WO2007097238A1 - 空気調和装置および熱源ユニット - Google Patents
空気調和装置および熱源ユニット Download PDFInfo
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- WO2007097238A1 WO2007097238A1 PCT/JP2007/052677 JP2007052677W WO2007097238A1 WO 2007097238 A1 WO2007097238 A1 WO 2007097238A1 JP 2007052677 W JP2007052677 W JP 2007052677W WO 2007097238 A1 WO2007097238 A1 WO 2007097238A1
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- refrigerant
- heat source
- unit
- source unit
- control
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/50—Control or safety arrangements characterised by user interfaces or communication
- F24F11/54—Control or safety arrangements characterised by user interfaces or communication using one central controller connected to several sub-controllers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
- F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
- F24F5/0017—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning using cold storage bodies, e.g. ice
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/006—Compression machines, plants or systems with reversible cycle not otherwise provided for two pipes connecting the outdoor side to the indoor side with multiple indoor units
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
- F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
- F25B2313/0253—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in parallel arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/02742—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using two four-way valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/19—Pumping down refrigerant from one part of the cycle to another part of the cycle, e.g. when the cycle is changed from cooling to heating, or before a defrost cycle is started
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/26—Problems to be solved characterised by the startup of the refrigeration cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/05—Refrigerant levels
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B45/00—Arrangements for charging or discharging refrigerant
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
- Y02E60/14—Thermal energy storage
Definitions
- Air conditioner and heat source unit Air conditioner and heat source unit
- the present invention relates to an air conditioner and a heat source unit, and more particularly to an air conditioner in which a plurality of heat source units are present in one refrigerant circuit.
- Patent Document 1 discloses a multi-air conditioner that achieves uniform operation time of a plurality of compressors while equalizing operation time of a plurality of outdoor units.
- Patent Document 2 discloses a plurality of outdoor units having a compressor, an outdoor heat exchanger, and an accumulator, a plurality of indoor units, a gas refrigerant communication pipe and a liquid refrigerant communication pipe common to both units, and an outdoor unit.
- a multi-air conditioner including a bypass circuit that supplies liquid refrigerant in the accumulator to an outdoor heat exchanger of another outdoor unit.
- Patent Document 1 Japanese Patent Laid-Open No. 2001-41528
- Patent Document 2 JP-A-11-63711
- An object of the present invention is to provide a plurality of outdoor units (heat source units) that can suppress the excessive operation of the remaining refrigerant in the outdoor unit and hindering smooth operation even when the capacity of the accumulator is relatively small. It is in providing the air conditioning apparatus provided. Means for solving the problem
- An air conditioner includes a plurality of heat source units, a utilization unit, a liquid refrigerant communication pipe and a gas refrigerant communication pipe, and a control unit.
- One of the plurality of heat source units is the first heat source unit.
- the heat source unit includes a compressor, a heat source side heat exchanger, and an accumulator.
- the utilization unit has a utilization side expansion mechanism and a utilization side heat exchanger.
- the liquid refrigerant communication pipe and the gas refrigerant communication pipe connect a plurality of heat source units and utilization units to form one main refrigerant circuit.
- the control unit determines that the amount of refrigerant in the first heat source unit in the operating state is excessive, the other unit start control for starting the other heat source unit in the stopped state, or the first heat source unit in the operating state.
- refrigerant accumulation control for accumulating refrigerant in the accumulator is performed.
- the refrigerant compressed by the compressor flows through the main refrigerant circuit, heat exchange is performed by the use side heat exchanger, and air conditioning is performed. Then, when the amount of refrigerant in the operating first heat source unit becomes excessive, the other heat source units in the stopped state are started, or the other heat source unit controls the accumulation of refrigerant in the accumulator (refrigerant accumulation control). Let it be done. According to the former other unit start-up control, the other heat source unit is put into an operating state, so that
- the refrigerant can be moved from one heat source unit to another heat source unit.
- air conditioning is performed in the other heat source units by other unit start-up control, and the first heat source unit in which the refrigerant is excessive is stopped, and the movement of the refrigerant from the first heat source unit to the other heat source units is promoted.
- the refrigerant can be moved from one heat source unit to another heat source unit. Therefore, in the air conditioner according to the present invention, even when the capacity of the accumulator is relatively small, it is possible to suppress an excessive surplus refrigerant from staying in the first heat source unit and hindering smooth operation.
- An air conditioner is the apparatus of the first aspect, wherein the control unit first causes a refrigerant in the first heat source unit when a predetermined refrigerant reservoir condition is reached in the first heat source unit. Reservoir control is performed, and when it is determined that the amount of refrigerant is excessive in the first heat source unit during the refrigerant reservoir control, other unit start-up control or other than the first heat source unit Refrigerant reservoir control in the heat source unit is performed.
- the first heat source unit executes the refrigerant storage control for storing the refrigerant in the accumulator based on a predetermined refrigerant storage condition. Will do. Therefore, when surplus refrigerant is generated, the amount of refrigerant can be adjusted by first introducing the surplus refrigerant to the accumulator, and the number of times that other heat source units are affected can be reduced.
- An air conditioner is the apparatus according to the first or second aspect, wherein an accumulator is disposed on the suction side of the compressor in the heat source unit.
- the heat source unit further includes a bypass refrigerant circuit.
- the bypass refrigerant circuit has a bypass flow rate adjustment valve for adjusting the flow rate of the refrigerant, and guides the refrigerant between the heat source side heat exchanger and the liquid refrigerant communication pipe to the accumulator.
- the accumulator arranged on the suction side of the compressor serves to separate the liquid refrigerant from the gas refrigerant and prevent the liquid refrigerant from being sucked into the compressor.
- the accumulator is connected to the accumulator via a bypass refrigerant circuit. The liquid refrigerant is allowed to flow in. As a result, surplus liquid refrigerant can be reliably stored in the accumulator.
- An air conditioner according to a fourth invention is the device according to the third invention, wherein the heat source unit further includes a subcooler.
- the subcooler cools the refrigerant sent from the heat source side heat exchanger to the utilization unit via the liquid refrigerant communication pipe by the refrigerant flowing from the bypass flow rate control valve to the accumulator.
- liquid refrigerant can be supercooled by using a bypass refrigerant circuit that guides excess liquid refrigerant to the accumulator.
- An air conditioner according to a fifth aspect of the present invention is the device according to any one of the first to fourth aspects, wherein the control unit has a degree of superheat of the gas refrigerant on the discharge side of the compressor lower than a predetermined value. Sometimes, it is determined that the refrigerant amount is excessive in the first heat source unit.
- An air conditioner according to a sixth aspect of the present invention is the device of the fourth aspect, wherein the control unit is configured to supply the gas refrigerant when the bypass flow rate adjustment valve is fully opened or on the discharge side of the compressor. When the degree of superheat falls below a predetermined value, it is determined that the amount of refrigerant in the heat source unit is excessive.
- An air conditioner is the device of the second aspect, wherein the predetermined refrigerant storage condition during the cooling operation includes at least a first condition and / or a second condition.
- the first condition is that the degree of refrigerant supercooling at the outlet of the heat source side heat exchanger is higher than a predetermined value.
- the second condition is a condition that the refrigerant high pressure on the discharge side of the compressor is higher than a predetermined value.
- An air conditioner is the apparatus of the second aspect, wherein the heat source unit further includes a heat source side expansion mechanism.
- the heat source side expansion mechanism includes an expansion valve disposed between the heat source side heat exchanger and the liquid refrigerant communication pipe.
- the predetermined refrigerant reservoir condition during the heating operation includes at least a third condition that the expansion valve of the heat source side expansion mechanism is fully open.
- An air conditioner according to a ninth invention is the device according to any one of the first to eighth inventions, wherein the control unit determines that the amount of refrigerant is excessive in the first heat source unit in an operating state. At this time, if there is a heat source unit in a stopped state, the other unit start control is performed in addition to the refrigerant reservoir control in the heat source unit other than the first heat source unit in the operating state.
- Activating the other heat source unit in the stopped state is more effective in eliminating the excess state of the excess refrigerant in the first heat source unit than performing the refrigerant accumulation control in the other heat source unit in the operating state. Since the effect is high, priority is given here to starting any other heat source units that are in a stopped state. As a result, the operation of the first heat source unit in the state where there is an excessive surplus refrigerant is quickly eliminated.
- An air conditioner according to a tenth aspect of the present invention is the device according to any one of the first to ninth aspects, wherein the control unit sets a refrigerant reservoir processed flag on the heat source unit that has performed the refrigerant reservoir control. . Then, when the control unit determines that the amount of refrigerant in the first heat source unit in the operating state is excessive, the control unit performs other unit activation control or refrigerant accumulation control in the heat source unit in which the refrigerant accumulation processing flag is not set. Make it. [0015] A heat source unit that has once been subjected to refrigerant accumulation control is likely to have a relatively large amount of liquid refrigerant accumulated in an accumulator.
- the other unit activation control or the refrigerant in the heat source unit in which the flag other than the heat source unit in which the refrigerant accumulation processing flag is set is not set is set. Reservoir control is performed. As a result, the continued operation of the first heat source unit in the presence of excess surplus refrigerant is quickly eliminated.
- the heat source unit of the air conditioner according to the eleventh aspect of the present invention is connected to another heat source unit and a utilization unit to form one main refrigerant circuit, and the heat on the utilization side of the utilization unit is exchanged with the air in the space to be conditioned.
- This unit exchanges heat with the vessel.
- the heat source unit includes a compressor, a heat source side heat exchanger, an accumulator, and a control unit. When the control unit determines that the amount of refrigerant is excessive, the control unit starts another heat source unit that is in a stopped state, or the accumulator of the heat source unit in another heat source unit that is in an operating state.
- the other unit refrigerant storage control for storing the refrigerant is performed.
- the refrigerant compressed by the compressor flows through the main refrigerant circuit, heat exchange is performed by the use side heat exchanger, and air conditioning is performed. Then, when the amount of refrigerant becomes excessive during operation, another heat source unit in a stopped state is started, or control for accumulating refrigerant in the accumulator with another heat source unit (other unit refrigerant accumulation control) is performed. According to the former other unit start-up control, the refrigerant can be moved from the heat source unit in which the refrigerant is excessive to the other heat source unit by putting the other heat source unit in the operating state.
- a heat source unit is the heat source unit of the eleventh aspect of the present invention, wherein the control unit first stores the refrigerant in the accumulator when the predetermined refrigerant accumulation condition is met. And determine that the amount of refrigerant is excessive during the self-unit refrigerant reservoir control. Then, other unit activation control or other unit refrigerant reservoir control is performed.
- the own unit before executing the other unit activation control or the other unit refrigerant reservoir control, first, executes the own unit refrigerant reservoir control for storing the refrigerant in the accumulator based on a predetermined refrigerant reservoir condition. It will be. For this reason, when surplus refrigerant is generated, the amount of refrigerant can be adjusted by first introducing the surplus refrigerant to the accumulator, thereby reducing the number of times that other heat source units are affected.
- the refrigerant is moved from the first heat source unit in which the refrigerant has become excessive to the other heat source unit by the other unit start-up control or the refrigerant reservoir control in the other heat source unit.
- the capacity of the accumulator is relatively small, it is possible to suppress an excessive surplus refrigerant from staying in the first heat source unit and hindering smooth operation.
- the surplus refrigerant when surplus refrigerant is generated, the surplus refrigerant is first introduced into the accumulator to adjust the amount of the refrigerant, so that the number of times affecting other heat source units can be reduced. it can.
- the liquid refrigerant can be supercooled using the bypass refrigerant circuit that guides excess liquid refrigerant to the accumulator.
- the first heat source unit is prevented from being operated while the excess refrigerant is excessive, and the compressor is sucked into the two-phase refrigerant.
- the refrigerant can be moved from the heat source unit in which the refrigerant has become excessive to the other heat source unit by the other unit start-up control or the other unit refrigerant reservoir control. Even when the capacity of the accumulator is small, it is possible to suppress an excessive surplus refrigerant from staying in the heat source unit and hindering smooth operation.
- the surplus refrigerant when surplus refrigerant is generated, the surplus refrigerant is first introduced into its accumulator to adjust the amount of refrigerant, so that the number of times affecting other heat source units can be reduced.
- FIG. 1 is a schematic configuration diagram of an air conditioner including a heat source unit according to an embodiment of the present invention.
- FIG. 2 is a control block diagram of the air conditioner.
- FIG. 5 Flow chart of outdoor rotation control.
- FIG. 1 shows an air conditioner 1 according to an 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 is mainly composed of a plurality of outdoor units 2, 102 as heat source units (two in FIG. 1) and a plurality of usage units connected in parallel to the unit. All the indoor units 4, a liquid refrigerant communication pipe 6 and a gas refrigerant communication pipe 7 as refrigerant communication pipes connecting the outdoor units 2, 102 and the indoor unit 4 are provided.
- the outdoor units 2, 102, the indoor unit 4, the liquid refrigerant communication pipe 6, and the gas refrigerant communication pipe 7 are connected. Therefore, it is comprised.
- the indoor unit 4 is installed by being embedded or suspended in the ceiling of a room such as a building or by hanging on the wall surface of the room.
- the indoor unit 4 is connected to the outdoor units 2 and 102 via the liquid refrigerant communication pipe 6 and the gas refrigerant communication pipe 7 and constitutes a part of the refrigerant circuit 10.
- the indoor unit 4 mainly has an indoor-side refrigerant circuit 10b that constitutes a part of the refrigerant circuit 10.
- This indoor refrigerant circuit 10b mainly includes an indoor expansion valve 41 as an expansion mechanism and an indoor heat exchanger 42 as a use side heat exchanger.
- the indoor expansion valve 41 is an electric expansion valve connected to the liquid side of the indoor heat exchanger 42 in order to adjust the flow rate of the refrigerant flowing in the indoor refrigerant circuit 10b.
- the indoor heat exchanger 42 is a cross-fin type fin-and-tube heat exchanger constituted by a heat transfer tube and a large number of fins, and serves as a refrigerant evaporator during cooling operation. It functions to cool indoor air, and functions as a refrigerant condenser during heating operation to heat indoor air.
- the indoor unit 4 has an indoor fan 43.
- the indoor fan 43 sucks indoor air into the unit, exchanges heat with the refrigerant in the indoor heat exchanger 42, and supplies the indoor air as supply air.
- the indoor fan 43 is a fan capable of changing the air volume supplied to the indoor heat exchanger 42, and is a centrifugal fan or a multiblade fan driven by a DC fan motor in this embodiment.
- the indoor unit 4 is provided with various sensors.
- the liquid side of the indoor heat exchanger 42 has a refrigerant temperature (that is, a condensing temperature during heating operation or a cooling operation).
- a liquid temperature sensor 44 for detecting a refrigerant temperature corresponding to the evaporation temperature in the liquid is provided.
- a gas side temperature sensor 45 that detects the temperature of the refrigerant is provided on the gas side of the indoor heat exchanger 42.
- An indoor air temperature sensor 46 for detecting the temperature of indoor air flowing into the unit (that is, the indoor temperature) is provided on the indoor air inlet side of the indoor unit 4.
- the liquid side temperature sensor 44, the gas side temperature sensor 45, and the indoor air temperature sensor 46 are composed of thermistors.
- the indoor unit 4 also has an indoor unit control unit 50c (see FIG. 2) that controls the operation of each part constituting the indoor unit 4.
- the indoor unit control section 50c has a microcomputer memory provided for controlling the indoor unit 4, and is connected to a remote controller (not shown) for individually operating the indoor unit 4. Control signals, etc., and exchange control signals, etc. via a transmission line (not shown) between the first outdoor unit controller 50a and the second outdoor unit controller 50b shown in FIG. You can go on and off.
- the outdoor units 2 and 102 are installed outside a building or the like, and are connected to the indoor unit 4 via the liquid refrigerant communication pipe 6 and the gas refrigerant communication pipe 7 and constitute the refrigerant circuit 10 together with the indoor unit 4. ing.
- the configuration of the outdoor units 2 and 102 will be described. Since the first outdoor unit 2 and the second outdoor unit 102 have the same configuration, only the configuration of the first outdoor unit 2 will be described here, and the configuration of the second outdoor unit 102 will be described. In each case, instead of the reference numerals indicating the respective parts of the first outdoor unit 2, the reference numerals are added with 100, and the description thereof is omitted.
- the first outdoor unit 2 mainly has an outdoor refrigerant circuit 10a that constitutes a part of the refrigerant circuit 10.
- the outdoor refrigerant circuit 10a mainly includes a compressor 21, a four-way switching valve 22, an outdoor heat exchanger 23 as a heat source side heat exchanger, an outdoor expansion valve 38 as an expansion mechanism, and an accumulator 24. And a supercooler 25 as a temperature adjusting mechanism, a liquid side closing valve 26, and a gas side closing valve 27.
- the compressor 21 is a compressor whose operating capacity can be varied.
- the compressor 21 is a positive displacement compressor driven by a motor whose rotational speed is controlled by an inverter. is there.
- FIG. 1 only one compressor 21 is shown. Actually, two or more compressors are connected in parallel. As shown in FIG. 1, the compressor 21 may be configured by a single compressor.
- the four-way switching valve 22 is a valve for switching the flow direction of the refrigerant.
- the outdoor heat exchanger 23 is used as a refrigerant condenser compressed by the compressor 21, and the indoor heat exchange is performed.
- the unit 42 is caused to function as an evaporator for refrigerant condensed in the outdoor heat exchanger 23.
- the four-way switching valve 22 connects the discharge side of the compressor 21 and the gas side of the outdoor heat exchanger 23, and also connects the suction side (specifically, accumulator 24) of the compressor 21 and the gas refrigerant communication pipe 7 side. (Refer to the solid line of the four-way selector valve 22 in FIG. 1).
- the indoor heat exchanger 42 is used as a refrigerant condenser compressed by the compressor 21, and the outdoor heat exchanger 23 is It functions as an evaporator for the refrigerant condensed in the indoor heat exchanger.
- the four-way switching valve 22 connects the discharge side of the compressor 21 and the gas refrigerant communication pipe 7 side, and also connects the suction side of the compressor 21 and the gas side of the outdoor heat exchanger 23. It is possible (see the broken line for the four-way selector valve 22 in Fig. 1).
- the outdoor heat exchanger 23 is a cross-fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins, and serves as a refrigerant condenser during cooling operation. It functions as a refrigerant evaporator during heating operation.
- the outdoor heat exchanger 23 has a gas side connected to the four-way switching valve 22 and a liquid side connected to the liquid refrigerant communication pipe 6.
- the outdoor expansion valve 38 is an electric expansion valve connected to the liquid side of the outdoor heat exchanger 23 in order to adjust the pressure and flow rate of the refrigerant flowing in the outdoor refrigerant circuit 10a.
- the outdoor unit 2 has an outdoor fan 28.
- the outdoor fan 28 sucks outdoor air into the unit, exchanges heat with the refrigerant in the outdoor heat exchanger 23, and then discharges the outdoor air.
- the outdoor fan 28 is a fan capable of changing the air volume of the air supplied to the outdoor heat exchanger 23, and is a propeller fan or the like driven by a DC fan motor in this embodiment.
- the accumulator 24 is connected between the four-way selector valve 22 and the compressor 21, and has an indoor unit. This is a container that can store surplus refrigerant generated in the refrigerant circuit 10 in accordance with fluctuations in the operating load of the knit 4.
- the accumulator 24 separates the liquid refrigerant and the gas refrigerant and sucks only the gas refrigerant into the compressor 21, and the mixed liquid of the refrigerant and the refrigerating machine oil accumulated in the bottom portion passes through an oil return pipe (not shown). Then, let the compressor 21 suck in and keep the amount of oil necessary for lubrication inside the compressor 21 properly.
- the subcooler 25 is a double-pipe heat exchanger, and after being condensed in the outdoor heat exchanger 23, the supercooler 25 is sent to the indoor expansion valve 41 via the liquid refrigerant communication pipe 6. Can be cooled.
- the supercooler 25 is interposed between the outdoor expansion valve 38 and the liquid side closing valve 26.
- a bypass refrigerant circuit 61 is provided as a cooling source for the subcooler 25.
- a part of the refrigerant circuit 10 excluding the bypass refrigerant circuit 61 is used for convenience. It will be called a main refrigerant circuit.
- the bypass refrigerant circuit 61 is connected to the main refrigerant circuit so that a part of the refrigerant sent from the outdoor heat exchanger 23 to the indoor expansion valve 41 is branched from the main refrigerant circuit and returned to the suction side of the compressor 21. Yes.
- the bypass refrigerant circuit 61 includes a branch circuit 61a and a junction circuit 61b.
- the branch circuit 61a branches a part of the cooling medium sent from the outdoor expansion valve 38 to the indoor expansion valve 41 from a position between the outdoor heat exchanger 23 and the subcooler 25.
- the junction circuit 61b is connected to the suction side of the compressor 21 so that the refrigerant is returned to the suction side of the compressor 21 from the outlet on the bypass refrigerant circuit 61 side of the subcooler 25.
- the branch circuit 61a is provided with a bypass valve 62 for adjusting the flow rate of the refrigerant flowing through the no-pass refrigerant circuit 61.
- the bypass valve 62 is an electric expansion valve.
- bypass refrigerant circuit 61 is also used in accumulator refrigerant accumulation control, which will be described later, and plays a role of moving excess refrigerant to the accumulator 24.
- liquid side shutoff valve 26 and the gas side shutoff valve 27 are connected to external equipment and piping (specifically, liquid refrigerant It is a valve provided at the connection port with the communication pipe 6 and the gas refrigerant communication pipe 7). Liquid side closing valve
- the gas side closing valve 27 is connected to the four-way switching valve 22.
- the outdoor unit 2 is provided with various sensors. Specifically, the outdoor unit 2 includes a suction pressure sensor 29 that detects the suction pressure of the compressor 21, a discharge pressure sensor 30 that detects the discharge pressure of the compressor 21, and a suction temperature of the compressor 21. An intake temperature sensor 31 and a discharge temperature sensor 32 for detecting the discharge temperature of the compressor 21 are provided. The suction temperature sensor 31 is provided at a position between the accumulator 24 and the compressor 21.
- the outdoor heat exchanger 23 has a heat exchange temperature sensor 33 for detecting the temperature of the refrigerant flowing in the outdoor heat exchanger 23 (that is, the refrigerant temperature corresponding to the condensation temperature during the cooling operation or the evaporation temperature during the heating operation). Is provided.
- a liquid side temperature sensor 34 for detecting the temperature Tb of the cooling medium On the liquid side of the outdoor heat exchanger 23, a liquid side temperature sensor 34 for detecting the temperature Tb of the cooling medium is provided.
- a liquid pipe temperature sensor 35 for detecting the refrigerant temperature (that is, the liquid pipe temperature) is provided at the outlet of the subcooler 25 on the main refrigerant circuit side.
- the junction circuit 61b of the bypass refrigerant circuit 61 is provided with a bypass temperature sensor 63 for detecting the temperature of the refrigerant flowing through the outlet of the subcooler 25 on the bypass refrigerant circuit 61 side.
- An outdoor air temperature sensor 36 for detecting the temperature of the outdoor air flowing into the unit is provided on the outdoor air inlet side of the outdoor unit 2.
- the outdoor unit 2 also has a first outdoor unit controller 50a (see FIG. 2) that controls the operation of each part constituting the outdoor unit 2.
- the first outdoor unit controller 50a includes a microcomputer, a memory, an inverter circuit that controls the motor of the compressor 21, and the like that are provided to control the outdoor unit 2, and the indoor unit. Control signals and the like can be exchanged with the four indoor unit control units 50c via the transmission line. That is, as shown in FIG. 2, the overall operation of the air conditioner 1 is controlled by the indoor unit controller 50c, the first outdoor unit controller 50a (and the second outdoor unit controller 50b), and the transmission line.
- the control unit 50 is configured.
- control unit 50 is connected so as to be able to receive detection signals of various sensors 29 to 36, 44 to 46, and 63, and based on these detection signals and the like, It is connected to various devices and valves so that valves 21, 22, 38, 41, 62, etc. can be controlled.
- the four-way switching valves 22, 122 are in the state shown by the solid line in FIG. 1, that is, the discharge side of the compressors 21, 121 is connected to the gas side of the outdoor heat exchangers 23, 123 and The suction sides of the machines 21 and 121 are connected to the gas side of the indoor heat exchanger 42 via the gas refrigerant communication pipe 7.
- the outdoor expansion valves 38 and 138 are fully opened.
- the opening of each indoor expansion valve 41 is adjusted so that the superheat degree of the refrigerant at the outlet of the indoor heat exchanger 42 (that is, the gas side of the indoor heat exchanger 42) is constant at the superheat degree target value. It has become.
- the degree of superheat of the refrigerant at the outlet of each indoor heat exchanger 42 is determined from the refrigerant temperature value detected by the gas side temperature sensor 45 and the refrigerant temperature value (evaporation) detected by the liquid side temperature sensor 44.
- the suction pressure of the compressors 21 and 121 detected by the suction pressure sensors 29 and 129 is converted into a saturation temperature value corresponding to the evaporation temperature, and the gas side This is detected by subtracting the saturation temperature value of the refrigerant from the refrigerant temperature value detected by the temperature sensor 45.
- a temperature sensor for detecting the temperature of the refrigerant flowing in each indoor heat exchanger 42 is provided, and a refrigerant temperature value corresponding to the evaporation temperature detected by this temperature sensor is set.
- the refrigerant superheat degree at the outlet of each indoor heat exchanger 42 may be detected by subtracting from the refrigerant temperature value detected by the gas side temperature sensor 45.
- the opening degree of the bypass valves 62, 162 is adjusted so that the superheat degree of the refrigerant at the outlet of the supercoolers 25, 125 on the bypass refrigerant circuit 61 side becomes the superheat degree target value.
- the degree of superheat of the refrigerant at the outlet on the bypass refrigerant circuit 61 side of the supercoolers 25 and 125 Is obtained by converting the suction pressure of the compressors 21 and 121 detected by the suction pressure sensors 29 and 129 into a saturation temperature value corresponding to the evaporation temperature, and from the refrigerant temperature value detected by the no-pass temperature sensors 63 and 163. It is detected by subtracting the saturation temperature value of this refrigerant.
- a temperature sensor is provided at the inlet of the bypass refrigerant circuit 61 side of the subcoolers 25 and 125, and the refrigerant temperature value detected by this temperature sensor is used as the bypass temperature sensor 63. , 163 may be subtracted from the refrigerant temperature value to detect the degree of superheat of the refrigerant at the outlet of the subcooler 25, 125 on the bypass refrigerant circuit 61 side.
- the low-pressure gas refrigerant is sucked into the compressors 21 and 121, compressed, and compressed. It becomes a gas refrigerant.
- the high-pressure gas refrigerant is sent to the outdoor heat exchangers 23 and 123 via the four-way switching valves 22 and 122, and is condensed by exchanging heat with the outdoor air supplied by the outdoor fans 28 and 128. It becomes a high-pressure liquid refrigerant.
- the high-pressure liquid refrigerant passes through the outdoor expansion valves 38 and 138, flows into the subcoolers 25 and 125, exchanges heat with the refrigerant flowing through the bypass refrigerant circuits 61 and 161, and is further cooled and passed. It becomes cool.
- a part of the high-pressure liquid refrigerant condensed in the outdoor heat exchangers 23 and 123 is branched into the bypass refrigerant circuits 61 and 1601, and after being decompressed by the bypass valves 62 and 162, Returned to the suction side.
- a part of the refrigerant passing through the bypass valves 62 and 162 is evaporated by being reduced to near the suction pressure of the compressors 21 and 121.
- the high-pressure liquid refrigerant sent to the indoor unit 4 is reduced to near the suction pressure of the compressors 21 and 121 by the indoor expansion valve 41 to become a low-pressure gas-liquid two-phase refrigerant, and the indoor heat exchanger 42 In the indoor heat exchanger 42, heat is exchanged with room air to evaporate and become a low-pressure gas refrigerant.
- This low-pressure gas refrigerant is sent to the outdoor units 2, 102 via the gas refrigerant communication pipe 7. Then, it flows into the accumulators 24 and 124 via the four-way switching valves 22 and 122. The low-pressure gas refrigerant flowing into the accumulators 24 and 124 is again sucked into the compressors 21 and 121.
- the four-way switching valves 22, 122 are in the state indicated by the broken lines in FIG. 1, that is, the discharge side of the compressors 21, 121 is connected to the gas side of the indoor heat exchanger 42 via the gas refrigerant communication pipe 7.
- the suction side of the compressors 21 and 121 is connected to the gas side of the outdoor heat exchangers 23 and 123.
- the outdoor expansion valves 38 and 138 are adjusted in opening to reduce the refrigerant flowing into the outdoor heat exchangers 23 and 123 to a pressure at which the refrigerant can evaporate in the outdoor heat exchangers 23 and 123 (that is, evaporation pressure).
- the opening of the indoor expansion valve 41 is adjusted so that the degree of supercooling of the refrigerant at the outlet of the indoor heat exchanger 42 becomes constant at the target value of the degree of supercooling.
- the degree of supercooling of the refrigerant at the outlet of the indoor heat exchanger 42 is the saturation temperature value corresponding to the condensing temperature of the discharge pressures of the compressors 21 and 121 detected by the discharge pressure sensors 30 and 130.
- the refrigerant temperature is detected by subtracting the refrigerant temperature value detected by the liquid side temperature sensor 44 from the saturation temperature value of the refrigerant.
- a temperature sensor for detecting the temperature of the refrigerant flowing in each indoor heat exchanger 42 is provided, and a refrigerant temperature value corresponding to the condensation temperature detected by this temperature sensor is set.
- the degree of refrigerant subcooling at the outlet of the indoor heat exchanger 42 may be detected by subtracting the refrigerant temperature value detected by the liquid side temperature sensor 44. Further, the bypass valves 62 and 162 are closed.
- the low-pressure gas refrigerant is sucked and compressed by the compressors 21 and 121, and the high-pressure gas refrigerant. It is sent to the indoor unit 4 via the four-way switching valves 22 and 122 and the gas refrigerant communication pipe 7.
- the high-pressure gas refrigerant sent to the indoor unit 4 undergoes heat exchange with the indoor air in the indoor heat exchanger 42 to condense into a high-pressure liquid refrigerant, and then passes through the indoor expansion valve 41. Through When it passes, the pressure is reduced according to the opening degree of the indoor expansion valve 41.
- the refrigerant that has passed through the indoor expansion valve 41 is sent to the outdoor units 2 and 102 via the liquid refrigerant communication pipe 6 and further depressurized via the subcoolers 25 and 125 and the outdoor expansion valves 38 and 138. Later, it flows into the outdoor heat exchangers 23 and 123. Then, the low-pressure gas-liquid two-phase refrigerant flowing into the outdoor heat exchangers 23 and 123 exchanges heat with the outdoor air supplied by the outdoor fans 28 and 128 to evaporate into low-pressure gas refrigerant. It flows into the accumulators 24 and 124 via the four-way switching valves 22 and 122. Then, the low-pressure gas refrigerant flowing into the accumulators 24 and 124 is sucked into the compressors 21 and 121 again.
- the surplus refrigerant when surplus refrigerant is generated during cooling, the surplus refrigerant is controlled to be accumulated in the accumulators 24 and 124 via the bypass refrigerant circuits 61 and 161.
- the surplus refrigerant control during the cooling operation will be described with reference to FIG.
- the main part of each step is the control unit 50.
- step S11 it is determined whether or not three predetermined conditions are satisfied.
- the first condition is that the flag G of other outdoor units (referred to as other units in the drawing) is 0. This flag G is 1 when an accumulator refrigerant reservoir control (steps S14 to S16) described later is being performed, and is 0 when not being performed.
- the second condition is that the difference between the liquid refrigerant saturation temperature Tel of the outdoor unit itself (indicated in the drawing) and the liquid refrigerant temperature Tb of the outdoor heat exchangers 23 and 123, that is, the outdoor heat exchanger.
- the condition is that the degree of supercooling on the liquid side of 23 and 123 is greater than the predetermined value SC1.
- the liquid refrigerant temperature Tb is a detection value of the liquid side temperature sensor 34 disposed on the liquid side of the outdoor heat exchangers 23 and 123.
- the third condition is that the high pressure HP of the outdoor unit itself exceeds a predetermined value HPbl.
- the high pressure HP is a value detected by the discharge pressure sensors 30 and 130 that detect the discharge pressure of the compressors 21 and 121.
- the second and third conditions are conditions that occur when a large amount of refrigerant accumulates in the outdoor heat exchangers 23 and 123. In step S11, if these three conditions are satisfied, the process proceeds to step S13. If the three conditions are not satisfied, the process proceeds to step S12.
- step S12 it is determined whether or not three conditions different from step S11 are satisfied.
- the first condition is that the other indoor unit flag G is 1, that is, that the accumulator refrigerant accumulation control is performed in the other indoor units.
- the second condition is that the difference between the liquid refrigerant saturation temperature Tcl of the other outdoor units and the liquid refrigerant temperature Tb of the outdoor heat exchangers 23 and 123, that is, the degree of supercooling on the liquid side of the outdoor heat exchangers 23 and 123, The condition is larger than the predetermined value SC1.
- the third condition is that the high pressure HP of the other outdoor units exceeds a predetermined value HPbl.
- step S12 if these three conditions are satisfied, the process proceeds to step S13. If the three conditions are satisfied, the process returns to step S11.
- step S13 it is determined whether or not other conditions for shifting to the accumulator refrigerant accumulation control in step S14 and subsequent steps are satisfied. Specifically, when a predetermined time has not elapsed since startup, when a predetermined time has not elapsed since oil return operation, when an automatic refrigerant charging operation is performed, when a test operation is performed, refrigerant leakage detection Judgment power to not shift to accumulator refrigerant accumulation control during operation, etc. S is performed in step S13. In that case, the process returns to step S11.
- step S14 a flag G indicating that the accumulator refrigerant accumulation control is being performed is set to 1, and a flag F indicating 1 that the accumulator refrigerant accumulation control has been performed is set to 1.
- step S14 the degree of opening of the bypass valves 62 and 162 of the bypass refrigerant circuits 61 and 161 that guide the liquid refrigerant to the accumulators 24 and 124 between the outdoor heat exchangers 23 and 123 and the supercoolers 25 and 125
- the predetermined opening is made larger than the opening.
- the increase in the opening degree of the bypass valves 62, 162 is repeatedly performed at predetermined time intervals.
- step S15 or step S16 is made, and when the predetermined condition is met, the process goes out of the loop of steps S14 to S16.
- step S15 it is determined whether one of the two conditions is satisfied.
- the first condition is that the degree of superheat SH of the gas refrigerant on the discharge side of the compressors 21 and 121 (hereinafter referred to as discharge SH) is below a predetermined value SH1.
- the second condition is that the bypass valves 62 and 162 are fully opened.
- step S15 either condition is met.
- the flag G related to the execution of the accumulator refrigerant accumulation control is set to 0 and the outdoor rotation control (described later) in step S18 is performed. Transition .
- step S15 determines whether one of the conditions in step S15 is satisfied. If none of the conditions in step S15 is satisfied, it is determined that there is room for adjustment of surplus refrigerant by the accumulators 24 and 124, and the process proceeds to step S16.
- step S16 if the predetermined condition of step S11 is satisfied and the process proceeds to step S14, the outdoor unit itself satisfies the predetermined condition of step S12 and the process proceeds to step S14. In other outdoor units that satisfy the above conditions, determine whether one of the following two conditions is met.
- the first condition is that the difference between the liquid refrigerant saturation temperature Tel and the liquid refrigerant temperature Tb of the outdoor heat exchangers 23 and 123, that is, the degree of supercooling on the liquid side of the outdoor heat exchangers 23 and 123 is from the predetermined value SC2. It is a condition that is also small.
- the predetermined value SC2 is a value smaller than the predetermined value SC1.
- the second condition is that the high pressure HP is below the predetermined value HPb2.
- the predetermined value HPb2 is a value smaller than the predetermined value HPbl described above.
- step S 17 the flag G relating to execution of the accumulator refrigerant accumulation control is set to zero.
- step S16 it is necessary to continue accumulator refrigerant accumulation control to eliminate refrigerant stagnation in the outdoor heat exchangers 23 and 123, and the process returns to step S14.
- the surplus refrigerant when surplus refrigerant is generated during cooling, the surplus refrigerant is controlled to be accumulated in the accumulators 24 and 124 via the bypass refrigerant circuits 61 and 161.
- the surplus refrigerant control during the heating operation will be described with reference to FIG.
- the main part of each step is the control unit 50.
- step S21 it is determined whether or not three predetermined conditions are satisfied.
- the first condition is that the flag G of another outdoor unit is 0.
- the second condition is that the target value SHS of the superheat degree on the suction side of the compressors 21 and 121 of the outdoor unit itself is predetermined.
- the condition is that the value is smaller than SH5.
- the third condition is that the outdoor expansion valves 38 and 138 of the outdoor unit itself are fully opened.
- the second and third conditions are conditions that occur when excess refrigerant accumulates in the indoor heat exchanger 42 and it becomes difficult to control the indoor expansion valve 41.
- step S21 if these three conditions are satisfied, the process proceeds to step S23. If not, the process proceeds to step S22.
- step S22 it is determined whether or not three conditions different from step S21 are satisfied.
- the first condition is that the other indoor unit flag G is 1, that is, that the accumulator refrigerant accumulation control is performed in the other indoor units.
- the second condition is that the target value SHS of the superheat degree on the suction side of the compressors 21 and 121 of other outdoor units is smaller than the predetermined value SH5.
- the third condition is that the outdoor expansion valves 38 and 138 of other outdoor units are fully opened.
- the second and third conditions are conditions that arise when excess refrigerant accumulates in the indoor heat exchanger 42 and it becomes difficult to control the indoor expansion valve 41.
- step S22 if these three conditions are satisfied, the process proceeds to step S23, and if these three conditions are not satisfied, the process returns to step S21.
- step S23 it is determined whether or not the other conditions for shifting to the accumulator refrigerant accumulation control after step S24 are satisfied. Specifically, when the predetermined time has not elapsed since startup, when the predetermined time has not elapsed after the oil return operation, or when the predetermined time has elapsed after the defrost operation, the accumulator refrigerant reservoir A determination is made in step S23 that control should not be transferred. In that case, return to step S21.
- step S24 flag G is set to 1
- flag F indicating 1 that the accumulator refrigerant accumulation control has been performed is set to 1.
- the opening of the bypass valves 62 and 162 of the bypass refrigerant circuits 61 and 161 that lead the night refrigerant to the accumulators 24 and 124 by the force between the outdoor heat exchangers 23 and 123 and the supercooler P 25 and 125 Increase the current opening by a predetermined opening.
- the increase in the opening degree of the bypass valves 62, 162 is repeated at predetermined time intervals.
- step S25 it is determined whether or not one of the two conditions is satisfied.
- the first condition is that the discharge SH has fallen below a predetermined value SH1.
- the second condition is that the bypass valves 62 and 162 are fully opened.
- step S25 when it is determined that any of the conditions is satisfied and it is difficult to adjust the surplus refrigerant only by the accumulator refrigerant accumulation control in the outdoor unit itself, the flag G relating to the execution of the accumulator refrigerant accumulation control is set to 0, The process proceeds to outdoor rotation control (described later) in step S28.
- step S26 it is determined that there is room for adjustment of the surplus refrigerant by the accumulators 24 and 124, and the process proceeds to step S26.
- step S26 when the predetermined condition of step S21 is satisfied and the process proceeds to step S24, the outdoor unit itself has satisfied the predetermined condition of step S22 and the process proceeds to step S24.
- Other conditions include the condition that all the indoor expansion valves 41 are open enough to be controlled when the opening is smaller than the predetermined opening, and other outdoor units that satisfy the condition of step S22. This is a condition that the discharge SH has become sufficiently high.
- step S27 the flag G regarding the execution of the accumulator refrigerant accumulation control is set to 0, and the opening degree of the bypass valve 62 is decreased.
- step S26 the condition in step S26 is not satisfied, the accumulator refrigerant accumulation control is continued, and the process returns to step S24.
- the discharge is performed.
- SH falls below the predetermined value SH1 or when the opening degree of the bypass valve 62 is fully opened, it is determined that excess refrigerant adjustment in the accumulators 24 and 124 reaches a limit, and excess refrigerant exists in the outdoor unit. Shift to outdoor rotation control as shown in Fig. 5.
- step S42 it is determined whether there is a stopped outdoor unit. If yes, go to Step S46, otherwise go to Step S43.
- step S43 it is determined whether or not there is an outdoor unit (denoted as an “operator” in FIG. 5) whose discharge SH is greater than a predetermined value SH1. If there is such an outdoor unit, go to Step S44, and if not, go to Step S47.
- an outdoor unit denoted as an “operator” in FIG. 5
- step S44 a predetermined operation E is performed.
- the opening degree of the bypass valves 62 and 162 is set to a predetermined small opening degree (for the outdoor unit in which the discharge SH is less than the predetermined value SH1 or the outdoor unit in which the bypass valves 62 and 162 are fully opened). Or fully closed). Then, the accumulator refrigerant accumulation control is performed in the outdoor unit in which the discharge SH is larger than the predetermined value SH1.
- the opening degree of the bypass valves 62, 162 is also left to normal control.
- step S45 it is determined whether or not the outdoor unit whose discharge SH is larger than the predetermined value SH1 has been stopped. If not stopped, the process returns to step S44. If stopped, go to step S46.
- step S46 a predetermined operation D is performed.
- operation D the stopped outdoor unit is started, and rotation is performed to stop other outdoor units (outdoor units whose discharge SH is below the predetermined value SH1) instead. If this operation D is repeated three times within a predetermined period (for example, one hour), the process proceeds from step S46 to step S47.
- a predetermined operation A is performed.
- the opening degree of the bypass valves 62 and 162 is set to a predetermined small opening degree (or fully closed).
- the outdoor unit with the opening of the bypass valves 62, 162 set to a predetermined small opening (or fully closed) is returned to normal control, and the bypass valves 62, 162 are returned to normal control.
- the degree of opening is also left to normal control.
- a predetermined operation C is performed.
- the opening of the bypass valves 62 and 162 is set to a predetermined small opening (for an outdoor unit in which the discharge SH is less than the predetermined value SH1 or an outdoor unit in which the bypass valves 62 and 162 are fully opened). Or fully closed).
- accumulator refrigerant accumulation control is performed.
- the outdoor unit whose bypass valve 62, 162 is set to a predetermined small opening (or fully closed) is returned to normal control, and the bypass valve 62, 162 is returned to normal control.
- step S50 it is determined whether there is a stopped outdoor unit. Stopped outdoor If there is a knit, the process proceeds to step S51, and if not, the process returns to step S49.
- step S51 a predetermined operation B is performed.
- the above operation is also applicable to the operation of the air conditioner 1 in which only the two outdoor units 2 and 102 shown in Fig. 1 exist as heat source units, but three or more outdoor units are present.
- the operation can be applied as it is even when connected in parallel, and the outdoor unit is described without a reference numeral.
- the control unit 50 of the air conditioner 1 first performs accumulator coolant accumulation control, and determines that the amount of refrigerant is excessive during the accumulator refrigerant accumulation control (step S15). Alternatively, in step S25), the operation is shifted to the outdoor rotation control in which the stopped outdoor unit is started or the accumulator refrigerant accumulation control is performed in the other outdoor units in operation. In this way, the accumulator refrigerant accumulation control is first executed, and the surplus refrigerant is adjusted in the outdoor unit itself in which the surplus refrigerant is generated, so that the number of times of affecting other outdoor units is minimized. [0060] (2)
- the control unit 50 determines that the adjustment of the surplus refrigerant by the accumulators 24 and 124 has reached the limit because the discharge SH is less than the predetermined value SH1 or the opening degree of the bypass valves 62 and 162 is fully opened. That is, when it is determined that the amount of refrigerant in the outdoor unit has become excessive, the outdoor rotation control is performed such that the outdoor unit that is stopped is started or the accumulator refrigerant accumulation control is performed in another outdoor unit that is in operation. Transition (Step S15, Step S25). According to this outdoor rotation control, surplus that satisfies the conditions of Step S15 and Step S25 by activating other heat source units that are in a stopped state or performing accumulator coolant accumulation control with other heat source units.
- the refrigerant can be moved from the outdoor unit in which the refrigerant is excessively generated to another outdoor unit. For this reason, if the configuration of the air conditioner 1 according to the present embodiment is adopted, even if the capacity of the accumulators 24 and 124 is designed to be relatively small, excess surplus refrigerant stays in the outdoor units 2 and 102 and is smooth. It is possible to prevent the driving from being hindered.
- bypass refrigerant circuits 61 and 161 which are circuits as cooling sources for the subcooler 25, are used as circuits for introducing excess liquid refrigerant to the accumulators 24 and 124.
- a circuit for cooling the refrigerant sent from the outdoor heat exchanger 23 to the indoor expansion valve 41 and a circuit for moving the surplus refrigerant to the accumulator 24 are combined into one bypass refrigerant circuit (first outdoor unit 2 In this case, the bypass refrigerant circuit 61 and the second outdoor unit 102 are shared by the bypass refrigerant circuit 161). As a result, the cost of outdoor units 2, 102 is reduced.
- the control unit 50 of the air conditioner 1 gives priority to starting any other outdoor units that are stopped (steps S42, S46, and S48). And step S51). As a result, the operation of the outdoor unit may be continued in the presence of excess refrigerant. , Is to be resolved quickly.
- the outdoor unit that has once performed accumulator refrigerant accumulation control is in a state where a relatively large amount of liquid refrigerant is accumulated in the accumulators 24 and 124 at the end of the control, and even if the refrigerant moves after that, the accumulator There is a high possibility that a large amount of refrigerant has accumulated in 24 and 124. Therefore, when the control unit 50 of the air conditioner 1 determines that the amount of refrigerant in the outdoor unit is excessive (step S15, step S25), the flag indicating the accumulator refrigerant accumulation control is displayed.
- the surplus liquid refrigerant is moved to the accumulators 24 and 124 by using the bypass refrigerant circuits 61 and 161 which are circuits as the cooling source of the supercooler 25.
- the surplus liquid refrigerant is accumulated in the accumulator.
- Another dedicated circuit leading to 24 and 124 may be provided.
- the fact that the operation A of step S47 of the outdoor rotation control is repeated means that there is a strong possibility that the refrigerant circuit 10 of the air conditioner 1 is excessively filled with refrigerant.
- an alarm may be issued informing the refrigerant overfill.
- a warning display may be output to a remote control or the like.
- the air conditioner according to the present invention can suppress the fact that excessive surplus refrigerant stays in the outdoor unit and prevents smooth operation even when the capacity of the accumulator is relatively small. It is useful as an air conditioner having a plurality of heat source units in one refrigerant circuit.
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
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US12/278,321 US9239175B2 (en) | 2006-02-20 | 2007-02-15 | Air conditioner and heat source unit with other unit start up control |
AU2007218821A AU2007218821B2 (en) | 2006-02-20 | 2007-02-15 | Air conditioner and heat source unit |
CN2007800053628A CN101384866B (zh) | 2006-02-20 | 2007-02-15 | 空调装置和热源单元 |
EP07708407.7A EP1995536B1 (en) | 2006-02-20 | 2007-02-15 | Air conditioner |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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JP2006042558A JP4120682B2 (ja) | 2006-02-20 | 2006-02-20 | 空気調和装置および熱源ユニット |
JP2006-042558 | 2006-02-20 |
Publications (1)
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WO2007097238A1 true WO2007097238A1 (ja) | 2007-08-30 |
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PCT/JP2007/052677 WO2007097238A1 (ja) | 2006-02-20 | 2007-02-15 | 空気調和装置および熱源ユニット |
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Country | Link |
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US (1) | US9239175B2 (ja) |
EP (1) | EP1995536B1 (ja) |
JP (1) | JP4120682B2 (ja) |
KR (1) | KR100989623B1 (ja) |
CN (1) | CN101384866B (ja) |
AU (1) | AU2007218821B2 (ja) |
WO (1) | WO2007097238A1 (ja) |
Families Citing this family (39)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2007139225A (ja) * | 2005-11-15 | 2007-06-07 | Hitachi Ltd | 冷凍装置 |
JP5401806B2 (ja) * | 2008-02-29 | 2014-01-29 | ダイキン工業株式会社 | 空気調和装置および冷媒量判定方法 |
JP2010032104A (ja) * | 2008-07-29 | 2010-02-12 | Hitachi Appliances Inc | 空気調和機 |
JP2010032105A (ja) * | 2008-07-29 | 2010-02-12 | Hitachi Appliances Inc | 空気調和機 |
JP4864110B2 (ja) * | 2009-03-25 | 2012-02-01 | 三菱電機株式会社 | 冷凍空調装置 |
EP2413065B1 (en) * | 2009-03-26 | 2019-05-08 | Mitsubishi Electric Corporation | Refrigerator |
JP5484890B2 (ja) * | 2009-12-25 | 2014-05-07 | 三洋電機株式会社 | 冷凍装置 |
JP5484889B2 (ja) * | 2009-12-25 | 2014-05-07 | 三洋電機株式会社 | 冷凍装置 |
JP5409405B2 (ja) * | 2010-01-12 | 2014-02-05 | 日立アプライアンス株式会社 | 空気調和装置 |
JP5352512B2 (ja) * | 2010-03-31 | 2013-11-27 | 日立アプライアンス株式会社 | 空気調和機 |
JP5610843B2 (ja) * | 2010-05-24 | 2014-10-22 | 三菱電機株式会社 | 空気調和装置 |
KR101712213B1 (ko) * | 2011-04-22 | 2017-03-03 | 엘지전자 주식회사 | 멀티형 공기조화기 및 그의 제어방법 |
CN102226600B (zh) * | 2011-06-10 | 2012-10-17 | 江苏天舒电器有限公司 | 一种双系统热回收多功能泳池一体机 |
JP5257491B2 (ja) * | 2011-06-30 | 2013-08-07 | ダイキン工業株式会社 | 冷凍装置の室外機 |
JP6003160B2 (ja) * | 2011-09-30 | 2016-10-05 | 株式会社富士通ゼネラル | 空気調和装置 |
KR20130041640A (ko) * | 2011-10-17 | 2013-04-25 | 엘지전자 주식회사 | 공기조화기 및 그 운전 방법 |
JP5746962B2 (ja) * | 2011-12-20 | 2015-07-08 | 株式会社神戸製鋼所 | ガス供給方法およびガス供給装置 |
JP5765278B2 (ja) * | 2012-03-21 | 2015-08-19 | ダイキン工業株式会社 | 室外マルチ型空気調和装置 |
JP6021943B2 (ja) * | 2012-12-13 | 2016-11-09 | 三菱電機株式会社 | 空気調和装置 |
JP5787102B2 (ja) * | 2013-01-11 | 2015-09-30 | ダイキン工業株式会社 | 分離型空気調和装置 |
JP6017058B2 (ja) * | 2013-10-24 | 2016-10-26 | 三菱電機株式会社 | 空気調和装置 |
JP6291794B2 (ja) * | 2013-10-31 | 2018-03-14 | 株式会社富士通ゼネラル | 空気調和機 |
EP3098531B1 (en) * | 2014-01-21 | 2018-06-20 | Mitsubishi Electric Corporation | Air conditioner |
JP5751355B1 (ja) * | 2014-01-31 | 2015-07-22 | ダイキン工業株式会社 | 冷凍装置 |
CN104235978B (zh) * | 2014-08-22 | 2017-04-12 | 海信(山东)空调有限公司 | 蓄冷蓄热型空调机 |
JP6394683B2 (ja) * | 2016-01-08 | 2018-09-26 | 株式会社デンソー | 輸送用冷凍装置 |
JP6350577B2 (ja) * | 2016-03-31 | 2018-07-04 | ダイキン工業株式会社 | 空気調和装置 |
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CN111271892B (zh) * | 2018-12-05 | 2021-11-05 | 约克广州空调冷冻设备有限公司 | 制冷系统 |
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AU2019429836B2 (en) * | 2019-02-22 | 2022-07-28 | Mitsubishi Electric Corporation | Indoor unit and air-conditioning apparatus |
EP3967949A4 (en) * | 2019-05-14 | 2023-01-11 | Toshiba Carrier Corporation | HEAT SOURCE SYSTEM |
JP6881503B2 (ja) * | 2019-05-31 | 2021-06-02 | ダイキン工業株式会社 | 空調システム |
EP4212798A1 (en) | 2020-09-14 | 2023-07-19 | Toshiba Carrier Corporation | Air conditioning apparatus |
KR20220040220A (ko) * | 2020-09-23 | 2022-03-30 | 엘지전자 주식회사 | 냉난방환기 멀티 공기조화기 |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH05288422A (ja) * | 1992-04-09 | 1993-11-02 | Sanyo Electric Co Ltd | 空気調和装置 |
JPH1163711A (ja) | 1997-08-25 | 1999-03-05 | Mitsubishi Electric Corp | マルチ空気調和装置 |
JPH11108472A (ja) * | 1997-10-02 | 1999-04-23 | Mitsubishi Electric Corp | 空気調和装置 |
JPH11257762A (ja) * | 1998-03-12 | 1999-09-24 | Denso Corp | 冷凍サイクル装置 |
JP2000146345A (ja) * | 1998-11-04 | 2000-05-26 | Daikin Ind Ltd | 冷凍装置 |
JP2001041528A (ja) | 1999-07-28 | 2001-02-16 | Hitachi Ltd | マルチ形空気調和機 |
Family Cites Families (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH06103130B2 (ja) * | 1990-03-30 | 1994-12-14 | 株式会社東芝 | 空気調和機 |
JP2909190B2 (ja) * | 1990-11-02 | 1999-06-23 | 株式会社東芝 | 空気調和機 |
JP3163121B2 (ja) * | 1991-06-28 | 2001-05-08 | 東芝キヤリア株式会社 | 空気調和機 |
TW212224B (ja) * | 1992-02-28 | 1993-09-01 | Sanyo Denki Kk | |
JP3060770B2 (ja) * | 1993-02-26 | 2000-07-10 | ダイキン工業株式会社 | 冷凍装置 |
JP3289366B2 (ja) * | 1993-03-08 | 2002-06-04 | ダイキン工業株式会社 | 冷凍装置 |
JPH07234038A (ja) * | 1994-02-18 | 1995-09-05 | Sanyo Electric Co Ltd | 多室型冷暖房装置及びその運転方法 |
JPH08189719A (ja) * | 1995-01-12 | 1996-07-23 | Mitsubishi Electric Corp | 空気調和装置 |
JP3603514B2 (ja) * | 1996-12-20 | 2004-12-22 | ダイキン工業株式会社 | 冷凍装置 |
JP3327215B2 (ja) * | 1998-07-22 | 2002-09-24 | 三菱電機株式会社 | 空気調和機の冷媒充填量決定方法 |
JP3085296B2 (ja) * | 1998-12-25 | 2000-09-04 | ダイキン工業株式会社 | 冷凍装置 |
JP2001091071A (ja) * | 1999-09-24 | 2001-04-06 | Sanyo Electric Co Ltd | 多段圧縮冷凍装置 |
JP3940840B2 (ja) * | 2002-11-22 | 2007-07-04 | ダイキン工業株式会社 | 空気調和装置 |
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 |
JP4459776B2 (ja) * | 2004-10-18 | 2010-04-28 | 三菱電機株式会社 | ヒートポンプ装置及びヒートポンプ装置の室外機 |
KR100640855B1 (ko) * | 2004-12-14 | 2006-11-02 | 엘지전자 주식회사 | 멀티 공기조화기의 제어 방법 |
-
2006
- 2006-02-20 JP JP2006042558A patent/JP4120682B2/ja active Active
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2007
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- 2007-02-15 CN CN2007800053628A patent/CN101384866B/zh active Active
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Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH05288422A (ja) * | 1992-04-09 | 1993-11-02 | Sanyo Electric Co Ltd | 空気調和装置 |
JPH1163711A (ja) | 1997-08-25 | 1999-03-05 | Mitsubishi Electric Corp | マルチ空気調和装置 |
JPH11108472A (ja) * | 1997-10-02 | 1999-04-23 | Mitsubishi Electric Corp | 空気調和装置 |
JPH11257762A (ja) * | 1998-03-12 | 1999-09-24 | Denso Corp | 冷凍サイクル装置 |
JP2000146345A (ja) * | 1998-11-04 | 2000-05-26 | Daikin Ind Ltd | 冷凍装置 |
JP2001041528A (ja) | 1999-07-28 | 2001-02-16 | Hitachi Ltd | マルチ形空気調和機 |
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AU2007218821B2 (en) | 2010-05-27 |
CN101384866A (zh) | 2009-03-11 |
US20090056358A1 (en) | 2009-03-05 |
EP1995536B1 (en) | 2018-10-10 |
JP2007218558A (ja) | 2007-08-30 |
KR20080091397A (ko) | 2008-10-10 |
US9239175B2 (en) | 2016-01-19 |
AU2007218821A1 (en) | 2007-08-30 |
JP4120682B2 (ja) | 2008-07-16 |
KR100989623B1 (ko) | 2010-10-26 |
EP1995536A4 (en) | 2014-06-18 |
EP1995536A1 (en) | 2008-11-26 |
CN101384866B (zh) | 2011-03-09 |
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