WO2016002021A1 - 空気調和装置 - Google Patents
空気調和装置 Download PDFInfo
- Publication number
- WO2016002021A1 WO2016002021A1 PCT/JP2014/067618 JP2014067618W WO2016002021A1 WO 2016002021 A1 WO2016002021 A1 WO 2016002021A1 JP 2014067618 W JP2014067618 W JP 2014067618W WO 2016002021 A1 WO2016002021 A1 WO 2016002021A1
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- WIPO (PCT)
- Prior art keywords
- refrigerant
- pipe
- gas
- heat exchanger
- bypass
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/89—Arrangement or mounting of control or safety devices
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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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
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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
- F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
- F24F11/63—Electronic processing
- F24F11/65—Electronic processing for selecting an operating mode
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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
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
- F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
- F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
- F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
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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
- F24F2140/00—Control inputs relating to system states
- F24F2140/20—Heat-exchange fluid temperature
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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
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/006—Compression machines, plants or systems with reversible cycle not otherwise provided for two pipes connecting the outdoor side to the indoor side with multiple indoor units
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
- F25B2313/0231—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with simultaneous cooling and heating
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/023—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
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/0272—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using bridge circuits of one-way valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/031—Sensor arrangements
- F25B2313/0314—Temperature sensors near the indoor heat exchanger
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/23—Separators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/19—Calculation of parameters
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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
- F25B2600/25—Control of valves
- F25B2600/2509—Economiser 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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1931—Discharge pressures
Definitions
- the present invention relates to an air conditioner including a control unit.
- Patent Document 1 there is known an air conditioner capable of performing a cooling and heating mixed operation in which a heating operation and a cooling operation are independently performed in a plurality of load side units connected to a heat source side unit (see, for example, Patent Document 1). .
- the air conditioner disclosed in Patent Document 1 has a refrigerant flow path so that the heat source side heat exchanger acts as an evaporator or a condenser according to a heating load or a cooling load required in the load side unit. Can be switched.
- the heat source side heat exchanger acts as an evaporator
- the heat source side heat exchanger is Acts as a condenser. Further, the refrigerant flowing out from the heat source side unit is supplied to the load side unit by the relay, and the flow direction in the load side unit is switched.
- control called dievaporation temperature control may be performed during heating main operation with a large heating load ratio.
- This dual evaporation temperature control is performed on the inlet side of the heat source side heat exchanger of the heat source side unit that acts as an evaporator under the condition that the liquid pipe temperature of the load side unit that is performing the cooling operation is equal to or lower than a predetermined temperature.
- the installed on-off valve is closed, and the opening degree of the expansion device installed in parallel with the on-off valve is controlled so that the evaporation temperature of the heat source side heat exchanger falls within a predetermined range.
- the flow rate of the refrigerant flowing into the heat source side heat exchanger of the heat source side unit is changed by controlling the opening degree of the expansion device.
- the operating efficiency of an air conditioning apparatus may deteriorate.
- pressure loss downstream of the heat source side heat exchanger and the heat source side heat exchanger may be reduced by changing the flow rate of the refrigerant flowing into the heat source side heat exchanger.
- the gas-liquid separator is provided in the air conditioning apparatus, the refrigerant separation ratio in the gas-liquid separator may be destroyed.
- the present invention has been made against the background of the above problems, and provides an air conditioner that improves the operating efficiency of the air conditioner.
- An air-conditioning apparatus is a gas-liquid separator that separates refrigerant in an air-conditioning apparatus in which refrigerant flows and a compressor, a load-side heat exchanger, an expansion unit, and a heat-source-side heat exchanger are connected by piping.
- bypass pipe connecting the gas-liquid separator and the suction side of the compressor, a bypass throttle provided in the bypass pipe for adjusting the flow rate of the refrigerant, and a flow rate of the refrigerant flowing into the heat source side heat exchanger
- the bypass flow rate of the refrigerant flowing through the bypass piping calculated based on the opening degree of the heat source side throttle unit and the heat source side throttle unit, the inflow rate of the refrigerant flowing into the gas-liquid separator, and the dryness of the inlet of the gas-liquid separator
- a control unit for adjusting the opening of the bypass throttling unit.
- control unit adjusts the opening of the bypass throttle unit based on the bypass flow rate, the inflow rate, and the inlet dryness, the operation efficiency of the air conditioner is improved.
- FIG. 1 is a circuit diagram showing an air conditioner 1 according to Embodiment 1.
- FIG. 3 is a block diagram showing a control unit 80 of the air-conditioning apparatus 1 according to Embodiment 1.
- FIG. FIG. 3 is a circuit diagram showing a heating only operation in the first embodiment.
- FIG. 3 is a circuit diagram illustrating a main heating operation in the first embodiment.
- FIG. 3 is a circuit diagram showing a cooling only operation in the first embodiment.
- FIG. 3 is a circuit diagram illustrating a cooling main operation in the first embodiment.
- 3 is a flowchart showing the operation of the air conditioning apparatus 1 according to Embodiment 1.
- 3 is a flowchart showing the operation of the air conditioning apparatus 1 according to Embodiment 1.
- FIG. 1 is a circuit diagram showing an air conditioner 1 according to Embodiment 1.
- the air conditioner 1 will be described with reference to FIG.
- the air conditioner 1 is installed in a building or a condominium, for example, and uses a heat pump cycle that is a refrigeration cycle in which a refrigerant circulates, and can perform a cooling and heating mixed operation.
- the air conditioner 1 includes a refrigerant circuit 2 and a control unit in which a heat source side unit 3 and a load side unit group 5 including a plurality of load side units are connected by a pipe via a relay unit 4. 80.
- the heat source side unit 3 and the relay unit 4 are connected by a high-pressure pipe 72 and a low-pressure pipe 73, and the relay unit 4 switches the flow direction of the refrigerant flowing in from the high-pressure pipe 72 or the low-pressure pipe 73.
- the heating operation and the cooling operation are performed independently.
- the relay unit 4 and the load side unit group 5 are connected by a liquid pipe 79 and a gas pipe 78.
- refrigerant examples of the refrigerant circulating in the refrigerant circuit 2 include natural refrigerants such as carbon dioxide, hydrocarbons, and helium, HFC410A, HFC407C, HFC404A and other refrigerants that do not contain chlorine, and R22 and R134a used in existing products.
- the refrigerant can be selected as appropriate.
- the heat source side unit 3 supplies cold heat or warm heat to the load side unit group 5.
- the heat source side unit 3 includes a compressor 31 that compresses the refrigerant, a flow path switch 32 that switches the flow direction of the refrigerant, a heat source side heat exchanger 34 that performs heat exchange between the heat medium and the refrigerant, and an accumulator that stores the liquid refrigerant. 36, and a gas-liquid separator 33 that separates the gas refrigerant and the liquid refrigerant.
- the compressor 31 sucks low-temperature and low-pressure gas refrigerant, compresses the gas refrigerant into high-temperature and high-pressure gas refrigerant, and discharges it to the refrigerant circuit 2. Thereafter, the refrigerant circulates through the refrigerant circuit 2, and air conditioning operation is performed in the air conditioning apparatus 1.
- the compressor 31 compresses the sucked refrigerant to a high pressure, and can be constituted by, for example, an inverter type compressor that can control the capacity.
- the compressor 31 is not limited to an inverter type compressor capable of such capacity control.
- the compressor 31 may be a constant speed type compressor, or a compressor combining an inverter type and a constant speed type. Also good.
- you may comprise a compressor using each type, such as a reciprocating, a rotary, a scroll, or a screw.
- the flow path switch 32 is provided on the discharge side of the compressor 31 and switches the refrigerant flow direction between the heating operation and the cooling operation.
- the flow direction of the refrigerant is such that the heat source side heat exchanger 34 acts as an evaporator in the heating operation, and the heat source side heat exchanger 34 acts as a condenser in the cooling operation.
- the flow path switch 32 can be a four-way valve, for example.
- the heat source side heat exchanger 34 is connected to the flow path switching device 32 by the first connection pipe 11 and performs heat exchange between the heat medium, for example, ambient outdoor air or water, and the refrigerant. .
- the heat source side heat exchanger 34 functions as an evaporator in the heating operation to evaporate the refrigerant, and functions as a condenser (heat radiator) in the cooling operation to condense and liquefy the refrigerant.
- the heat source side heat exchanger 34 is an air-cooled heat exchanger, and the heat source side blower 35 is provided in the vicinity of the heat source side heat exchanger 34.
- the heat source side blower 35 blows outdoor air or the like to the heat source side heat exchanger 34, and the evaporation capability or the condensation capability in the heat source side heat exchanger 34 is adjusted by the number of rotations thereof.
- a water circulation pump is provided in the vicinity of the heat source side heat exchanger 34.
- the heat source side heat exchanger 34 is provided. The evaporation capacity or the condensation capacity in is adjusted.
- the accumulator 36 is provided on the suction side of the compressor 31 and has a function of storing excess refrigerant and a function of separating liquid refrigerant and gas refrigerant. Only the liquid refrigerant is stored by the accumulator 36, and the gas refrigerant passes through the accumulator 36 and is sucked into the compressor 31.
- the gas-liquid separator 33 is provided between the heat source side heat exchanger 34 and the separation pipe 73a branched from the low pressure pipe 73 connecting the heat source side unit 3 and the relay unit 4, and also the gas-liquid separation.
- the vessel 33 and the accumulator 36 are connected by a bypass pipe 71.
- the gas-liquid separator 33 and the suction side of the compressor 31 are directly connected by the bypass pipe 71.
- the gas-liquid separator 33 separates the refrigerant flowing in from the high-pressure pipe 72 into liquid refrigerant and gas refrigerant, and the liquid refrigerant flows out to the heat source side heat exchanger 34 and the gas refrigerant flows out to the bypass pipe 71. To do.
- the gas-liquid separator 33 prevents the heat exchange in the heat source side heat exchanger 34 from being deteriorated by preventing the gas refrigerant from flowing out to the heat source side heat exchanger 34. .
- the gas-liquid separator 33 is provided in a separation pipe 73 a that branches from the low-pressure pipe 73. Thereby, when the heat source side heat exchanger 34 acts as a condenser, the pressure drop in the low pressure pipe 73 due to the pressure loss generated in the gas-liquid separator 33 is suppressed. Further, the gas-liquid separator 33 may be provided in the low pressure pipe 73 without providing the separate separation pipe 73a. Further, the gas-liquid separator 33 is not limited in its method or shape as long as the two-phase refrigerant can be separated into a gas phase and a liquid phase, and for example, a method such as gravity separation or centrifugal separation can be adopted. Furthermore, the separation efficiency of the gas-liquid separator 33 can be selected as appropriate according to the amount of liquid back, the amount of refrigerant circulation, the target performance value, the target cost, etc. allowed in the system.
- the heat source side unit 3 includes a plurality of connection pipes 10 and a plurality of check valves 20 in order to make the flow direction of the refrigerant flowing into the relay unit 4 constant regardless of the operation request of the load side unit group 5.
- the first connection pipe 11 connects the flow path switching unit 32 and the heat source side heat exchanger 34
- the first check valve 21 is connected to the first connection pipe 11. Is provided.
- the first check valve 21 regulates the flow direction of the refrigerant flowing through the first connection pipe 11 in a direction from the flow path switching device 32 toward the heat source side heat exchanger 34.
- One end of the second connection pipe 12 is connected to the outlet side of the heat source side heat exchanger 34, and a second check valve 22 is provided in the second connection pipe 12.
- the second check valve 22 regulates the flow direction of the refrigerant flowing through the second connection pipe 12 in a direction from the heat source side heat exchanger 34 toward each device.
- the second connection pipe 12 and the high-pressure pipe 72 are connected by a third connection pipe 13.
- the third connection pipe 13 includes a third check valve 23 and a fourth check valve 24. Is provided.
- the third check valve 23 and the fourth check valve 24 regulate the flow direction of the refrigerant flowing through the third connection pipe 13 in the direction from the second connection pipe 12 toward the high-pressure pipe 72. It is.
- the low pressure pipe 73 connecting the relay unit 4 and the flow path switching device 32 is provided with a fifth check valve 25, and the fifth check valve 25 distributes the refrigerant flowing through the low pressure pipe 73.
- the direction is restricted to a direction from the relay unit 4 toward the flow path switching unit 32.
- the gas-liquid separator 33 and the third connection pipe 13 are connected by a fourth connection pipe 14, and a sixth check valve 26 is provided in the fourth connection pipe 14.
- the sixth check valve 26 regulates the flow direction of the refrigerant flowing through the fourth connection pipe 14 in the direction from the gas-liquid separator 33 toward the third connection pipe 13.
- the third connection pipe 13 and the first connection pipe 11 are connected by a fifth connection pipe 15, and a seventh check valve 27 is provided in the fifth connection pipe 15. .
- the seventh check valve 27 regulates the flow direction of the refrigerant flowing through the fifth connection pipe 15 in a direction from the third connection pipe 13 toward the first connection pipe 11.
- the flow path switch 32 and the high-pressure pipe 72 are connected by a sixth connection pipe 16, and an eighth check valve 28 is provided in the sixth connection pipe 16.
- the eighth check valve 28 regulates the flow direction of the refrigerant flowing through the sixth connection pipe 16 in a direction from the flow path switching device 32 toward the high-pressure pipe 72.
- the second connection pipe 12 and the first connection pipe 11 are connected by a seventh connection pipe 17, and a ninth check valve 29 is provided in the seventh connection pipe 17. .
- the ninth check valve 29 regulates the flow direction of the refrigerant flowing through the seventh connection pipe 17 in a direction from the second connection pipe 12 toward the first connection pipe 11.
- the first connection pipe 11 is provided with a heat source side on / off valve 38, and the heat source side throttle section 39 is provided on the throttle pipe 11 a connected in parallel with the heat source side on / off valve 38. .
- the heat source side opening / closing valve 38 is opened, the refrigerant flows through the first connection pipe 11.
- the heat source side throttle unit 39 can adjust the opening degree, and adjusts the flow rate of the refrigerant flowing through the throttle pipe 11a according to the opening degree.
- the heat source side throttle unit 39 may be, for example, an electronic expansion valve.
- the bypass throttling part 37 is provided on the bypass pipe 71 and adjusts the flow rate of the refrigerant flowing through the bypass pipe 71 according to the opening degree.
- the bypass throttle 37 may be, for example, an electronic expansion valve.
- a discharge pressure detector 61 is provided on the discharge side of the compressor 31, and this discharge pressure detector 61 detects the discharge pressure of the refrigerant flowing through the discharge side of the compressor 31.
- a suction pressure detection unit 62 is provided on the suction side of the compressor 31, and the suction pressure detection unit 62 detects the suction pressure of the refrigerant flowing through the suction side of the compressor 31.
- the separation pipe 73 a is provided with an inflow pressure detection unit 63, and this inflow pressure detection unit 63 detects the inflow pressure of the refrigerant flowing into the gas-liquid separator 33.
- the relay unit 4 branches the refrigerant to a plurality of load side units in the load side unit group 5 and switches the flow direction of the refrigerant flowing from the high pressure pipe 72 or the low pressure pipe 73. Thereby, heating operation and cooling operation are performed independently in each of the plurality of load-side units.
- the relay unit 4 includes a sub-gas / liquid separator 41, a first inter-refrigerant heat exchanger 42, a first refrigerant constriction section 43, a second inter-refrigerant heat exchanger 44, a second refrigerant constriction section 45, and a refrigerant.
- the switchgear group 46 is provided.
- a sub bypass pipe 74 is connected to the gas pipe 78 connecting the relay unit 4 and the load side unit group 5 via the refrigerant switching device group 46, and the sub gas-liquid separator 41 is connected to the high pressure pipe 72.
- the auxiliary bypass pipe 74 is provided.
- the sub gas-liquid separator 41 and the liquid pipe 79 connecting the relay unit 4 and the load side unit group 5 are connected by a primary side pipe 75.
- the sub gas-liquid separator 41 separates the refrigerant flowing in from the low pressure pipe 73 into a gas refrigerant and a liquid refrigerant, flows out the gas refrigerant into the sub bypass pipe 74, and flows out the liquid refrigerant into the primary side pipe 75.
- the sub-gas / liquid separator 41 is not limited in its method or shape as long as the two-phase refrigerant can be separated into a gas phase and a liquid phase, and for example, a method such as gravity separation or centrifugal separation can be adopted. . Further, the separation efficiency of the sub-gas / liquid separator 41 can be appropriately selected according to the amount of liquid back allowed by the system, the circulation amount of the refrigerant, the target performance value, the target cost, or the like.
- a secondary side pipe 76 is further provided at a portion where the primary side pipe 75 and the liquid pipe 79 are connected.
- the secondary side pipe 76 is connected to the low pressure pipe 73.
- the first inter-refrigerant heat exchanger 42 is provided on the outlet side of the auxiliary gas-liquid separator 41 in the primary side pipe 75, and the liquid refrigerant that has flowed out of the auxiliary gas-liquid separator 41 in the primary side pipe 75, Heat exchange is performed with the refrigerant flowing through the secondary pipe 76.
- the first refrigerant throttling portion 43 is provided on the outlet side of the first inter-refrigerant heat exchanger 42 in the primary side pipe 75 and expands by reducing the pressure of the refrigerant flowing through the primary side pipe 75.
- the first refrigerant throttle portion 43 has a function such as a pressure reducing valve or an expansion valve.
- a precise flow control device such as an electronic expansion valve whose opening degree is variably controlled, or a capillary tube.
- An inexpensive flow rate control device such as
- the second inter-refrigerant heat exchanger 44 is provided on the outlet side of the first refrigerant constriction part 43 in the primary side pipe 75, and the refrigerant that has flowed out of the first refrigerant constriction part 43 in the primary side pipe 75; Heat exchange is performed with the refrigerant flowing through the secondary side pipe 76.
- the second refrigerant constricting section 45 is provided on the outlet side of the second inter-refrigerant heat exchanger 44 in the secondary side pipe 76 and expands by reducing the pressure of the refrigerant flowing through the secondary side pipe 76. is there.
- the second refrigerant throttle 45 has a function such as a pressure reducing valve or an expansion valve.
- a precise flow control device such as an electronic expansion valve whose opening degree is variably controlled, or a capillary tube.
- An inexpensive flow rate control device such as
- the refrigerant flowing through the primary pipe 75 and the secondary Heat exchange is performed with the refrigerant flowing through the side pipe 76, whereby the refrigerant flowing through the primary side pipe 75 is supercooled.
- circulates the primary side piping 75 is appropriately subcooled by optimizing the opening degree of the 2nd refrigerant
- the refrigerant switching device group 46 includes a plurality of refrigerant switching devices, and includes the same number of refrigerant switching devices as the number of load-side units. This refrigerant switching device group 46 controls the presence or absence of refrigerant circulation.
- the load-side unit group 5 includes a first load-side unit 5a and a second load-side unit 5b, and accordingly, the refrigerant switching device group 46 is a first refrigerant switching device. 47 and a second refrigerant switching device 48 are provided.
- the first refrigerant opening / closing device 47 includes an eleventh refrigerant opening / closing device 47a and a twelfth refrigerant opening / closing device 47b connected in parallel.
- the eleventh refrigerant switching device 47 a is connected to the sub gas-liquid separator 41 by the sub bypass piping 74
- the twelfth refrigerant switching device 47 b is the secondary side piping 76 and the low pressure piping 73.
- the eleventh refrigerant opening / closing device 47a and the twelfth refrigerant opening / closing device 47b are interlocked.
- the twelfth refrigerant opening / closing device 47b When the eleventh refrigerant opening / closing device 47a is opened, the twelfth refrigerant opening / closing device 47b is closed. At this time, the sub bypass pipe 74 and the gas pipe 78 are electrically connected, and the refrigerant flows between the sub gas-liquid separator 41 and the first load side unit 5a. On the other hand, when the eleventh refrigerant switching device 47a is closed, the twelfth refrigerant switching device 47b is opened. At this time, the secondary low-pressure pipe 77 and the gas pipe 78 are conducted, and the refrigerant flows between the heat source side unit 3 and the first load side unit 5a.
- the second refrigerant opening / closing device 48 includes a twenty-first refrigerant opening / closing device 48a and a twenty-second refrigerant opening / closing device 48b connected in parallel.
- the 21st refrigerant switching device 48a is connected to the sub gas-liquid separator 41 by the sub bypass piping 74
- the 22nd refrigerant switching device 48b is the secondary side piping 76 and the low pressure piping 73.
- the twenty-first refrigerant opening / closing device 48a and the twenty-second refrigerant opening / closing device 48b are interlocked.
- the twenty-second refrigerant opening / closing device 48b is closed. At this time, the sub bypass pipe 74 and the gas pipe 78 are conducted, and the refrigerant flows between the sub gas-liquid separator 41 and the second load side unit 5b. On the other hand, when the twenty-first refrigerant opening / closing device 48a is closed, the twenty-second refrigerant opening / closing device 48b is opened. At this time, the secondary low-pressure pipe 77 and the gas pipe 78 are electrically connected, and the refrigerant flows between the heat source side unit 3 and the second load side unit 5b.
- the load side unit group 5 is supplied with cold or warm heat from the heat source side unit 3 to process a cooling load or a heating load, and includes a plurality of load side heat exchangers 51, a plurality of expansion units 52, and a plurality of gases.
- a tube temperature detector 64 and a plurality of liquid tube temperature detectors 65 are provided.
- the load side unit group 5 includes the first load side unit 5a and the second load side unit 5b.
- the load-side heat exchanger 51 includes a first load-side heat exchanger 51a and a second load-side heat exchanger 51b
- the expansion unit 52 includes the first expansion unit 52a and the second expansion unit.
- the gas pipe temperature detector 64 includes a first gas pipe temperature detector 64a and a second gas pipe temperature detector 64b, and the liquid pipe temperature detector 65 detects the first liquid pipe temperature. Part 65a and a second liquid tube temperature detection part 65b.
- the some load side heat exchanger 51 acts as a condenser or an evaporator each independently.
- the first load side unit 5a has one end connected to the first gas pipe 78a and the other end connected to the first liquid pipe 79a.
- the first load side unit 5a includes a first load side heat exchanger 51a, a first expansion part 52a, a first gas pipe temperature detection part 64a, and a first liquid pipe temperature detection part 65a. .
- the first load-side heat exchanger 51a is connected to the first gas pipe 78a, and performs heat exchange between the heat medium, for example, ambient room air or water, and the refrigerant.
- the first load-side heat exchanger 51a functions as an evaporator in the heating operation to evaporate the refrigerant, and functions as a condenser (heat radiator) in the cooling operation to condense and liquefy the refrigerant.
- the first load-side heat exchanger 51a is an air-cooled heat exchanger, and the first load-side fan (not shown) is the first load-side heat exchanger. It is provided in the vicinity of the vessel 51a.
- the first load-side blower blows room air or the like to the first load-side heat exchanger 51a, and the evaporation capacity or condensation capacity in the first load-side heat exchanger 51a is adjusted by the number of rotations thereof. Is done.
- a water circulation pump is provided in the vicinity of the first load-side heat exchanger 51a, and depending on the rotation speed of the water circulation pump, The evaporation capacity or the condensation capacity in the first load-side heat exchanger 51a is adjusted.
- the first expansion part 52a is provided in the first liquid pipe 79a, and expands by reducing the pressure of the refrigerant flowing through the first liquid pipe 79a.
- the first expansion part 52a has a function such as a pressure reducing valve or an expansion valve.
- a precise flow control device such as an electronic expansion valve whose opening degree is variably controlled, or a capillary tube or the like. Such an inexpensive flow rate control device may be used.
- the first gas pipe temperature detection unit 64a is provided in the vicinity of the first load-side heat exchanger 51a in the first gas pipe 78a, and detects the temperature of the refrigerant flowing through the first gas pipe 78a. Is. When the eleventh refrigerant opening / closing device 47a is closed and the twelfth refrigerant opening / closing device 47b is opened, the refrigerant flows between the heat source side unit 3 and the first load side unit 5a. In this state, when the first load-side heat exchanger 51a acts as an evaporator, the refrigerant that has flowed out of the first load-side heat exchanger 51a flows into the gas-liquid separator 33. That is, in this case, the first gas pipe temperature detection unit 64a functions as a first inflow temperature detection unit that detects the inflow temperature of the refrigerant flowing into the gas-liquid separator 33.
- the first liquid pipe temperature detector 65a is provided in the vicinity of the first load-side heat exchanger 51a in the first liquid pipe 79a, and detects the temperature of the refrigerant flowing through the first liquid pipe 79a. Is.
- the second load side unit 5b has one end connected to the second gas pipe 78b and the other end connected to the second liquid pipe 79b.
- the second load side unit 5b includes a second load side heat exchanger 51b, a second expansion part 52b, a second gas pipe temperature detection part 64b, and a second liquid pipe temperature detection part 65b. .
- the second load-side heat exchanger 51b is connected to the second gas pipe 78b, and performs heat exchange between the heat medium, for example, surrounding indoor air or water, and the refrigerant.
- the second load side heat exchanger 51b functions as an evaporator in the heating operation to evaporate the refrigerant, and functions as a condenser (heat radiator) in the cooling operation to condense and liquefy the refrigerant.
- the second load-side heat exchanger 51b is an air-cooled heat exchanger
- the second load-side fan (not shown) is a second load-side heat exchanger. It is provided in the vicinity of the vessel 51b.
- the second load-side fan blows room air or the like to the second load-side heat exchanger 51b, and the evaporation capacity or the condensation capacity in the second load-side heat exchanger 51b is adjusted by the number of rotations thereof. Is done.
- a water circulation pump is provided in the vicinity of the second load-side heat exchanger 51b. Depending on the number of rotations of the water circulation pump, The evaporation capacity or the condensation capacity in the second load side heat exchanger 51b is adjusted.
- the second expansion part 52b is provided in the second liquid pipe 79b, and expands by reducing the pressure of the refrigerant flowing through the second liquid pipe 79b.
- the second expansion portion 52b has a function such as a pressure reducing valve or an expansion valve.
- a precise flow control device such as an electronic expansion valve whose opening degree is variably controlled, a capillary tube, or the like. Such an inexpensive flow rate control device may be used.
- the second gas pipe temperature detector 64b is provided in the vicinity of the second load-side heat exchanger 51b in the second gas pipe 78b, and detects the temperature of the refrigerant flowing through the second gas pipe 78b. Is.
- the twenty-first refrigerant opening / closing device 48a is closed and the twenty-second refrigerant opening / closing device 48b is opened, the refrigerant flows between the heat source side unit 3 and the second load side unit 5b.
- the second load-side heat exchanger 51b acts as an evaporator
- the refrigerant that has flowed out of the second load-side heat exchanger 51b flows into the gas-liquid separator 33. That is, in this case, the second gas pipe temperature detection unit 64b functions as a second inflow temperature detection unit that detects the inflow temperature of the refrigerant flowing into the gas-liquid separator 33.
- the second liquid pipe temperature detector 65b is provided in the vicinity of the second load-side heat exchanger 51b in the second liquid pipe 79b, and detects the temperature of the refrigerant flowing through the second liquid pipe 79b. Is.
- Control unit 80 The control unit 80 is provided, for example, in the heat source side unit 3 and controls the operation of the refrigerant circuit 2.
- the control unit 80 determines the drive frequency of the compressor 31, the heat source side blower based on the discharge pressure detected by the discharge pressure detection unit 61, the suction pressure detected by the suction pressure detection unit 62, and the like. The number of rotations of 35, switching of the flow path switch 32, and the like are controlled.
- the control unit 80 detects, for example, the first gas pipe temperature detected by the first gas pipe temperature detection unit 64a and the second gas pipe temperature detected by the second gas pipe temperature detection unit 64b.
- the control unit 80 may be provided in the relay unit 4, may be provided in the load side unit group 5, or may be provided outside the heat source side unit 3, the relay unit 4, and the load side unit group 5. May be. Further, the control unit 80 may be divided into a plurality of parts depending on the function and the like, and may be provided in each of the heat source side unit 3, the relay unit 4, and the load side unit group 5. In this case, the control units 80 are connected so that they can communicate with each other wirelessly or by wire.
- FIG. 2 is a block diagram showing the control unit 80 of the air-conditioning apparatus 1 according to Embodiment 1. As shown in FIG. 2, the control unit 80 includes a threshold determination unit 81, a heat source opening adjustment unit 82, a first determination unit 83, a second determination unit 84, and a bypass opening adjustment unit 85.
- the threshold determination means 81 determines whether or not the liquid tube temperature detected by the liquid tube temperature detection unit 65 is equal to or lower than a predetermined threshold liquid tube temperature.
- the threshold liquid tube temperature can be changed as appropriate.
- the heat source opening degree adjusting means 82 adjusts the opening degree of the heat source side restricting portion 39 so that the liquid pipe temperature exceeds the threshold liquid pipe temperature when the threshold value judging means 81 determines that the liquid pipe temperature is equal to or lower than the threshold liquid pipe temperature.
- the heat source side throttle unit 39 adjusts the flow rate of the refrigerant flowing through the throttle pipe 11a according to the opening thereof, and thereby, the pipe temperature in the load side unit group 5, for example, the load side unit group 5 is adjusted.
- the liquid pipe temperature in the vicinity of the load-side heat exchanger 51 provided in is adjusted.
- the heat source opening degree adjusting means 82 may adjust the opening degree of the heat source side throttle unit 39 without the threshold value determining means 81 determining the liquid pipe temperature.
- the first determination means 83 determines whether or not the bypass flow rate is different from a multiplication value obtained by multiplying the inflow flow rate by the inlet dryness.
- bypass flow the bypass flow rate of the refrigerant flowing through the bypass pipe 71
- the bypass flow rate is calculated by the first determination unit 83 based on the suction pressure detected by the suction pressure detection unit 62, the inflow pressure detected by the inflow pressure detection unit 63, and the opening degree of the heat source side throttle unit 39. Is.
- the inflow pressure is P1
- the suction pressure is P2
- the flow path resistance obtained from the opening degree of the heat source side throttle unit 39 is Cv
- the specific gravity G
- the density the bypass flow rate Grg is calculated from the following equation (1). .
- the inflow flow rate is calculated by the first determination unit 83 based on the performance of the compressor 31.
- the stroke volume of the compressor 31 is Vst
- the volume efficiency of the compressor 31 is ⁇ v
- the frequency of the compressor 31 is F
- the suction density of the compressor 31 is ⁇ s
- the inflow flow rate Gr is calculated from the following equation (2).
- the inlet dryness of the gas-liquid separator 33 will be described.
- the inlet dryness is determined by the first determination unit 83 based on the discharge pressure detected by the discharge pressure detection unit 61, the suction pressure detected by the suction pressure detection unit 62, and the inflow temperature detected by the inflow temperature detection unit. It is calculated.
- the load side heat exchanger outlet side enthalpy calculated from the discharge pressure and the inflow temperature is ho
- the saturated liquid enthalpy calculated from the suction pressure is hl
- the saturated gas enthalpy calculated from the suction pressure is hg
- the inlet dryness x is calculated from the following equation (3).
- the separation efficiency between the gas refrigerant and the liquid refrigerant in the gas-liquid separator 33 is optimal. That is, the first determination means 83 determines whether the bypass flow rate is different from a multiplication value obtained by multiplying the inflow rate by the inlet dryness, thereby separating the gas refrigerant from the liquid refrigerant in the gas-liquid separator 33. Determine if the efficiency is optimal.
- the second determination unit 84 determines whether or not the bypass flow rate is larger than the multiplication value. That is, if the first determination unit 83 determines that the separation efficiency between the gas refrigerant and the liquid refrigerant in the gas-liquid separator 33 is not optimal, the second determination unit 84 determines whether the bypass flow rate is greater than the multiplication value. Determine whether or not.
- the bypass opening adjustment means 85 is for lowering the opening of the bypass restrictor 37 when the second determination means 84 determines that the bypass flow rate is larger than the multiplication value.
- the bypass opening adjustment means 85 reduces the opening of the bypass restrictor 37 in the bypass pipe 71 and decreases the bypass flow rate flowing through the bypass pipe 71.
- bypass opening adjusting means 85 increases the opening of the bypass restrictor 37 when the second determining means 84 determines that the bypass flow rate is smaller than the multiplication value.
- the bypass opening adjusting means 85 increases the opening of the bypass restrictor 37 in the bypass pipe 71 and increases the bypass flow rate flowing through the bypass pipe 71.
- the air conditioner 1 receives an operation request from, for example, a remote controller installed indoors, and performs an air conditioning operation.
- the air conditioning operation mode in the air conditioning apparatus 1 includes a heating operation in which the heat source side heat exchanger 34 acts as an evaporator, and a cooling operation in which the heat source side heat exchanger 34 acts as a condenser.
- the heating operation includes a total heating operation in which all of the plurality of load-side heat exchangers 51 act as condensers, and a heating main operation in which at least one of the plurality of load-side heat exchangers 51 acts as an evaporator. I have.
- This heating main operation is an operation mode when the heating load is larger than the cooling load in the cooling / heating mixed operation.
- the cooling operation includes a cooling only operation in which all of the plurality of load-side heat exchangers 51 act as evaporators, and a cooling main operation in which at least one of the plurality of load-side heat exchangers 51 acts as a condenser.
- the cooling main operation is an operation mode in the case where the cooling load is larger than the heating load in the cooling / heating mixed operation.
- FIG. 3 is a circuit diagram showing a heating only operation in the first embodiment.
- both the first load side unit 5a and the second load side unit 5b perform the heating operation, that is, the first load side heat exchanger 51a and the second load side heat exchanger. Any of 51b acts as a condenser.
- the eleventh refrigerant switching device 47a is opened, and the twelfth refrigerant switching device 47b is closed.
- the twenty-first refrigerant opening / closing device 48a is also opened, and the twenty-second refrigerant opening / closing device 48b is also closed.
- the 1st load side unit 5a and the 2nd load side unit 5b are connected in parallel.
- the heat source side opening / closing valve 38 is opened, and the heat source side throttle unit 39 is closed.
- the compressor 31 sucks the refrigerant, compresses the refrigerant, and discharges the refrigerant in a high-temperature and high-pressure gas state.
- the discharged refrigerant passes through the flow path switching device 32 and then reaches the high-pressure pipe 72 through the sixth connection pipe 16.
- the refrigerant flows from the high-pressure pipe 72 into the sub-gas / liquid separator 41, the gas refrigerant flows out to the sub-bypass pipe 74, and the liquid refrigerant flows out to the primary side pipe 75.
- the gas refrigerant that has flowed out to the sub-bypass pipe 74 then branches and flows through the eleventh refrigerant switching device 47a and the twenty-first refrigerant switching device 48a, respectively.
- Each refrigerant flows into the first load side heat exchanger 51a and the second load side heat exchanger 51b through the first gas pipe 78a and the second gas pipe 78b, respectively.
- the first load-side heat exchanger 51a and the second load-side heat exchanger 51b are exchanged with each indoor air supplied from the first load-side fan and the second load-side fan, Condenses refrigerant. Thereby, each room air is warmed and each room is heated.
- the condensed refrigerant flows into the first refrigerant throttling part 43, and the first refrigerant throttling part 43 depressurizes the condensed refrigerant. Thereafter, the refrigerant flows into the second inter-refrigerant heat exchanger 44 and merges with the refrigerant that has passed through the first liquid pipe 79a and the second liquid pipe 79b. The refrigerant flows into the second inter-refrigerant heat exchanger 44, and the second inter-refrigerant heat exchanger 44 condenses the refrigerant flowing through the primary side pipe 75 by heat exchange with the refrigerant flowing through the secondary side pipe 76. .
- the condensed refrigerant flows into the second refrigerant throttle unit 45 through the secondary side pipe 76, and the second refrigerant throttle unit 45 depressurizes the condensed refrigerant.
- circulates the primary side piping 75 is supercooled.
- the refrigerant flowing through the secondary side pipe 76 flows into the gas-liquid separator 33 through the low pressure pipe 73 and further through the separation pipe 73a.
- the gas-liquid separator 33 separates the refrigerant flowing from the separation pipe 73 a into a gas refrigerant and a liquid refrigerant, the gas refrigerant flows out to the bypass pipe 71, and the liquid refrigerant flows out to the fourth connection pipe 14.
- the gas refrigerant that has flowed out to the bypass pipe 71 flows into the accumulator 36 and is then sucked into the compressor 31.
- the liquid refrigerant that has flowed out to the third connection pipe 13 then flows into the heat source side heat exchanger 34 through the fifth connection pipe 15.
- the heat source side heat exchanger 34 evaporates the refrigerant by exchanging heat with the outdoor air supplied from the heat source side blower 35.
- the evaporated refrigerant passes through the second connection pipe 12, and then passes through the seventh connection pipe 17 and reaches the flow path switching device 32. Then, the refrigerant flows into the accumulator 36 and is then sucked into the compressor 31.
- FIG. 4 is a circuit diagram showing a heating main operation in the first embodiment.
- the first load side unit 5a performs the heating operation
- the second load side unit 5b performs the cooling operation. That is, the first load side heat exchanger 51a acts as a condenser, and the second load side heat exchanger 51b acts as an evaporator.
- the eleventh refrigerant switching device 47a is opened, and the twelfth refrigerant switching device 47b is closed.
- the twenty-first refrigerant opening / closing device 48a is closed and the twenty-second refrigerant opening / closing device 48b is opened.
- the 1st load side unit 5a and the 2nd load side unit 5b are connected in series. Further, the heat source side opening / closing valve 38 is opened, and the heat source side throttle unit 39 is closed. In addition, the 1st load side unit 5a may perform a cooling operation, and the 2nd load side unit 5b may perform a heating operation.
- the compressor 31 sucks the refrigerant, compresses the refrigerant, and discharges it in the state of high-temperature and high-pressure gas.
- the discharged refrigerant passes through the flow path switching device 32 and then reaches the high-pressure pipe 72 through the sixth connection pipe 16.
- the refrigerant flows from the high-pressure pipe 72 into the sub-gas / liquid separator 41, the gas refrigerant flows out to the sub-bypass pipe 74, and the liquid refrigerant flows out to the primary side pipe 75.
- the gas refrigerant that has flowed out to the sub bypass pipe 74 flows through the eleventh refrigerant opening / closing device 47a.
- the refrigerant opening / closing device 48a since the twenty-first refrigerant opening / closing device 48a is closed, the refrigerant does not flow through the twenty-first refrigerant opening / closing device 48a. And a refrigerant
- coolant flows in into the 1st load side heat exchanger 51a through the 1st gas piping 78a.
- the first load-side heat exchanger 51a condenses the refrigerant by heat exchange with the indoor air supplied from the first load-side fan. Thereby, indoor air is warmed and the room is heated.
- the condensed refrigerant flows into the first expansion part 52a, and the first expansion part 52a depressurizes the condensed refrigerant.
- the decompressed refrigerant flows into the second inter-refrigerant heat exchanger 44 through the first liquid pipe 79a.
- a part of the refrigerant flows into the second liquid pipe 79b.
- the refrigerant that has flowed into the second liquid pipe 79b flows into the second expansion portion 52b, and the second expansion portion 52b decompresses the refrigerant.
- the decompressed refrigerant flows into the second load-side heat exchanger 51b, and the second load-side heat exchanger 51b exchanges heat with room air supplied from the second load-side fan. Evaporate the refrigerant. Thereby, indoor air is cooled and the room is cooled.
- the evaporated refrigerant passes through the second gas pipe 78b, flows through the twenty-second refrigerant switching device 48b, and reaches the low-pressure pipe 73.
- the refrigerant circulating in the primary side pipe 75 is condensed by heat exchange with the circulating refrigerant.
- the condensed refrigerant flows into the first refrigerant throttling part 43, and the first refrigerant throttling part 43 depressurizes the condensed refrigerant.
- the refrigerant flows into the second inter-refrigerant heat exchanger 44 and merges with the refrigerant that has passed through the first liquid pipe 79a.
- the refrigerant flows into the second inter-refrigerant heat exchanger 44, and the second inter-refrigerant heat exchanger 44 condenses the refrigerant flowing through the primary side pipe 75 by heat exchange with the refrigerant flowing through the secondary side pipe 76. .
- the condensed refrigerant flows into the second refrigerant throttle unit 45 through the secondary side pipe 76, and the second refrigerant throttle unit 45 depressurizes the condensed refrigerant. Thereby, the refrigerant
- the refrigerant flowing through the secondary side pipe 76 merges with the refrigerant passed through the second gas pipe 78b and reaches the low pressure pipe 73. Thereafter, the refrigerant flows into the gas-liquid separator 33 through the separation pipe 73a.
- the gas-liquid separator 33 separates the refrigerant flowing from the separation pipe 73 a into a gas refrigerant and a liquid refrigerant, the gas refrigerant flows out to the bypass pipe 71, and the liquid refrigerant flows out to the fourth connection pipe 14.
- the gas refrigerant that has flowed out to the bypass pipe 71 flows into the accumulator 36 and is then sucked into the compressor 31.
- the liquid refrigerant that has flowed out to the third connection pipe 13 then flows into the heat source side heat exchanger 34 through the fifth connection pipe 15.
- the heat source side heat exchanger 34 evaporates the refrigerant by exchanging heat with the outdoor air supplied from the heat source side blower 35.
- the evaporated refrigerant passes through the second connection pipe 12, and then passes through the seventh connection pipe 17 and reaches the flow path switching device 32. Then, the refrigerant flows into the accumulator 36 and is then sucked into the compressor 31.
- FIG. 5 is a circuit diagram showing a cooling only operation in the first embodiment.
- both the first load side unit 5a and the second load side unit 5b perform the cooling operation, that is, the first load side heat exchanger 51a and the second load side heat exchanger. Any of 51b acts as an evaporator.
- the eleventh refrigerant switching device 47a is closed and the twelfth refrigerant switching device 47b is opened.
- the twenty-first refrigerant opening / closing device 48a is also closed, and the twenty-second refrigerant opening / closing device 48b is also opened.
- the 1st load side unit 5a and the 2nd load side unit 5b are connected in parallel.
- the heat source side opening / closing valve 38 is opened, and the heat source side throttle unit 39 is closed.
- the compressor 31 sucks the refrigerant, compresses the refrigerant, and discharges it in the state of high-temperature and high-pressure gas.
- the discharged refrigerant passes through the flow path switching device 32 and then flows into the heat source side heat exchanger 34 through the first connection pipe 11.
- the heat source side heat exchanger 34 condenses the refrigerant by exchanging heat with outdoor air supplied from the heat source side blower 35.
- the condensed refrigerant flows in the order of the second connection pipe 12 and the third connection pipe 13 and reaches the high-pressure pipe 72.
- the refrigerant flows into the sub gas-liquid separator 41 from the high pressure pipe 72.
- the eleventh refrigerant opening / closing device 47a and the twenty-first refrigerant opening / closing device 48a are closed, the refrigerant does not flow through the sub bypass pipe 74 but flows through only the primary side pipe 75.
- the refrigerant that has flowed out to the primary side pipe 75 flows into the first inter-refrigerant heat exchanger 42, and the first inter-refrigerant heat exchanger 42 performs primary exchange by heat exchange with the refrigerant that flows through the secondary side pipe 76.
- the refrigerant flowing through the side pipe 75 is condensed.
- the condensed refrigerant flows into the first refrigerant throttling part 43, and the first refrigerant throttling part 43 depressurizes the condensed refrigerant.
- the refrigerant flowing into the second inter-refrigerant heat exchanger 44 is condensed by heat exchange with the refrigerant flowing through the secondary side pipe 76.
- circulates the primary side piping 75 is supercooled.
- the refrigerant condensed in the second inter-refrigerant heat exchanger 44 branches and flows to the first liquid pipe 79a, the second liquid pipe 79b, and the secondary side pipe 76, respectively.
- the respective refrigerants flowing into the first liquid pipe 79a and the second liquid pipe 79b flow into the first expansion section 52a and the second expansion section 52b, respectively, and the first expansion section 52a and the second expansion section. 52b depressurizes the refrigerant.
- the decompressed refrigerant flows into the first load-side heat exchanger 51a and the second load-side heat exchanger 51b, respectively, and the first load-side heat exchanger 51a and the second load-side heat exchanger are
- the refrigerant is evaporated by heat exchange with the indoor air supplied from the first load-side fan and the second load-side fan, respectively. Thereby, each room air is cooled and each room is cooled.
- These evaporated refrigerants flow through the first gas pipe 78a and the second gas pipe 78b, respectively, through the twelfth refrigerant switching device 47b and the twenty-second refrigerant switching device 48b, and then merge.
- the low pressure pipe 73 is reached.
- the refrigerant flowing from the second inter-refrigerant heat exchanger 44 to the secondary side pipe 76 flows into the second refrigerant throttle unit 45, and the second refrigerant throttle unit 45 depressurizes the condensed refrigerant. . Then, the decompressed refrigerant flows through the secondary side pipe 76, merges with the refrigerant that has passed through the first gas pipe 78 a and the second gas pipe 78 b, and reaches the low pressure pipe 73. Then, the refrigerant flowing through the low pressure pipe 73 passes through the flow path switching device 32, flows into the accumulator 36, and is then sucked into the compressor 31.
- FIG. 6 is a circuit diagram showing a cooling main operation in the first embodiment.
- the first load side unit 5a performs the cooling operation
- the second load side unit 5b performs the heating operation. That is, the first load side heat exchanger 51a functions as an evaporator, and the second load side heat exchanger 51b functions as a condenser.
- the eleventh refrigerant switching device 47a is closed and the twelfth refrigerant switching device 47b is opened.
- the twenty-first refrigerant opening / closing device 48a is opened and the twenty-second refrigerant opening / closing device 48b is closed.
- the 1st load side unit 5a and the 2nd load side unit 5b are connected in series. Further, the heat source side opening / closing valve 38 is opened, and the heat source side throttle unit 39 is closed. In addition, the 1st load side unit 5a may perform heating operation, and the 2nd load side unit 5b may perform air_conditionaing
- the compressor 31 sucks the refrigerant, compresses the refrigerant, and discharges the refrigerant in a high-temperature and high-pressure gas state.
- the discharged refrigerant passes through the flow path switching device 32 and then flows into the heat source side heat exchanger 34 through the first connection pipe 11.
- the heat source side heat exchanger 34 condenses the refrigerant by exchanging heat with outdoor air supplied from the heat source side blower 35.
- the condensed refrigerant flows in the order of the second connection pipe 12 and the third connection pipe 13 and reaches the high-pressure pipe 72.
- the refrigerant flows from the high-pressure pipe 72 into the sub-gas / liquid separator 41, the gas refrigerant flows out to the sub-bypass pipe 74, and the liquid refrigerant flows out to the primary side pipe 75.
- the eleventh refrigerant opening / closing device 47a is closed to the sub bypass pipe 74, the gas refrigerant does not flow through the eleventh refrigerant opening / closing device 47a.
- the twenty-first refrigerant switching device 48a is open, the gas refrigerant flows through the twenty-first refrigerant switching device 48a.
- the refrigerant that has flowed out to the primary side pipe 75 flows into the first inter-refrigerant heat exchanger 42, and the first inter-refrigerant heat exchanger 42 performs primary exchange by heat exchange with the refrigerant that flows through the secondary side pipe 76.
- the refrigerant flowing through the side pipe 75 is condensed.
- the condensed refrigerant flows into the first refrigerant throttling part 43, and the first refrigerant throttling part 43 depressurizes the condensed refrigerant.
- the refrigerant flowing into the second inter-refrigerant heat exchanger 44 is condensed by heat exchange with the refrigerant flowing through the secondary side pipe 76.
- circulates the primary side piping 75 is supercooled.
- the refrigerant that has flowed into the first liquid pipe 79a flows into the first expansion section 52a, and the first expansion section 52a depressurizes the refrigerant. Then, the decompressed refrigerant flows into the first load-side heat exchanger 51a, and the first load-side heat exchanger 51a exchanges heat with room air supplied from the first load-side fan. Evaporate the refrigerant. Thereby, indoor air is cooled and the room is cooled.
- the evaporated refrigerant passes through the first gas pipe 78a, flows through the twelfth refrigerant switching device 47b, and reaches the low-pressure pipe 73.
- the refrigerant flowing through the sub bypass pipe 74 flows through the twenty-first refrigerant opening / closing device 48a, flows into the second load side heat exchanger 51b through the second gas pipe 78b.
- the second load-side heat exchanger 51b condenses the refrigerant by heat exchange with room air supplied from the second load-side fan. Thereby, indoor air is warmed and the room is heated.
- the condensed refrigerant flows into the second expansion part 52b, and the second expansion part 52b decompresses the condensed refrigerant. Then, the decompressed refrigerant flows into the second inter-refrigerant heat exchanger 44 through the second liquid pipe 79b.
- the refrigerant flowing from the second inter-refrigerant heat exchanger 44 to the secondary side pipe 76 merges with the refrigerant that has passed through the second liquid pipe 79b. Then, the refrigerant flows into the second refrigerant throttle unit 45, and the second refrigerant throttle unit 45 depressurizes the condensed refrigerant. Then, the decompressed refrigerant flows through the secondary side pipe 76, merges with the refrigerant that has passed through the first gas pipe 78 a, and reaches the low pressure pipe 73. Then, the refrigerant flowing through the low pressure pipe 73 passes through the flow path switching device 32, flows into the accumulator 36, and is then sucked into the compressor 31.
- FIG. 7 is a flowchart showing the operation of the air-conditioning apparatus 1 according to Embodiment 1.
- the air conditioner 1 capable of performing the cooling and heating mixed operation may be subjected to a control referred to as the bi-evaporation temperature control during the heating main operation with a large heating load ratio.
- the inlet of the heat source side heat exchanger 34 of the heat source side unit 3 acting as an evaporator under the condition that the liquid pipe temperature of the load side unit in which the cooling operation is performed is equal to or lower than a predetermined temperature.
- the heat source side on / off valve 38 installed on the side is closed, and the heat source side on / off valve 38 is installed in parallel with the heat source side on / off valve 38 so as to keep the evaporation temperature of the load side unit in the cooling operation within a predetermined range. 39 is used to control the opening degree.
- the dual evaporation temperature control will be described.
- operation is performed is demonstrated.
- the first load side unit 5a performs the heating operation
- the second load side unit 5b performs the cooling operation. That is, the first load side heat exchanger 51a acts as a condenser, and the second load side heat exchanger 51b acts as an evaporator.
- the bi-evaporation temperature control is started, first, the second liquid pipe temperature of the refrigerant flowing into the second load side heat exchanger 51b acting as an evaporator is changed to the second liquid temperature. It is detected by the tube temperature detector 65b (step S1).
- the threshold value determination unit 81 determines whether or not the second liquid tube temperature detected by the second liquid tube temperature detection unit 65b is equal to or lower than a predetermined threshold liquid tube temperature (step S2). .
- the process returns to step S1.
- the threshold value determination unit 81 determines that the second liquid tube temperature detected by the second liquid tube temperature detector 65b is equal to or lower than the threshold liquid tube temperature (Yes in step S2)
- the heat source opening degree The opening degree of the heat source side throttle unit 39 is adjusted by the adjusting means 82 so that the liquid pipe temperature exceeds the threshold liquid pipe temperature (step S3). Thereafter, the control ends.
- the opening degree of the heat source side throttle unit 39 when the opening degree of the heat source side throttle unit 39 is adjusted, the flow rate of the refrigerant flowing into the heat source side heat exchanger 34 changes. For this reason, there is a possibility that pressure loss downstream of the heat source side heat exchanger 34 and the heat source side heat exchanger 34 may be reduced.
- the opening degree of the heat source side restricting portion 39 when the opening degree of the heat source side restricting portion 39 is adjusted, the refrigerant separation ratio in the gas-liquid separator 33 may be lost in the refrigerant flowing from the second load side unit 5b to the gas-liquid separator 33. .
- the control unit 80 adjusts the opening degree of the bypass throttling unit 37 based on the bypass flow rate, the inflow rate, and the inlet dryness.
- FIG. 8 is a flowchart showing the operation of the air-conditioning apparatus 1 according to Embodiment 1.
- the discharge pressure detecting unit 61 detects the discharge pressure of the refrigerant flowing through the discharge side of the compressor 31 (step S11).
- the suction pressure detection unit 62 detects the suction pressure of the refrigerant flowing through the suction side of the compressor 31 (step S12).
- the 2nd load side heat exchanger 51b acts as an evaporator, the refrigerant which flowed out from the 2nd load side heat exchanger 51b flows into gas-liquid separator 33.
- the second gas pipe temperature detection unit 64b functions as a second inflow temperature detection unit that detects the inflow temperature of the refrigerant flowing into the gas-liquid separator 33.
- the inflow temperature of the refrigerant flowing into the gas-liquid separator 33 is detected by the second gas pipe temperature detection unit 64b (Step S13).
- the inflow pressure of the refrigerant flowing into the gas-liquid separator 33 is detected by the inflow pressure detection unit 63 (step S14).
- the second determination is made.
- the means 84 determines whether or not the bypass flow rate Grg is larger than the multiplication value Gr ⁇ x (Grg> Gr ⁇ x) (step S16).
- the bypass opening adjustment means 85 causes the bypass throttling unit to The opening degree of 37 is lowered (step S17).
- the bypass opening degree adjusting means 85 causes the bypass flow rate to be bypassed.
- the opening degree of the throttle unit 37 is increased (step S18). Thereafter, the control ends.
- the control unit 80 adjusts the opening degree of the bypass throttle unit 37 based on the bypass flow rate, the inflow rate, and the inlet dryness, so that the operation efficiency of the air conditioner is improved. improves. Further, by adjusting the opening degree of the bypass throttle portion 37, the gas refrigerant is prevented from flowing through the heat source side heat exchanger 34. For this reason, the air conditioner 1 can improve the pressure loss downstream of the heat source side heat exchanger 34 and the heat source side heat exchanger 34, and the heat exchange efficiency in the heat source side heat exchanger 34 may be reduced. Deterred.
- control unit 80 adjusts the opening degree of the bypass throttle unit 37 based on the bypass flow rate, the inflow rate, and the inlet dryness, so that the separation ratio between the gas refrigerant and the liquid refrigerant in the gas-liquid separator 33 is appropriate. It becomes. For this reason, even if the refrigerant separation ratio in the gas-liquid separator 33 is about to collapse when the bi-evaporation temperature control is being performed, the separation ratio can be properly maintained. Furthermore, in order to avoid the liquid back phenomenon, it is not necessary to close the on-off valve provided in the bypass pipe 71 and prevent the refrigerant from flowing into the bypass pipe 71, so the gas-liquid separator 33 is used. The energy saving effect obtained by the above can be obtained.
- the air conditioner 1 including one heat source unit 3, one relay unit 4, and two load units is illustrated, but the heat source unit 3, the relay unit 4, and the load
- the number of side units may be plural or one.
- an example in which the present invention is applied to an air conditioner has been shown.
- the present invention can also be applied to other systems that constitute a refrigerant circuit using a refrigeration cycle such as a refrigeration system. .
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Abstract
Description
図1は、実施の形態1に係る空気調和装置1を示す回路図である。この図1に基づいて、空気調和装置1について説明する。空気調和装置1は、例えばビル又はマンション等に設置され、冷媒が循環する冷凍サイクルであるヒートポンプサイクルを利用したものであり、冷暖混在運転が可能なものである。この空気調和装置1は、図1に示すように、熱源側ユニット3と複数の負荷側ユニットを備える負荷側ユニット群5とが中継ユニット4を介して配管により接続された冷媒回路2及び制御部80を備えている。
冷媒回路2に流通する冷媒としては、例えば二酸化炭素、炭化水素又はヘリウム等の自然冷媒、HFC410A、HFC407C又はHFC404A等の塩素を含まないフロン代替冷媒、既存の製品に使用されているR22、R134a等のフロン系冷媒等が挙げられるが、冷媒は、適宜選択することができる。
熱源側ユニット3は、負荷側ユニット群5に冷熱又は温熱を供給するものである。この熱源側ユニット3は、冷媒を圧縮する圧縮機31、冷媒の流通方向を切り替える流路切換器32、熱媒体と冷媒との熱交換を行う熱源側熱交換器34、液冷媒を貯留するアキュムレータ36、及びガス冷媒と液冷媒とを分離する気液分離器33を備えている。
圧縮機31は、低温低圧のガス冷媒を吸入し、そのガス冷媒を圧縮して高温高圧のガス冷媒とし、冷媒回路2に吐出するものである。その後、冷媒は、冷媒回路2を循環して、空気調和装置1において空気調和運転が行われる。この圧縮機31は、吸入した冷媒を圧縮して高圧にするものであり、例えば容量を制御することができるインバータタイプの圧縮機等で構成することができる。なお、圧縮機31は、このような容量制御が可能なインバータタイプの圧縮機に限定されず、例えば、一定速タイプの圧縮機としてもよく、インバータタイプと一定速タイプとを組み合わせた圧縮機としてもよい。また、レシプロ、ロータリ、スクロール又はスクリュー等の各タイプを利用して圧縮機を構成してもよい。
流路切換器32は、圧縮機31の吐出側に設けられており、暖房運転と冷房運転とにおいて、冷媒の流通方向を切り替えるものである。この流路切換器32は、暖房運転においては、熱源側熱交換器34が蒸発器として作用し、冷房運転においては、熱源側熱交換器34が凝縮器として作用するように、冷媒の流通方向を切り替える。流路切換器32は、例えば四方弁とすることができる。
熱源側熱交換器34は、第1の接続配管11によって流路切換器32に接続されており、熱媒体、例えば周囲の室外空気又は水等と冷媒との間で熱交換を行うものである。この熱源側熱交換器34は、暖房運転においては蒸発器として作用して冷媒を蒸発ガス化し、冷房運転においては凝縮器(放熱器)として作用して冷媒を凝縮液化する。なお、本実施の形態1においては、熱源側熱交換器34は、空冷式の熱交換器であり、熱源側送風機35が、熱源側熱交換器34の近傍に設けられている。熱源側送風機35は、熱源側熱交換器34に室外空気等を送風するものであり、その回転数によって、熱源側熱交換器34における蒸発能力又は凝縮能力が調整される。なお、熱源側熱交換器34が水冷式の熱交換器である場合は、水循環ポンプが、熱源側熱交換器34の近傍に設けられ、この水循環ポンプの回転数によって、熱源側熱交換器34における蒸発能力又は凝縮能力が調整される。
アキュムレータ36は、圧縮機31の吸入側に設けられ、余剰冷媒を貯留する機能及び液冷媒とガス冷媒とを分離する機能を備えている。アキュムレータ36によって、液冷媒のみが貯留され、ガス冷媒は、アキュムレータ36を通過して、圧縮機31に吸入される。
気液分離器33は、熱源側熱交換器34と、熱源側ユニット3と中継ユニット4とを接続する低圧配管73から分岐する分離配管73aとの間に設けられており、また、気液分離器33とアキュムレータ36とは、バイパス配管71によって接続されている。なお、アキュムレータ36が設けられない場合は、気液分離器33と圧縮機31の吸入側とが、直接、バイパス配管71によって接続される。そして、気液分離器33は、高圧配管72から流入する冷媒を、液冷媒とガス冷媒とに分離して、液冷媒を熱源側熱交換器34に流出し、ガス冷媒をバイパス配管71に流出するものである。このように、気液分離器33は、ガス冷媒が熱源側熱交換器34に流出することを阻止することによって、熱源側熱交換器34における熱交換性が低下することを抑止するものである。
熱源側ユニット3は、負荷側ユニット群5の運転要求に関わらず、中継ユニット4に流入する冷媒の流通方向を一定にするため、複数の接続配管10及び複数の逆止弁20を備えている。第1の接続配管11は、前述の如く、流路切換器32と熱源側熱交換器34とを接続するものであり、この第1の接続配管11には、第1の逆止弁21が設けられている。この第1の逆止弁21は、第1の接続配管11に流通する冷媒の流通方向を、流路切換器32から熱源側熱交換器34に向かう方向に規制するものである。
第1の接続配管11には、熱源側開閉弁38が設けられており、更に、この熱源側開閉弁38と並列に接続された絞り配管11aには、熱源側絞り部39が設けられている。熱源側開閉弁38が開くと、冷媒が第1の接続配管11を流通し、熱源側開閉弁38が閉じると、冷媒が第1の接続配管11を流通しない。また、熱源側絞り部39は、開度を調整することができ、その開度によって、絞り配管11aを流通する冷媒の流量を調整するものである。これにより、負荷側ユニット群5における配管温度、例えば負荷側ユニット群5に設けられた負荷側熱交換器51の蒸発温度等を調整することができる。なお、熱源側絞り部39は、例えば、電子式膨張弁としてもよい。
バイパス絞り部37は、バイパス配管71上に設けられており、その開度によって、バイパス配管71を流通する冷媒の流量を調整するものである。バイパス絞り部37は、例えば、電子式膨張弁としてもよい。
圧縮機31の吐出側には、吐出圧力検出部61が設けられており、この吐出圧力検出部61は、圧縮機31の吐出側を流通する冷媒の吐出圧力を検出するものである。また、圧縮機31の吸入側には、吸入圧力検出部62が設けられており、この吸入圧力検出部62は、圧縮機31の吸入側を流通する冷媒の吸入圧力を検出するものである。
分離配管73aには、流入圧力検出部63が設けられており、この流入圧力検出部63は、気液分離器33に流入する冷媒の流入圧力を検出するものである。
中継ユニット4は、負荷側ユニット群5における複数の負荷側ユニットに、冷媒を分岐するものであると共に、高圧配管72又は低圧配管73から流入した冷媒の流通方向を切り替えるものである。これにより、複数の負荷側ユニットにおいて、夫々独立に暖房運転及び冷房運転が行われる。この中継ユニット4は、副気液分離器41、第1の冷媒間熱交換器42、第1の冷媒絞り部43、第2の冷媒間熱交換器44、第2の冷媒絞り部45、冷媒開閉装置群46を備えている。
中継ユニット4と負荷側ユニット群5とを接続するガス配管78には、冷媒開閉装置群46を介して、副バイパス配管74が接続されており、副気液分離器41は、高圧配管72と、副バイパス配管74との間に設けられている。また、副気液分離器41と、中継ユニット4と負荷側ユニット群5とを接続する液配管79とは、一次側配管75によって接続されている。副気液分離器41は、低圧配管73から流入する冷媒を、ガス冷媒と液冷媒とに分離して、ガス冷媒を副バイパス配管74に流出し、また、液冷媒を一次側配管75に流出するものである。なお、副気液分離器41は、二相冷媒を気相と液相とに分離することができれば、方式又は形状を限定せず、例えば重力分離又は遠心分離等の方式を採用することができる。更に、副気液分離器41の分離効率は、システムにて許容される液バック量、冷媒の循環量、目標性能値又は目標コスト等に応じて適宜選択することができる。
一次側配管75と液配管79とが接続される部分には、更に、二次側配管76が設けられており、この二次側配管76は、低圧配管73に接続されている。第1の冷媒間熱交換器42は、一次側配管75における副気液分離器41の出口側に設けられており、一次側配管75における副気液分離器41から流出した液冷媒と、二次側配管76を流通する冷媒との間で熱交換を行うものである。
第1の冷媒絞り部43は、一次側配管75における第1の冷媒間熱交換器42の出口側に設けられており、一次側配管75を流通する冷媒を減圧して膨張するものである。このように、第1の冷媒絞り部43は、減圧弁又は膨張弁等の機能を備えており、例えば、開度が可変に制御される電子式膨張弁といった緻密な流量制御装置、又は、毛細管等といった安価な流量制御装置としてもよい。
第2の冷媒間熱交換器44は、一次側配管75における第1の冷媒絞り部43の出口側に設けられており、一次側配管75における第1の冷媒絞り部43から流出した冷媒と、二次側配管76を流通する冷媒との間で熱交換を行うものである。
第2の冷媒絞り部45は、二次側配管76における第2の冷媒間熱交換器44の出口側に設けられており、二次側配管76を流通する冷媒を減圧して膨張するものである。このように、第2の冷媒絞り部45は、減圧弁又は膨張弁等の機能を備えており、例えば、開度が可変に制御される電子式膨張弁といった緻密な流量制御装置、又は、毛細管等といった安価な流量制御装置としてもよい。
冷媒開閉装置群46は、複数の冷媒開閉装置からなり、負荷側ユニットの数と同数の冷媒開閉装置を備える。この冷媒開閉装置群46は、冷媒の流通の有無を制御するものである。本実施の形態1では、負荷側ユニット群5は、第1の負荷側ユニット5a及び第2の負荷側ユニット5bを備えており、それに伴い、冷媒開閉装置群46は、第1の冷媒開閉装置47及び第2の冷媒開閉装置48を備えている。
第1の冷媒開閉装置47は、並列に接続された第11の冷媒開閉装置47aと第12の冷媒開閉装置47bとを備えている。このうち、第11の冷媒開閉装置47aは、副バイパス配管74によって、副気液分離器41に接続されており、また、第12の冷媒開閉装置47bは、二次側配管76と低圧配管73とが接続される部分に更に設けられた二次低圧配管77に接続されている。これらの第11の冷媒開閉装置47a及び第12の冷媒開閉装置47bは、連動しており、第11の冷媒開閉装置47aが開くと、第12の冷媒開閉装置47bが閉じる。このとき、副バイパス配管74とガス配管78とが導通され、冷媒は、副気液分離器41と第1の負荷側ユニット5aとの間を流通する。一方、第11の冷媒開閉装置47aが閉じると、第12の冷媒開閉装置47bが開く。このとき、二次低圧配管77とガス配管78とが導通され、冷媒は、熱源側ユニット3と第1の負荷側ユニット5aとの間を流通する。
第2の冷媒開閉装置48は、並列に接続された第21の冷媒開閉装置48aと第22の冷媒開閉装置48bとを備えている。このうち、第21の冷媒開閉装置48aは、副バイパス配管74によって、副気液分離器41に接続されており、また、第22の冷媒開閉装置48bは、二次側配管76と低圧配管73とが接続される部分に更に設けられた二次低圧配管77に接続されている。これらの第21の冷媒開閉装置48a及び第22の冷媒開閉装置48bは、連動しており、第21の冷媒開閉装置48aが開くと、第22の冷媒開閉装置48bが閉じる。このとき、副バイパス配管74とガス配管78とが導通され、冷媒は、副気液分離器41と第2の負荷側ユニット5bとの間を流通する。一方、第21の冷媒開閉装置48aが閉じると、第22の冷媒開閉装置48bが開く。このとき、二次低圧配管77とガス配管78とが導通され、冷媒は、熱源側ユニット3と第2の負荷側ユニット5bとの間を流通する。
負荷側ユニット群5は、熱源側ユニット3から冷熱又は温熱が供給されて、冷房負荷又は暖房負荷を処理するものであり、複数の負荷側熱交換器51、複数の膨張部52、複数のガス管温度検出部64及び複数の液管温度検出部65を備えている。前述の如く、負荷側ユニット群5は、第1の負荷側ユニット5a及び第2の負荷側ユニット5bを備えている。これに伴い、負荷側熱交換器51は、第1の負荷側熱交換器51a及び第2の負荷側熱交換器51bを備え、膨張部52は、第1の膨張部52a及び第2の膨張部52bを備え、ガス管温度検出部64は、第1のガス管温度検出部64a及び第2のガス管温度検出部64bを備え、液管温度検出部65は、第1の液管温度検出部65a及び第2の液管温度検出部65bを備えている。なお、複数の負荷側熱交換器51は、夫々独立して凝縮器又は蒸発器として作用するものである。
第1の負荷側ユニット5aは、一端が第1のガス配管78aに接続され、他端が第1の液配管79aに接続されている。この第1の負荷側ユニット5aは、第1の負荷側熱交換器51a、第1の膨張部52a、第1のガス管温度検出部64a及び第1の液管温度検出部65aを備えている。
第1の負荷側熱交換器51aは、第1のガス配管78aに接続されており、熱媒体、例えば周囲の室内空気又は水等と冷媒との間で熱交換を行うものである。この第1の負荷側熱交換器51aは、暖房運転においては蒸発器として作用して冷媒を蒸発ガス化し、冷房運転においては凝縮器(放熱器)として作用して冷媒を凝縮液化する。なお、本実施の形態1においては、第1の負荷側熱交換器51aは、空冷式の熱交換器であり、第1の負荷側送風機(図示せず)が、第1の負荷側熱交換器51aの近傍に設けられている。第1の負荷側送風機は、第1の負荷側熱交換器51aに室内空気等を送風するものであり、その回転数によって、第1の負荷側熱交換器51aにおける蒸発能力又は凝縮能力が調整される。なお、第1の負荷側熱交換器51aが水冷式の熱交換器である場合は、水循環ポンプが、第1の負荷側熱交換器51aの近傍に設けられ、この水循環ポンプの回転数によって、第1の負荷側熱交換器51aにおける蒸発能力又は凝縮能力が調整される。
第1の膨張部52aは、第1の液配管79aに設けられており、第1の液配管79aを流通する冷媒を減圧して膨張するものである。このように、第1の膨張部52aは、減圧弁又は膨張弁等の機能を備えており、例えば、開度が可変に制御される電子式膨張弁といった緻密な流量制御装置、又は、毛細管等といった安価な流量制御装置としてもよい。
第1のガス管温度検出部64aは、第1のガス配管78aにおいて第1の負荷側熱交換器51aの近傍に設けられており、第1のガス配管78aに流通する冷媒の温度を検出するものである。なお、第11の冷媒開閉装置47aが閉じ、第12の冷媒開閉装置47bが開くと、冷媒は、熱源側ユニット3と第1の負荷側ユニット5aとの間を流通する。この状態で、第1の負荷側熱交換器51aが蒸発器として作用する場合、第1の負荷側熱交換器51aから流出した冷媒は、気液分離器33に流入する。即ち、この場合、第1のガス管温度検出部64aは、気液分離器33に流入する冷媒の流入温度を検出する第1の流入温度検出部として作用する。
第1の液管温度検出部65aは、第1の液配管79aにおいて第1の負荷側熱交換器51aの近傍に設けられており、第1の液配管79aに流通する冷媒の温度を検出するものである。
第2の負荷側ユニット5bは、一端が第2のガス配管78bに接続され、他端が第2の液配管79bに接続されている。この第2の負荷側ユニット5bは、第2の負荷側熱交換器51b、第2の膨張部52b、第2のガス管温度検出部64b及び第2の液管温度検出部65bを備えている。
第2の負荷側熱交換器51bは、第2のガス配管78bに接続されており、熱媒体、例えば周囲の室内空気又は水等と冷媒との間で熱交換を行うものである。この第2の負荷側熱交換器51bは、暖房運転においては蒸発器として作用して冷媒を蒸発ガス化し、冷房運転においては凝縮器(放熱器)として作用して冷媒を凝縮液化する。なお、本実施の形態1においては、第2の負荷側熱交換器51bは、空冷式の熱交換器であり、第2の負荷側送風機(図示せず)が、第2の負荷側熱交換器51bの近傍に設けられている。第2の負荷側送風機は、第2の負荷側熱交換器51bに室内空気等を送風するものであり、その回転数によって、第2の負荷側熱交換器51bにおける蒸発能力又は凝縮能力が調整される。なお、第2の負荷側熱交換器51bが水冷式の熱交換器である場合は、水循環ポンプが、第2の負荷側熱交換器51bの近傍に設けられ、この水循環ポンプの回転数によって、第2の負荷側熱交換器51bにおける蒸発能力又は凝縮能力が調整される。
第2の膨張部52bは、第2の液配管79bに設けられており、第2の液配管79bを流通する冷媒を減圧して膨張するものである。このように、第2の膨張部52bは、減圧弁又は膨張弁等の機能を備えており、例えば、開度が可変に制御される電子式膨張弁といった緻密な流量制御装置、又は、毛細管等といった安価な流量制御装置としてもよい。
第2のガス管温度検出部64bは、第2のガス配管78bにおいて第2の負荷側熱交換器51bの近傍に設けられており、第2のガス配管78bに流通する冷媒の温度を検出するものである。なお、第21の冷媒開閉装置48aが閉じ、第22の冷媒開閉装置48bが開くと、冷媒は、熱源側ユニット3と第2の負荷側ユニット5bとの間を流通する。この状態で、第2の負荷側熱交換器51bが蒸発器として作用する場合、第2の負荷側熱交換器51bから流出した冷媒は、気液分離器33に流入する。即ち、この場合、第2のガス管温度検出部64bは、気液分離器33に流入する冷媒の流入温度を検出する第2の流入温度検出部として作用する。
第2の液管温度検出部65bは、第2の液配管79bにおいて第2の負荷側熱交換器51bの近傍に設けられており、第2の液配管79bに流通する冷媒の温度を検出するものである。
制御部80は、例えば熱源側ユニット3に設けられており、冷媒回路2の動作を制御するものである。制御部80は、熱源側ユニット3において、例えば吐出圧力検出部61において検出された吐出圧力、吸入圧力検出部62において検出された吸入圧力等に基づいて、圧縮機31の駆動周波数、熱源側送風機35の回転数、流路切換器32の切り替え等を制御する。
閾値判定手段81は、液管温度検出部65において検出された液管温度が予め決められた閾値液管温度以下であるか否かを判定するものである。なお、閾値液管温度は、適宜変更することができる。
熱源開度調整手段82は、閾値判定手段81において液管温度が閾値液管温度以下と判定された場合、液管温度が閾値液管温度を上回るように熱源側絞り部39の開度を調整するものである。前述の如く、熱源側絞り部39は、その開度によって、絞り配管11aを流通する冷媒の流量を調整するものであり、これにより、負荷側ユニット群5における配管温度、例えば負荷側ユニット群5に設けられた負荷側熱交換器51近傍の液管温度が調整される。なお、熱源開度調整手段82は、閾値判定手段81が液管温度を判定せずに、熱源側絞り部39の開度を調整してもよい。
第1の判定手段83は、バイパス流量が、流入流量に入口乾き度を乗算した乗算値と異なるか否かを判定するものである。
ここで、バイパス配管71を流通する冷媒のバイパス流量について説明する。バイパス流量は、吸入圧力検出部62において検出された吸入圧力、流入圧力検出部63において検出された流入圧力、及び熱源側絞り部39の開度に基づいて、第1の判定手段83によって算出されるものである。流入圧力をP1、吸入圧力をP2、熱源側絞り部39の開度から求まる流路抵抗をCv、比重をG、密度をρとすると、バイパス流量Grgは、下記式(1)から算出される。
Grg=17・Cv・ρ・[(P1+P2)・(P2-P1)]1/2/G1/2・・(1)
次に、気液分離器33に流入する冷媒の流入流量について説明する。流入流量は、圧縮機31の性能に基づいて、第1の判定手段83によって算出されるものである。圧縮機31のストロークボリュームをVst、圧縮機31の体積効率をηv、圧縮機31の周波数をF、圧縮機31の吸入密度をρsとすると、流入流量Grは、下記式(2)から算出される。
Gr=3600・Vst・ηv・F・ρs・・・(2)
気液分離器33の入口乾き度について説明する。入口乾き度は、吐出圧力検出部61において検出された吐出圧力、吸入圧力検出部62において検出された吸入圧力及び流入温度検出部において検出された流入温度に基づいて、第1の判定手段83によって算出されるものである。吐出圧力と流入温度とから算出される負荷側熱交換器出口側エンタルピをho、吸入圧力から算出される飽和液エンタルピをhl、吸入圧力から算出される飽和ガスエンタルピをhgとすると、入口乾き度xは、下記式(3)から算出される。
x=(ho-hl)/(hg-hl)・・・(3)
第2の判定手段84は、第1の判定手段83においてバイパス流量が乗算値と異なることが判定された場合、バイパス流量が乗算値よりも大きいか否かを判定するものである。即ち、第2の判定手段84は、第1の判定手段83において気液分離器33におけるガス冷媒と液冷媒との分離効率が最適でないと判定された場合、バイパス流量が乗算値よりも大きいか否かを判定する。
バイパス開度調整手段85は、第2の判定手段84においてバイパス流量が乗算値よりも大きいと判定された場合、バイパス絞り部37の開度を下げるものである。バイパス流量が乗算値よりも大きい(Grg>Gr・x)とき、バイパス配管71に液冷媒が流通する液バック現象が発生している。このため、バイパス開度調整手段85は、バイパス配管71におけるバイパス絞り部37の開度を下げて、バイパス配管71に流通するバイパス流量を下げる。
先ず、全暖房運転について説明する。図3は、実施の形態1における全暖房運転を示す回路図である。全暖房運転においては、第1の負荷側ユニット5a及び第2の負荷側ユニット5bのいずれもが暖房運転を行い、即ち、第1の負荷側熱交換器51a及び第2の負荷側熱交換器51bのいずれもが凝縮器として作用する。このとき、第11の冷媒開閉装置47aは開き、第12の冷媒開閉装置47bは閉じる。また、第21の冷媒開閉装置48aも開き、第22の冷媒開閉装置48bも閉じる。これにより、第1の負荷側ユニット5aと第2の負荷側ユニット5bとが、並列に接続される。更に、熱源側開閉弁38は開き、熱源側絞り部39は閉じる。
次に、暖房主運転について説明する。図4は、実施の形態1における暖房主運転を示す回路図である。暖房主運転においては、例えば第1の負荷側ユニット5aが暖房運転を行い、第2の負荷側ユニット5bが冷房運転を行う。即ち、第1の負荷側熱交換器51aは凝縮器として作用し、第2の負荷側熱交換器51bは蒸発器として作用する。このとき、第11の冷媒開閉装置47aは開き、第12の冷媒開閉装置47bは閉じる。また、第21の冷媒開閉装置48aは閉じ、第22の冷媒開閉装置48bは開く。これにより、第1の負荷側ユニット5aと第2の負荷側ユニット5bとが、直列に接続される。更に、熱源側開閉弁38は開き、熱源側絞り部39は閉じる。なお、第1の負荷側ユニット5aが冷房運転を行い、第2の負荷側ユニット5bが暖房運転を行ってもよい。
次に、全冷房運転について説明する。図5は、実施の形態1における全冷房運転を示す回路図である。全冷房運転においては、第1の負荷側ユニット5a及び第2の負荷側ユニット5bのいずれもが冷房運転を行い、即ち、第1の負荷側熱交換器51a及び第2の負荷側熱交換器51bのいずれもが蒸発器として作用する。このとき、第11の冷媒開閉装置47aは閉じ、第12の冷媒開閉装置47bは開く。また、第21の冷媒開閉装置48aも閉じ、第22の冷媒開閉装置48bも開く。これにより、第1の負荷側ユニット5aと第2の負荷側ユニット5bとが、並列に接続される。更に、熱源側開閉弁38は開き、熱源側絞り部39は閉じる。
次に、冷房主運転について説明する。図6は、実施の形態1における冷房主運転を示す回路図である。冷房主運転においては、例えば第1の負荷側ユニット5aが冷房運転を行い、第2の負荷側ユニット5bが暖房運転を行う。即ち、第1の負荷側熱交換器51aは蒸発器として作用し、第2の負荷側熱交換器51bは凝縮器として作用する。このとき、第11の冷媒開閉装置47aは閉じ、第12の冷媒開閉装置47bは開く。また、第21の冷媒開閉装置48aは開き、第22の冷媒開閉装置48bは閉じる。これにより、第1の負荷側ユニット5aと第2の負荷側ユニット5bとが、直列に接続される。更に、熱源側開閉弁38は開き、熱源側絞り部39は閉じる。なお、第1の負荷側ユニット5aが暖房運転を行い、第2の負荷側ユニット5bが冷房運転を行ってもよい。
Claims (7)
- 冷媒が流通し、圧縮機、負荷側熱交換器、膨張部及び熱源側熱交換器が配管により接続された空気調和装置において、
冷媒を分離する気液分離器と、
前記気液分離器と前記圧縮機の吸入側とを接続するバイパス配管と、
前記バイパス配管に設けられ冷媒の流量を調整するバイパス絞り部と、
前記熱源側熱交換器に流入する冷媒の流量を調整する熱源側絞り部と、
前記熱源側絞り部の開度に基づいて算出される前記バイパス配管を流通する冷媒のバイパス流量、前記気液分離器に流入する冷媒の流入流量、及び前記気液分離器の入口乾き度に基づいて、前記バイパス絞り部の開度を調整する制御部と、
を備える空気調和装置。 - 前記制御部は、
前記気液分離器に流入するガス冷媒が、前記バイパス配管に流入するガス冷媒と一致するか否かを判定し、その判定結果に基づいて、前記バイパス絞り部の開度を調整するものである
請求項1記載の空気調和装置。 - 前記制御部は、
前記バイパス流量が、前記流入流量に前記入口乾き度を乗算した乗算値と異なるか否かを判定する第1の判定手段と、
前記第1の判定手段において前記バイパス流量が前記乗算値と異なることが判定された場合、前記バイパス流量が前記乗算値よりも大きいか否かを判定する第2の判定手段と、
前記第2の判定手段において、前記バイパス流量が前記乗算値よりも大きいと判定された場合、前記バイパス絞り部の開度を下げ、前記バイパス流量が前記乗算値よりも小さいと判定された場合、前記バイパス絞り部の開度を上げるバイパス開度調整手段と、
を備える請求項1又は2記載の空気調和装置。 - 前記圧縮機の吐出側を流通する冷媒の吐出圧力を検出する吐出圧力検出部と、
前記圧縮機の吸入側を流通する冷媒の吸入圧力を検出する吸入圧力検出部と、
前記気液分離器に流入する冷媒の流入温度を検出する流入温度検出部と、を更に備え、
前記制御部は、
前記吐出圧力検出部において検出された吐出圧力、前記吸入圧力検出部において検出された吸入圧力及び前記流入温度検出部において検出された流入温度に基づいて、前記入口乾き度を算出するものである
請求項1~3のいずれか1項に記載の空気調和装置。 - 前記圧縮機の吸入側を流通する冷媒の吸入圧力を検出する吸入圧力検出部と、
前記気液分離器に流入する冷媒の流入圧力を検出する流入圧力検出部と、を更に備え、
前記制御部は、
前記吸入圧力検出部において検出された吸入圧力及び前記流入圧力検出部において検出された流入圧力に基づいて、前記バイパス流量を算出するものである
請求項1~4のいずれか1項に記載の空気調和装置。 - 前記負荷側熱交換器及び前記膨張部は、夫々複数設けられており、
複数の前記負荷側熱交換器は、夫々独立して凝縮器又は蒸発器として作用するものであり、
空気調和における運転モードは、
前記熱源側熱交換器が蒸発器として作用する暖房運転と、
前記熱源側熱交換器が凝縮器として作用する冷房運転と、を備え、
前記暖房運転は、
複数の前記負荷側熱交換器のいずれもが凝縮器として作用する全暖房運転と、
複数の前記負荷側熱交換器の少なくとも一つが蒸発器として作用する暖房主運転と、を備え、
前記冷房運転は、
複数の前記負荷側熱交換器のいずれもが蒸発器として作用する全冷房運転と、
複数の前記負荷側熱交換器の少なくとも一つが凝縮器として作用する冷房主運転と、
を備える請求項1~5のいずれか1項に記載の空気調和装置。 - 前記熱源側熱交換器に流入する冷媒の流量を調整する熱源側絞り部と、
複数の前記負荷側熱交換器のうち蒸発器として作用する負荷側熱交換器に流入する冷媒の液管温度を検出する液管温度検出部と、を更に備え、
前記制御部は、
前記液管温度検出部において検出された液管温度が予め決められた閾値液管温度以下であるか否かを判定する閾値判定手段と、
前記閾値判定手段において液管温度が前記閾値液管温度以下と判定された場合、液管温度が前記閾値液管温度を上回るように前記熱源側絞り部の開度を調整する熱源開度調整手段と、
を備える請求項6記載の空気調和装置。
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PCT/JP2014/067618 WO2016002021A1 (ja) | 2014-07-02 | 2014-07-02 | 空気調和装置 |
EP14896491.9A EP3165844B1 (en) | 2014-07-02 | 2014-07-02 | Air conditioning device |
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CN111397104A (zh) * | 2020-03-24 | 2020-07-10 | 珠海格力电器股份有限公司 | 空调系统的控制方法、装置、控制设备、介质和空调系统 |
CN114704940A (zh) * | 2022-03-28 | 2022-07-05 | 珠海格力电器股份有限公司 | 换热器的调节方法、调节装置、换热器以及空调 |
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US20230358446A1 (en) * | 2020-11-13 | 2023-11-09 | Mitsubishi Electric Corporation | Refrigeration cycle device |
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EP3165844B1 (en) | 2021-09-22 |
JPWO2016002021A1 (ja) | 2017-04-27 |
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