2012-08-29 |
AU2007225803A1 (en) | 2007-09-20 |
EP1998124A4 (en) | 2016-11-02 |
JP2007240108A (ja) | 2007-09-20 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
WO2007105604A1 (ja) | 空気調和装置 | |
JP4120676B2 (ja) | 空気調和装置 | |
JP4093275B2 (ja) | 空気調和装置 | |
JP4904908B2 (ja) | 空気調和装置 | |
JP4114691B2 (ja) | 空気調和装置 | |
JP4165566B2 (ja) | 空気調和装置 | |
JP4124228B2 (ja) | 空気調和装置 | |
JP4705878B2 (ja) | 空気調和装置 | |
JP4075933B2 (ja) | 空気調和装置 | |
WO2008001687A1 (en) | Air conditioner | |
WO2007069583A1 (ja) | 空気調和装置 | |
JP5104225B2 (ja) | 空気調和装置 | |
JP4665748B2 (ja) | 空気調和装置 | |
JP2007255738A (ja) | 空気調和装置 | |
JP4826266B2 (ja) | 空気調和装置 | |
WO2007125959A1 (ja) | 空気調和装置 | |
JP4311470B2 (ja) | 空気調和装置 | |
JP4655107B2 (ja) | 空気調和装置 | |
JP4826247B2 (ja) | 空気調和装置 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 07738077 Country of ref document: EP Kind code of ref document: A1 |
|
WWE | Wipo information: entry into national phase |
Ref document number: 12281064 Country of ref document: US |
|
WWE | Wipo information: entry into national phase |
Ref document number: 200780008011.2 Country of ref document: CN |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2007225803 Country of ref document: AU |
|
WWE | Wipo information: entry into national phase |
Ref document number: 1020087023156 Country of ref document: KR |
|
REEP | Request for entry into the european phase |
Ref document number: 2007738077 Country of ref document: EP |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2007738077 Country of ref document: EP |
|
ENP | Entry into the national phase |
Ref document number: 2007225803 Country of ref document: AU Date of ref document: 20070308 Kind code of ref document: A |