WO2011125111A1 - 空調給湯複合システム - Google Patents
空調給湯複合システム Download PDFInfo
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- WO2011125111A1 WO2011125111A1 PCT/JP2010/002480 JP2010002480W WO2011125111A1 WO 2011125111 A1 WO2011125111 A1 WO 2011125111A1 JP 2010002480 W JP2010002480 W JP 2010002480W WO 2011125111 A1 WO2011125111 A1 WO 2011125111A1
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- WIPO (PCT)
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- water supply
- hot water
- pressure
- heat exchanger
- refrigerant
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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
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D17/00—Domestic hot-water supply systems
- F24D17/02—Domestic hot-water supply systems using heat pumps
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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
- F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
- F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
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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
- F25B2313/021—Indoor unit or outdoor unit with auxiliary heat exchanger not forming part of the indoor or outdoor unit
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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
- F25B2313/02334—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements during heating
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/047—Water-cooled condensers
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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
- F25B2600/00—Control issues
- F25B2600/19—Refrigerant outlet condenser 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
- F25B2600/00—Control issues
- F25B2600/21—Refrigerant outlet evaporator 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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion valves
Definitions
- the present invention relates to an air conditioning and hot water supply combined system capable of simultaneously executing an air conditioning operation (cooling operation and heating operation) and a hot water supply operation, and more particularly to an air conditioning and hot water supply combined system capable of realizing a highly efficient operation state.
- a plurality of usage units are connected to the heat source unit via connection piping (refrigerant piping), so that each usage unit can perform cooling operation or heating operation.
- the hot water supply unit can execute the hot water supply operation by connecting the hot water supply unit to the heat source side unit through a connection pipe or a cascade system. That is, the air conditioning operation of the use side unit and the hot water supply operation of the hot water supply unit can be executed simultaneously.
- the cooling operation is performed by the utilization unit
- the hot water supply operation is executed by the hot water supply unit, so that exhaust heat can be recovered in the cooling operation, thereby realizing a highly efficient operation. be able to.
- Japanese Patent No. 2554208 page 3, FIG. 1 etc.
- Japanese Patent Publication No. 6-76864 pages 2-4, FIG. 2 etc.
- JP 2009-243793 A 5th page, FIG. 1 etc.
- the combined air conditioning and hot water supply system described in Patent Document 3 is a technology for hot water supply operation under conditions where the outside air temperature is low (low outside air conditions), and by controlling the injection flow rate to the compressor according to the condensation temperature, Hot water supply operation under low outside air conditions is possible.
- the air-conditioning and hot water supply combined system described in Patent Document 3 there is no description of hot water supply operation for high outside air conditions.
- the present invention has been made to solve the above-described problems. By appropriately controlling the degree of superheat and the degree of supercooling of the heat exchanger, it is possible to maintain a high hot water supply capacity even in a high outdoor air condition.
- An object of the present invention is to provide a combined air-conditioning and hot-water supply system capable of maintaining a highly efficient operation state.
- the combined air conditioning and hot water supply system includes at least one use unit on which a use side heat exchanger is mounted, and one or more hot water supply units on which at least a hot water supply side heat exchanger is mounted, A compressor, a heat source side heat exchanger, a heat source side decompression mechanism, a bypass circuit that bypasses the high pressure liquid refrigerant to the low pressure side, and a low pressure bypass decompression provided in the bypass circuit, connected to the use unit and the hot water supply unit A mechanism, an accumulator, one or a plurality of heat source units equipped with a supercooling heat exchanger for exchanging heat between the high-pressure side liquid refrigerant and the low-pressure side refrigerant flowing in the bypass circuit; The use side that is connected to the hot water supply unit and the heat source unit and controls the flow of the refrigerant that flows into the use unit according to the operating state of the use unit.
- a pressure mechanism and one or a plurality of branch units on which a hot water supply pressure reducing mechanism for controlling a flow of refrigerant flowing into the hot water supply unit according to an operating state of the hot water supply unit is mounted.
- the degree of superheat of the refrigerant on the low pressure gas side of the supercooling heat exchanger is determined by the opening of the low pressure bypass pressure reducing mechanism.
- the degree of supercooling of the refrigerant on the high-pressure liquid side of the supercooling heat exchanger is controlled so that the evaporating pressure or the evaporating temperature calculated from the evaporating pressure is not more than the first predetermined value.
- the combined air conditioning and hot water supply system includes at least one use unit on which a use side heat exchanger is mounted, and one or more hot water supply units on which at least a hot water supply side heat exchanger is mounted,
- a usage-side decompression mechanism that is connected to the heat source unit and controls the flow of the refrigerant that flows into the usage unit according to the operating state of the usage unit, and that flows into the hot water supply unit according to the operating status of the hot water supply unit
- high hot water supply capability can be maintained even in high outside air conditions, and a highly efficient operation state can be maintained.
- FIG. 1 is a refrigerant circuit diagram showing a refrigerant circuit configuration of an air conditioning and hot water supply complex system 100 according to Embodiment 1 of the present invention.
- FIG. 2 is a schematic diagram schematically illustrating the processing of various sensor information and the target of the control device of the air conditioning and hot water supply complex system 100.
- FIG. 3 is a table showing the operation contents of the four-way valve 11 and each electromagnetic valve with respect to the operation mode of the heat source unit 301.
- FIG. 1 is a refrigerant circuit diagram showing a refrigerant circuit configuration of an air conditioning and hot water supply complex system 100 according to Embodiment 1 of the present invention.
- FIG. 2 is a schematic diagram schematically illustrating the processing of various sensor information and the target of the control device of the air conditioning and hot water supply complex system 100.
- FIG. 3 is a table showing the operation contents of the four-way valve 11 and each electromagnetic valve with respect to the operation mode of the heat source unit 301.
- FIG. 4 is a schematic explanatory diagram for explaining the control for avoiding the low-pressure side pressure increase, the high-pressure side pressure increase, and the discharge temperature increase under the high outside air condition executed by the air conditioning and hot water supply combined system 100.
- FIG. 5 is a schematic diagram for explaining a change in evaporation temperature with respect to the degree of superheat or a change in condensation temperature and operating efficiency with respect to the degree of supercooling. The configuration and operation of the air conditioning and hot water supply complex system 100 will be described with reference to FIGS. In addition, in the following drawings including FIG. 1, the relationship of the size of each component may be different from the actual one.
- This combined air-conditioning and hot-water supply system 100 can perform a cooling operation or a heating operation selected in the use side unit and a hot-water supply operation in the hot water supply unit simultaneously by performing a vapor compression refrigeration cycle operation. It is a multi-system air conditioning and hot water supply complex system. This combined air-conditioning and hot-water supply system 100 can perform an air-conditioning operation and a hot-water supply operation at the same time, and can maintain a high hot-water temperature even under a high outside air temperature condition, thereby realizing a highly efficient operation.
- the combined air conditioning and hot water supply system 100 includes a heat source unit 301, a branch unit 302, and a usage unit 303.
- the heat source unit 301 and the branch unit 302 are connected by a liquid extension pipe 9 that is a refrigerant pipe and a gas extension pipe 12 that is a refrigerant pipe.
- One of the hot water supply units 304 is connected to the heat source unit 301 via a hot water supply gas pipe 4 that is a refrigerant pipe and a hot water supply extension pipe 3 that is a refrigerant pipe, and the other is a refrigerant pipe that is connected to a branch unit 302 via a hot water supply liquid pipe 7. It is connected to the.
- the use unit 303 and the branch unit 302 are connected by an indoor gas pipe 13 that is a refrigerant pipe and an indoor liquid pipe 16 that is a refrigerant pipe.
- the refrigerant used in the air conditioning and hot water supply combined system 100 includes, for example, an HFC (hydrofluorocarbon) refrigerant such as R410A, R407C, and R404A, an HCFC (hydrochlorofluorocarbon) refrigerant such as R22 and R134a, or a hydrocarbon, helium, and carbon dioxide.
- HFC hydrofluorocarbon
- HCFC hydrochlorofluorocarbon refrigerant
- the operation modes that can be executed by the air conditioning and hot water supply complex system 100 will be briefly described.
- the operation mode of the heat source unit 301 is determined by the ratio of the hot water supply load of the connected hot water supply unit 304 and the cooling load and heating load of the use unit 303.
- the combined air conditioning and hot water supply system 100 is configured to execute four operation modes (a full warm operation mode, a warm main operation mode, a full cool operation mode, and a cool main operation mode).
- the all-warm operation mode is an operation mode of the heat source unit 301 when simultaneous operation of hot water supply operation by the hot water supply unit 304 and heating operation by the use unit 303 is executed.
- the warm main operation mode is an operation mode of the heat source unit 301 when the hot water supply load is large in the simultaneous operation of the hot water supply operation by the hot water supply unit 304 and the cooling operation by the use unit 303.
- the cooling main operation mode is an operation mode of the heat source unit 301 when the cooling load is large in the simultaneous operation of the hot water supply operation by the hot water supply unit 304 and the cooling operation by the use unit 303.
- the all-cooling operation mode is an operation mode of the heat source unit 301 when there is no hot water supply load and the use unit 303 performs the cooling operation.
- the use unit 303 is installed in a place where conditioned air can be blown out to the air-conditioning target area (for example, by embedding in an indoor ceiling, hanging, or hanging on a wall surface).
- the utilization unit 303 is connected to the heat source unit 301 via the branch unit 302, the liquid extension pipe 9 and the gas extension pipe 12, and constitutes a part of the refrigerant circuit in the air conditioning and hot water supply complex system 100.
- the utilization unit 303 includes an indoor refrigerant circuit that forms part of the refrigerant circuit.
- This indoor refrigerant circuit has an indoor heat exchanger 14 as a use side heat exchanger as an element device.
- the use unit 303 is provided with an indoor blower 15 for supplying conditioned air after heat exchange with the refrigerant of the indoor heat exchanger 14 to an air-conditioning target area such as a room.
- the indoor heat exchanger 14 can be composed of, for example, a cross fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins. Moreover, you may comprise the indoor heat exchanger 14 with a microchannel heat exchanger, a shell and tube type heat exchanger, a heat pipe type heat exchanger, or a double pipe type heat exchanger.
- the indoor heat exchanger 14 functions as a refrigerant evaporator and discharges air in the air conditioning target area.
- the refrigerant functions as a refrigerant condenser (or radiator) to heat the air in the air-conditioning target area.
- the indoor blower 15 has a function of sucking room air into the use unit 303, exchanging heat with the indoor heat exchanger 14, and then supplying the room air as conditioned air to the air-conditioning target area. That is, in the utilization unit 303, it is possible to exchange heat between indoor air taken in by the indoor blower 15 and refrigerant flowing through the indoor heat exchanger 14.
- the indoor blower 15 is configured to be capable of changing the flow rate of the conditioned air supplied to the indoor heat exchanger 14, and for example, a fan such as a centrifugal fan or a multiblade fan, and a DC fan that drives the fan, for example. It has a motor consisting of a motor.
- the use unit 303 is provided with various sensors shown below. That is, the utilization unit 303 is provided on the gas side of the indoor heat exchanger 14 and is provided on the liquid side of the indoor heat exchanger 14 to detect the temperature of the gas refrigerant. An indoor liquid temperature sensor 208 to be detected and an indoor suction temperature sensor 209 that is provided on the indoor air inlet side of the usage unit 303 and detects the temperature of the indoor air flowing into the usage unit 303 are provided.
- control part 103 which functions as a normal operation control means which performs normal operation including the air_conditionaing
- the hot water supply unit 304 has a function of supplying boiling water to a hot water supply tank (not shown) installed outdoors, for example.
- One of the hot water supply units 304 is connected to the heat source unit 301 via the hot water supply gas pipe 4 and the hot water supply extension pipe 3, and the other is connected to the branch unit 302 via the hot water supply liquid pipe 7. Constitutes a part of the refrigerant circuit.
- the hot water supply unit 304 includes a hot water supply side refrigerant circuit that constitutes a part of the refrigerant circuit.
- This hot water supply side refrigerant circuit has the hot water supply side heat exchanger 5 as an element device.
- the hot water supply unit 304 is provided with a water supply pump 6 for supplying hot water after heat exchange with the refrigerant of the hot water supply side heat exchanger 5 to a hot water supply tank or the like.
- the hot water supply side heat exchanger 5 can be constituted by, for example, a plate heat exchanger.
- the hot water supply side heat exchanger 5 functions as a refrigerant condenser in the hot water supply operation mode executed by the hot water supply unit 304 and heats water supplied by the water supply pump 6.
- the water supply pump 6 has a function of supplying water in the hot water supply tank into the hot water supply unit 304 and exchanging heat with the hot water supply side heat exchanger 5 and then supplying the water as hot water into the hot water supply tank. That is, the hot water supply unit 304 can exchange heat between the water supplied by the water supply pump 6 and the refrigerant flowing through the hot water supply side heat exchanger 5. Further, the water supply pump 6 is configured with a variable flow rate of water supplied to the hot water supply side heat exchanger 5.
- the hot water supply unit 304 is provided with various sensors shown below. That is, the hot water supply unit 304 is provided on the gas side of the hot water supply side heat exchanger 5 and is provided on the liquid side of the hot water supply side heat exchanger 5 to detect the temperature of the gas refrigerant.
- a hot water supply liquid temperature sensor 204 for detecting the temperature is provided on the water inlet side of the hot water supply unit 304, and a water inlet temperature sensor 205 for detecting the temperature of the water flowing into the unit is provided on the water outlet side of the hot water supply unit 304.
- a water outlet temperature sensor 206 for detecting the temperature of water flowing out of the unit.
- operation of the water supply pump 6 is controlled by the control part 103 which performs normal operation including the hot water supply operation mode of the hot water supply unit 304 (refer FIG. 2).
- the heat source unit 301 is installed outdoors, for example, and is connected to the utilization unit 303 via the liquid extension pipe 9, the gas extension pipe 12 and the branch unit 302, and connects the hot water supply extension pipe 3, the hot water supply gas pipe 4 and the branch unit 302. And is connected to the hot water supply unit 304, and constitutes a part of the refrigerant circuit in the combined air and water supply system 100.
- the heat source unit 301 includes an outdoor refrigerant circuit that constitutes a part of the refrigerant circuit.
- the outdoor refrigerant circuit includes a compressor 1 that compresses the refrigerant, a four-way valve 11 that switches a direction in which the refrigerant flows, an outdoor heat exchanger 20 that serves as a heat source-side heat exchanger, and a refrigerant flow according to an operation mode. It has three solenoid valves (first solenoid valve 2, second solenoid valve 10, and third solenoid valve 27) for controlling the flow direction, and an accumulator 22 for storing surplus refrigerant as element devices. .
- the heat source unit 301 includes an outdoor fan 21 for supplying air to the outdoor heat exchanger 20, a supercooling heat exchanger 18 for controlling the flow rate of the refrigerant, and an outdoor unit for controlling the distribution flow rate of the refrigerant.
- a pressure reducing mechanism (heat source side pressure reducing mechanism) 19 a low pressure bypass pressure reducing mechanism 23, and a suction pressure reducing mechanism 25 are provided.
- the low-pressure bypass pressure reducing mechanism 23 is provided in a bypass circuit (low-pressure bypass pipe 24) that connects between the branch unit 302 and the supercooling heat exchanger 18 to the inlet of the accumulator 22 via the supercooling heat exchanger 18. Yes.
- the suction pressure reducing mechanism 25 is a second bypass circuit (suction) that connects between the supercooling heat exchanger 18 (or the receiver 28 in the case of Embodiment 2) and the outdoor pressure reducing mechanism 19 to the suction portion of the compressor 1. It is provided in the bypass pipe 26).
- the compressor 1 sucks refrigerant and compresses the refrigerant to a high temperature and high pressure state.
- the compressor 1 mounted on the air conditioning and hot water supply complex system 100 is capable of varying the operating capacity, and is composed of a positive displacement compressor driven by a motor (not shown) controlled by an inverter, for example. .
- a case where there is only one compressor 1 is shown as an example.
- the present invention is not limited to this, and two or more compressors 1 are used according to the number of connected usage units 303. May be provided in parallel.
- the discharge side pipe connected to the compressor 1 is branched in the middle, and one is connected to the gas extension pipe 12 via the four-way valve 11 and the other is connected to the hot water supply extension pipe 3.
- the four-way valve 11 has a function as a flow path switching device that switches the flow direction of the refrigerant according to the operation mode of the heat source unit 301.
- FIG. 3 the operation
- Solid line” and “broken line” displayed in FIG. 3 mean “solid line” and “broken line” indicating the switching state of the four-way valve 11 shown in FIG.
- the four-way valve 11 is switched to become a “solid line” in the case of the full warm operation mode or the warm main operation mode. That is, in the case of the full warm operation mode or the warm main operation mode, the four-way valve 11 causes the gas on the discharge side of the compressor 1 and the indoor heat exchanger 14 to function the outdoor heat exchanger 20 as a refrigerant evaporator. And the suction side of the compressor 1 and the gas side of the outdoor heat exchanger 20 are switched. Further, the four-way valve 11 is switched so as to be a “broken line” in the case of the all-cooling operation mode or the cold main operation mode.
- the four-way valve 11 causes the gas on the discharge side of the compressor 1 and the outdoor heat exchanger 20 to function the outdoor heat exchanger 20 as a refrigerant condenser. And the suction side of the compressor 1 and the gas side of the indoor heat exchanger 14 are switched.
- FIG. 3 also shows the operation contents for the operation mode of the solenoid valve.
- the first solenoid valve 2 is provided on the discharge side on the hot water supply extension pipe 3 side of the compressor 1, and has a function of controlling the flow of refrigerant according to the operation mode of the hot water supply unit 304. Is open, and closed when no hot water supply operation is performed.
- the second solenoid valve 10 is provided on the discharge side of the compressor 1 on the four-way valve 11 side, and has a function of controlling the flow of the refrigerant according to the operation mode of the heat source unit 301. It is open in the case of the mode or the cold main operation mode, and is closed in the case of the warm main operation mode.
- the third solenoid valve 27 is provided in a pipe connecting the inlet side of the accumulator 22 and the gas extension pipe 12, and has a function of controlling the flow of the refrigerant according to the operation mode of the heat source unit 301. It is open in the main operation mode and closed in the full warm operation mode, the cold main operation mode, or the full cooling operation mode.
- the outdoor heat exchanger 20 can be composed of, for example, a cross fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins. Moreover, you may comprise the outdoor heat exchanger 20 with a microchannel heat exchanger, a shell and tube type heat exchanger, a heat pipe type heat exchanger, or a double pipe type heat exchanger.
- the outdoor heat exchanger 20 functions as a refrigerant evaporator and cools the refrigerant when the operation mode executed by the air conditioning and hot water supply combined system 100 is the heating operation mode, and functions as a refrigerant condenser (or radiator) in the cooling operation mode. Thus, the refrigerant is heated.
- the outdoor heat exchanger 20 has a gas side connected to the four-way valve 11 and a liquid side connected to the outdoor pressure reducing mechanism 19.
- the outdoor blower 21 has a function of sucking outdoor air into the heat source unit 301, exchanging heat with the outdoor heat exchanger 20, and then discharging the outdoor air to the outside. That is, in the heat source unit 301, heat exchange can be performed between the outdoor air taken in by the outdoor blower 21 and the refrigerant flowing through the outdoor heat exchanger 20.
- the outdoor blower 21 is configured to be capable of changing the flow rate of outdoor air supplied to the outdoor heat exchanger 20, and is a motor composed of a fan such as a propeller fan and a DC fan motor that drives the fan, for example. And.
- the accumulator 22 is provided on the suction side of the compressor 1, and stores and compresses liquid refrigerant when an abnormality occurs in the air-conditioning and hot water supply complex system 100 or when there is a transient response of an operation state due to a change in operation control. It has a function to prevent liquid back to the machine 1.
- the supercooling heat exchanger 18 has a function of controlling the flow rate of the refrigerant by exchanging heat between the refrigerant flowing through the liquid extension pipe 9 and the refrigerant flowing through the low-pressure bypass pipe 24.
- the outdoor decompression mechanism 19 is provided between the outdoor heat exchanger 20 and the liquid extension pipe 9 side of the supercooling heat exchanger 18 and has a function as a decompression valve or an expansion valve, and decompresses and expands the refrigerant. Is.
- the outdoor pressure reducing mechanism 19 may be configured by a device whose opening degree can be variably controlled, for example, a precise flow rate control unit using an electronic expansion valve, an inexpensive refrigerant flow rate control unit such as a capillary tube, or the like.
- the low-pressure bypass decompression mechanism 23 is provided in the low-pressure bypass pipe 24 and functions as a decompression valve and an expansion valve.
- the low-pressure bypass decompression mechanism 23 decompresses and expands the refrigerant flowing through the low-pressure bypass pipe 24.
- the low-pressure bypass pressure-reducing mechanism 23 may be constituted by a device whose opening degree can be variably controlled, for example, a precise flow rate control means using an electronic expansion valve, an inexpensive refrigerant flow rate control means such as a capillary tube, or the like.
- the suction depressurization mechanism 25 is provided in the suction bypass pipe 26 and has a function as a pressure reducing valve or an expansion valve, and decompresses and expands the refrigerant flowing through the suction bypass pipe 26.
- the suction pressure reducing mechanism 25 may be constituted by a variable flow rate control means such as an electronic expansion valve, an inexpensive refrigerant flow rate control means such as a capillary tube, etc., whose opening degree can
- the heat source unit 301 is provided with various sensors shown below. That is, the heat source unit 301 is provided on the discharge side of the compressor 1 and is provided between the discharge pressure sensor 201 (high pressure detection device) for detecting the discharge pressure, the subcooling heat exchanger 18 and the branch unit 302, An intermediate pressure liquid temperature sensor 210 that detects the liquid refrigerant temperature on the intermediate pressure side, an intermediate pressure sensor 211 (intermediate pressure) that is provided between the high pressure side of the supercooling heat exchanger 18 and the outdoor pressure reducing mechanism 19 and detects the intermediate pressure.
- an outdoor liquid temperature sensor 212 that is provided on the liquid side of the outdoor heat exchanger 20 and detects the temperature of the liquid refrigerant
- a gas temperature sensor 213 is provided.
- the heat source unit 301 is provided on the outdoor air intake side of the heat source unit 301, detects the temperature of the outdoor air flowing into the unit, and the low pressure upstream side of the supercooling heat exchanger 18 ( A low-pressure bypass pipe 24) between the low-pressure bypass pressure reduction mechanism 23 and the supercooling heat exchanger 18), and a low-pressure liquid temperature sensor 215 for detecting a saturation temperature on the low-pressure side;
- a low-pressure gas temperature sensor 216 for detecting the gas refrigerant temperature on the low-pressure side and a suction pressure sensor 217 (low-pressure detection device) for detecting the suction pressure provided on the suction side of the compressor 1 are provided in the low-pressure bypass pipe 24. Is provided.
- the operations of the compressor 1, the four-way valve 11, the outdoor blower 21, the outdoor pressure reducing mechanism 19, the low pressure bypass pressure reducing mechanism 23, the suction pressure reducing mechanism 25, the first electromagnetic valve 2, the second electromagnetic valve 10, and the third electromagnetic valve 27 are as follows.
- the air conditioning and hot water supply combined system 100 is controlled by the control unit 103 that performs normal operation including various operation modes (full cooling operation mode, cold main operation mode, full warm operation mode, warm main operation mode) (see FIG. 2).
- the branch unit 302 is installed indoors, for example, to the heat source unit 301 via the liquid extension pipe 9 and the gas extension pipe 12, and to the use unit 303 via the indoor gas pipe 13 and the indoor liquid pipe 16, to the hot water supply liquid pipe. 7 is connected to the hot water supply unit 304, and constitutes a part of the refrigerant circuit in the combined air and water supply system 100.
- the branch unit 302 has a function of controlling the flow of the refrigerant according to the operation required for the use unit 303 and the hot water supply unit 304.
- the branch unit 302 includes a branch refrigerant circuit that constitutes a part of the refrigerant circuit.
- This branch refrigerant circuit has a hot water supply pressure reducing mechanism 8 for controlling the refrigerant distribution flow rate and an indoor pressure reduction mechanism (use side pressure reduction mechanism) 17 for controlling the refrigerant distribution flow rate as element devices. .
- the hot water supply pressure reducing mechanism 8 is provided in the hot water supply liquid pipe 7 in the branch unit 302.
- the indoor decompression mechanism 17 is provided in the indoor liquid piping 16 in the branch unit 302.
- the hot water supply decompression mechanism 8 and the indoor decompression mechanism 17 have functions as a decompression valve and an expansion valve, and decompress and expand the refrigerant flowing through the hot water supply liquid pipe 7 and the indoor liquid pipe 16.
- the hot water supply depressurization mechanism 8 and the indoor depressurization mechanism 17 may be configured by a device whose opening degree can be variably controlled, for example, a precise flow rate control means using an electronic expansion valve, an inexpensive refrigerant flow rate control means such as a capillary tube, or the like.
- the operation of the hot water supply decompression mechanism 8 is controlled by the control unit 103 that executes normal operation including the hot water supply operation mode of the hot water supply unit 304 (see FIG. 2).
- the operation of the indoor decompression mechanism 17 is controlled by the control unit 103 that executes normal operation including the cooling operation mode and the heating operation mode of the use unit 303 (see FIG. 2).
- various amounts detected by various temperature sensors and various pressure sensors are input to the measurement unit 101 and processed by the calculation unit 102.
- the air-conditioning hot water supply combined system 100 is based on the processing result of the calculating part 102, and the control part 103 makes the compressor 1, the 1st solenoid valve 2, the feed water pump 6, the hot water supply pressure reduction mechanism 8, and the 2nd solenoid valve. 10, four-way valve 11, indoor blower 15, indoor decompression mechanism 17, outdoor decompression mechanism 19, outdoor blower 21, low-pressure bypass decompression mechanism 23, suction decompression mechanism 25, third electromagnetic valve 27, Is to control. That is, the operation of the air-conditioning and hot water supply complex system 100 is comprehensively controlled by the measurement unit 101, the calculation unit 102, and the control unit 103. These may be constituted by a microcomputer or the like.
- the control unit 103 controls the driving frequency of the compressor 1, opening / closing of the first electromagnetic valve 2, water supply pump 6 rotation speed (including ON / OFF), opening degree of hot water supply decompression mechanism 8, switching of four-way valve 11, rotation speed of indoor blower 15 (including ON / OFF), opening degree of indoor decompression mechanism 17, outdoor decompression mechanism 19 ,
- the rotational speed of the outdoor blower 21 including ON / OFF
- the opening of the low pressure bypass decompression mechanism 23 the opening of the suction decompression mechanism 25, and the opening and closing of the third electromagnetic valve 27 are controlled. Is supposed to run.
- the measurement part 101, the calculating part 102, and the control part 103 may be provided integrally, and may be provided separately.
- the measurement unit 101, the calculation unit 102, and the control unit 103 may be provided in any unit.
- the measurement unit 101, the calculation unit 102, and the control unit 103 may be provided for each unit.
- the air conditioning and hot water supply complex system 100 controls each device (actuator) mounted on the heat source unit 301, the branch unit 302, the usage unit 303, and the hot water supply unit 304 in accordance with each operation load required for the usage unit 303.
- each device actuator mounted on the heat source unit 301, the branch unit 302, the usage unit 303, and the hot water supply unit 304 in accordance with each operation load required for the usage unit 303.
- the operation of the four-way valve and each solenoid valve in each operation mode is as shown in FIG.
- the four-way valve 11 is shown by a solid line, that is, the discharge side of the compressor 1 is connected to the indoor gas pipe 13 via the gas extension pipe 12, and the suction side of the compressor 1 is the outdoor heat exchanger. 20 is controlled to be connected.
- the utilization unit 303 is in the heating operation mode, and the hot water supply unit 304 is in the hot water supply operation mode.
- the first electromagnetic valve 2 is opened, the second electromagnetic valve 10 is opened, and the third electromagnetic valve 27 is closed.
- the compressor 1, the feed water pump 6, the indoor blower 15, and the outdoor blower 21 are started. Then, the low-pressure gas refrigerant is sucked into the compressor 1 and compressed to become a high-temperature / high-pressure gas refrigerant. Thereafter, the high-temperature and high-pressure gas refrigerant is distributed so as to flow through the first electromagnetic valve 2 or the second electromagnetic valve 10.
- the refrigerant that has flowed into the first solenoid valve 2 flows into the hot water supply unit 304 via the hot water supply extension pipe 3 and the hot water supply gas pipe 4.
- the refrigerant that has flowed into the hot water supply unit 304 flows into the hot water supply side heat exchanger 5, performs heat exchange with the water supplied by the water supply pump 6, is condensed, becomes a high-pressure liquid refrigerant, and flows out of the hot water supply side heat exchanger 5. To do.
- the refrigerant that has heated water in the hot water supply side heat exchanger 5 flows into the branch unit 302 via the hot water supply liquid pipe 7 and is depressurized by the hot water supply depressurization mechanism 8, and the intermediate-pressure gas-liquid two-phase or liquid-phase refrigerant and Become. Thereafter, it merges with the refrigerant flowing through the indoor decompression mechanism 17 and flows into the liquid extension pipe 9.
- the hot water supply depressurization mechanism 8 controls the flow rate of the refrigerant flowing through the hot water supply side heat exchanger 5, and the hot water supply side heat exchanger 5 has hot water supply required in the use situation of hot water in the space where the hot water supply unit 304 is installed. A refrigerant having a flow rate corresponding to the load flows.
- the hot water supply depressurization mechanism 8 is controlled by the control unit 103 so that the degree of supercooling on the liquid side of the hot water supply side heat exchanger 5 becomes a predetermined value.
- the degree of supercooling on the liquid side of the hot water supply side heat exchanger 5 is obtained by calculating a saturation temperature (condensation temperature) from the pressure detected by the discharge pressure sensor 201 and subtracting the temperature detected by the hot water supply liquid temperature sensor 204. It is done.
- the refrigerant flowing into the second electromagnetic valve 10 flows to the branch unit 302 via the four-way valve 11 and the gas extension pipe 12. Thereafter, it flows through the indoor gas pipe 13 and flows into the utilization unit 303.
- the refrigerant that has flowed into the utilization unit 303 flows into the indoor heat exchanger 14, performs heat exchange with the indoor air supplied by the indoor blower 15, is condensed, becomes a high-pressure liquid refrigerant, and flows out of the indoor heat exchanger 14. .
- the refrigerant that has heated the indoor air in the indoor heat exchanger 14 flows into the branch unit 302 via the indoor liquid pipe 16, is decompressed by the indoor decompression mechanism 17, and is an intermediate-pressure gas-liquid two-phase or liquid-phase refrigerant. Become. Thereafter, it merges with the refrigerant flowing through the hot water supply decompression mechanism 8 and flows into the liquid extension pipe 9.
- the indoor decompression mechanism 17 controls the flow rate of the refrigerant flowing through the indoor heat exchanger 14, and the indoor heat exchanger 14 has a flow rate according to the heating load required in the air-conditioning target area where the use unit 303 is installed.
- the refrigerant is flowing.
- the indoor decompression mechanism 17 is controlled by the control unit 103 so that the degree of supercooling on the liquid side of the indoor heat exchanger 14 becomes a predetermined value.
- the degree of supercooling on the liquid side of the indoor heat exchanger 14 is obtained by calculating a saturation temperature (condensation temperature) from the pressure detected by the discharge pressure sensor 201 and subtracting the temperature detected by the indoor liquid temperature sensor 208. .
- the refrigerant that has flowed into the liquid extension pipe 9 flows out of the branch unit 302 and flows into the heat source unit 301.
- the refrigerant that has flowed into the heat source unit 301 is divided into one that flows to the low-pressure bypass pipe 24 and one that flows to the high-pressure side of the supercooling heat exchanger 18.
- the refrigerant flowing into the high-pressure side of the supercooling heat exchanger 18 is cooled by the refrigerant flowing through the low-pressure side (that is, the low-pressure bypass pipe 24), and further distributed to the refrigerant flowing through the suction bypass pipe 26 and the refrigerant flowing into the outdoor decompression mechanism 19. Is done.
- the refrigerant flowing to the outdoor decompression mechanism 19 is decompressed to a low pressure, then flows into the outdoor heat exchanger 20, and is evaporated by exchanging heat with the outdoor air supplied by the outdoor blower 21, thereby becoming a low-pressure gas refrigerant. .
- This refrigerant flows out of the outdoor heat exchanger 20, and then merges with the refrigerant flowing through the low-pressure bypass pipe 24 via the four-way valve 11 and then flows into the accumulator 22.
- the outdoor pressure-reducing mechanism 19 is controlled by the control unit 103 so that the differential pressure between the intermediate pressure and the low pressure becomes a predetermined value.
- the differential pressure between the intermediate pressure and the low pressure is obtained by subtracting the pressure detected by the suction pressure sensor 217 from the pressure detected by the intermediate pressure sensor 211.
- the outdoor pressure reducing mechanism 19 is controlled to have an opening degree at which the differential pressure between the intermediate pressure and the low pressure becomes a predetermined value, and controls the flow rate of the refrigerant flowing through the outdoor pressure reducing mechanism 19, so that the differential pressure between the intermediate pressure and the low pressure is , A state having a predetermined value is obtained.
- the refrigerant flowing into the low pressure bypass pipe 24 is depressurized by the low pressure bypass depressurization mechanism 23 and then heated by the refrigerant flowing on the high pressure side on the low pressure side of the supercooling heat exchanger 18 and passes through the four-way valve 11. Merge with the refrigerant. Thereafter, it flows into the accumulator 22.
- the low pressure bypass pressure reducing mechanism 23 is controlled by the control unit 103 so that the degree of superheat of the refrigerant on the low pressure gas side of the supercooling heat exchanger 18 becomes a predetermined value.
- the degree of superheat of the refrigerant on the low-pressure gas side of the supercooling heat exchanger 18 is obtained by subtracting the temperature detected by the low-pressure liquid temperature sensor 215 from the temperature detected by the low-pressure gas temperature sensor 216.
- the refrigerant flowing into the suction bypass pipe 26 is decompressed by the suction decompression mechanism 25 and then merges with the refrigerant that has flowed out of the accumulator 22.
- the opening degree of the suction pressure reducing mechanism 25 is controlled by the control unit 103 to be fully closed during normal operation.
- the refrigerant that has flowed into the accumulator 22 then merges with the refrigerant that has flowed through the suction bypass pipe 26 and is sucked into the compressor 1 again.
- the control part 103 it is controlled by the control part 103 so that condensation temperature may become predetermined value.
- the outdoor air blower 21 is controlled by the control unit 103 so that the evaporation temperature becomes a predetermined value in accordance with the outside air temperature detected by the outside air temperature sensor 214.
- the condensation temperature is a saturation temperature calculated from the pressure detected from the discharge pressure sensor 201
- the evaporation temperature is a saturation temperature calculated from the pressure detected from the suction pressure sensor 217.
- FIG. 4 is a schematic explanatory diagram for explaining control for avoiding the increase in the low-pressure side pressure, the avoidance of the discharge temperature increase, and the avoidance of the increase in the high-pressure side pressure under the high outside air condition executed by the air conditioning and hot water supply complex system 100. is there.
- FIG. 4 (a) shows an outline of a change in the operating state when the control for avoiding a low-pressure side pressure increase under a high outside air condition of the air conditioning and hot water supply combined system 100 is performed
- FIG. 4 (b) is a control for avoiding a discharge temperature increase.
- 4 (c) shows the outline of the change in the operation state when the control for avoiding the high pressure side pressure increase is executed.
- a broken line represents a state change before control
- a solid line represents a state change after control.
- the opening of the low-pressure bypass decompression mechanism 23 is made larger than the predetermined value, so that the liquid refrigerant
- the refrigerant flow rate of the outdoor heat exchanger 20 is reduced. Since the refrigerant becomes saturated gas at the inlet of the accumulator 22, the degree of superheat (SH) of the refrigerant on the gas side of the outdoor heat exchanger 20 increases as the liquid refrigerant flows through the low-pressure bypass pipe 24.
- the degree of superheat of the outdoor heat exchanger 20 increases, the amount of gas refrigerant increases in the outdoor heat exchanger 20, and the low-pressure side pressure can be reduced.
- the refrigerant on the liquid side of the hot water supply side heat exchanger 5 is a supercooled liquid by controlling the opening degree of the hot water supply decompression mechanism 8 by the normal operation control by the control unit 103.
- coolant of the indoor heat exchanger 14 liquid side is a supercooled liquid by controlling the opening degree of the indoor decompression mechanism 17.
- FIG. Therefore, the liquid refrigerant is secured at the inlet of the low pressure bypass pressure reducing mechanism 23, and the liquid refrigerant can flow to the inlet of the accumulator 22 by making the opening of the low pressure bypass pressure reducing mechanism 23 larger than a predetermined value.
- FIG. 5A shows the relationship between the degree of superheating on the gas side of the outdoor heat exchanger 20 and the evaporation temperature ET.
- the superheat degree target SHm OC [° C.] on the gas side of the outdoor heat exchanger 20 is set by the following formula (1).
- T OCai is the outside air temperature [° C.]
- ET max is the evaporation temperature upper limit [° C.].
- the sum of ET max and SHm OC is the temperature on the outdoor heat exchanger 20 gas side, and the temperature on the outdoor heat exchanger 20 gas side is equal to or lower than the outside air temperature T OCai .
- the degree of superheat on the gas side of the outdoor heat exchanger 20 is 2 for example.
- the temperature is higher than the degree C (third predetermined value) and the suction superheat degree of the compressor 1 is increased. Therefore, in this case, by opening the opening of the low pressure bypass pressure reducing mechanism 23 to be larger than a predetermined value and sending the liquid refrigerant to the low pressure side, the gas refrigerant flowing on the gas side of the outdoor heat exchanger 20 is cooled, By reducing the degree of superheat on the gas side of the outdoor heat exchanger 20, the suction superheat degree of the compressor can be reduced. Therefore, the discharge temperature of the compressor 1 can be lowered to 110 ° C. or lower.
- the amount of liquid refrigerant flowing through the low pressure bypass pipe 24 is controlled by the low pressure bypass decompression mechanism 23, thereby controlling the degree of superheat on the gas side of the outdoor heat exchanger 20, and An increase in pressure and an increase in discharge temperature can be avoided. Therefore, in the air conditioning and hot water supply combined system 100, it is possible to exhibit a high hot water supply capability even under high outside air conditions.
- FIG. 5B shows the relationship between the degree of supercooling on the liquid side of the hot water supply side heat exchanger 5, the condensation temperature CT, and the operation efficiency.
- the supercooling degree target SCm w [° C.] on the liquid side of the hot water supply side heat exchanger 5 is set by the following equations (2) and (3).
- CT opt is the condensation temperature [° C.] at which the operation efficiency is maximum
- T wimax, opt is the inlet temperature [° C.] of the water flowing into the hot water supply side heat exchanger 5 at the maximum hot water temperature
- T scow, opt is The temperature [° C.] on the hot water supply side heat exchanger 5 liquid side at CT opt
- ⁇ is the liquid phase reference temperature efficiency [ ⁇ ]. As the liquid phase reference temperature efficiency ⁇ increases, the amount of liquid refrigerant in the hot water supply side heat exchanger 5 increases, and more refrigerant exists on the high pressure side.
- CT opt , T SCOw, opt and T wimax, opt are obtained by testing and simulation, and ⁇ is calculated. That is, ⁇ is a value set in advance in the device, and is obtained, for example, as follows.
- the hot water temperature is set to the maximum hot water temperature of the equipment (60 ° C when the maximum hot water temperature is 60 ° C), and the degree of supercooling on the liquid side of the hot water supply side heat exchanger 5 is adjusted by the hot water supply pressure reducing mechanism 8 so
- the condensation temperature at that time is CT opt
- the temperature on the liquid side of the hot water supply side heat exchanger 5 is T scow, opt
- T wimax, opt be the inlet temperature of water flowing into the hot water supply side heat exchanger 5 at the time.
- the low-pressure side pressure becomes low and the discharge temperature rises.
- the discharge temperature is 110 ° C. (sixth predetermined value) or more and the reliability of the device is impaired
- the liquid refrigerant is supplied to the compressor 1 by increasing the opening of the suction pressure reducing mechanism 25 beyond a predetermined value.
- the discharge temperature can be reduced to 110 ° C. (sixth predetermined value) or less by flowing into the suction part and cooling the refrigerant in the discharge part.
- the four-way valve 11 is indicated by a solid line, that is, the discharge side of the compressor 1 is connected to the indoor gas pipe 13 via the gas extension pipe 12, and the suction side of the compressor 1 is the outdoor heat exchanger. 20 is controlled to be connected.
- the utilization unit 303 is in the cooling operation mode
- the hot water supply unit 304 is in the hot water supply operation mode
- the first solenoid valve 2 is controlled to be open
- the second solenoid valve 10 is closed
- the third solenoid valve 27 is controlled to open.
- the compressor 1, the feed water pump 6, the indoor blower 15, and the outdoor blower 21 are started. Then, the low-pressure gas refrigerant is sucked into the compressor 1 and compressed to become a high-temperature / high-pressure gas refrigerant. Thereafter, the high-temperature and high-pressure gas refrigerant flows through the first electromagnetic valve 2.
- the refrigerant that has flowed into the first solenoid valve 2 flows into the hot water supply unit 304 via the hot water supply extension pipe 3 and the hot water supply gas pipe 4.
- the refrigerant that has flowed into the hot water supply unit 304 flows into the hot water supply side heat exchanger 5, performs heat exchange with the water supplied by the water supply pump 6, is condensed, becomes a high-pressure liquid refrigerant, and flows out of the hot water supply side heat exchanger 5. To do.
- the refrigerant that has heated water in the hot water supply side heat exchanger 5 flows into the branch unit 302 via the hot water supply liquid pipe 7 and is depressurized by the hot water supply depressurization mechanism 8, and the intermediate-pressure gas-liquid two-phase or liquid-phase refrigerant and Become. Thereafter, the refrigerant is distributed into the refrigerant flowing into the liquid extension pipe 9 and the refrigerant flowing into the indoor decompression mechanism 17.
- the hot water supply depressurization mechanism 8 controls the flow rate of the refrigerant flowing through the hot water supply side heat exchanger 5, and the hot water supply side heat exchanger 5 has hot water supply required in the use situation of hot water in the space where the hot water supply unit 304 is installed. A refrigerant having a flow rate corresponding to the load flows.
- the hot water supply depressurization mechanism 8 is controlled by the control unit 103 so that the degree of supercooling on the liquid side of the hot water supply side heat exchanger 5 becomes a predetermined value.
- the method for obtaining the degree of supercooling is as described in the heating only operation mode.
- the refrigerant that has flowed into the indoor decompression mechanism 17 is decompressed by the indoor decompression mechanism 17, becomes a low-pressure gas-liquid two-phase state, and flows into the utilization unit 303 via the indoor liquid piping 16.
- the refrigerant that has flowed into the utilization unit 303 flows into the indoor heat exchanger 14 and is evaporated by exchanging heat with the indoor air supplied by the indoor blower 15 to become a low-pressure gas refrigerant.
- the indoor decompression mechanism 17 is controlled by the control unit 103 so that the degree of superheat of the refrigerant on the gas side of the indoor heat exchanger 14 becomes a predetermined value.
- the degree of superheat of the refrigerant on the gas side of the indoor heat exchanger 14 is obtained by subtracting the temperature detected by the indoor liquid temperature sensor 208 from the temperature detected by the indoor gas temperature sensor 207.
- the indoor decompression mechanism 17 controls the flow rate of the refrigerant flowing through the indoor heat exchanger 14 so that the degree of superheat of the refrigerant on the gas side of the indoor heat exchanger 14 becomes a predetermined value, it evaporates in the indoor heat exchanger 14.
- the low-pressure gas refrigerant thus obtained has a predetermined degree of superheat.
- required in the air-conditioning space in which the utilization unit 303 was installed flows through the indoor heat exchanger 14.
- the refrigerant that has flowed out of the indoor heat exchanger 14 then flows through the indoor gas pipe 13 and the branch unit 302 and then flows through the third electromagnetic valve 27 through the gas extension pipe 12. This refrigerant merges with the refrigerant that has passed through the four-way valve 11.
- the refrigerant flowing into the liquid extension pipe 9 flows out from the branch unit 302 and flows into the heat source unit 301.
- the refrigerant that has flowed into the heat source unit 301 is distributed to the refrigerant that flows to the high pressure side of the supercooling heat exchanger 18 when it flows through the low pressure bypass pipe 24.
- the refrigerant flowing into the high-pressure side of the supercooling heat exchanger 18 is cooled by the refrigerant flowing through the low-pressure side (that is, the low-pressure bypass pipe 24), and further distributed to the refrigerant flowing through the suction bypass pipe 26 and the refrigerant flowing into the outdoor decompression mechanism 19. Is done.
- the refrigerant flowing to the outdoor decompression mechanism 19 is decompressed to a low pressure, then flows into the outdoor heat exchanger 20, and is evaporated by exchanging heat with the outdoor air supplied by the outdoor blower 21, thereby becoming a low-pressure gas refrigerant. .
- the refrigerant flows out of the outdoor heat exchanger 20, it merges with the refrigerant that has passed through the third electromagnetic valve 27 and the refrigerant that has flowed through the low-pressure bypass pipe 24 via the four-way valve 11, and then the accumulator. 22 flows into.
- the outdoor pressure-reducing mechanism 19 is controlled by the control unit 103 so that the differential pressure between the intermediate pressure and the low pressure becomes a predetermined value.
- the method for obtaining the differential pressure between the intermediate pressure and the low pressure is as described in the heating only operation mode.
- the outdoor pressure reducing mechanism 19 is controlled to have an opening degree at which the differential pressure between the intermediate pressure and the low pressure becomes a predetermined value, and controls the flow rate of the refrigerant flowing through the outdoor pressure reducing mechanism 19, so that the differential pressure between the intermediate pressure and the low pressure is , A state having a predetermined value is obtained.
- the refrigerant having a flow rate corresponding to the cooling load required in the air-conditioned space flows to the use unit 303.
- the refrigerant flowing into the low-pressure bypass pipe 24 is depressurized by the low-pressure bypass depressurization mechanism 23, and then heated by the refrigerant flowing on the high-pressure side on the low-pressure side of the supercooling heat exchanger 18 and passes through the four-way valve 11. Merge with the refrigerant. Thereafter, it flows into the accumulator 22.
- the low pressure bypass pressure reducing mechanism 23 is controlled by the control unit 103 so that the degree of superheat of the refrigerant on the low pressure gas side of the supercooling heat exchanger 18 becomes a predetermined value.
- the method for obtaining the degree of superheat of the refrigerant on the low-pressure gas side of the supercooling heat exchanger 18 is as described in the heating only operation mode.
- the refrigerant flowing into the suction bypass pipe 26 is decompressed by the suction decompression mechanism 25 and then merges with the refrigerant that has flowed out of the accumulator 22.
- the opening degree of the suction pressure reducing mechanism 25 is controlled by the control unit 103 to be fully closed during normal operation.
- the refrigerant that has flowed into the accumulator 22 then merges with the refrigerant that has flowed through the suction bypass pipe 26 and is sucked into the compressor 1 again.
- requires in the compressor 1, it is controlled by the control part 103 so that a condensation temperature becomes a predetermined value.
- the outdoor fan 21 is controlled by the control unit 103 so that the evaporation temperature becomes a predetermined value.
- the air conditioning and hot water supply complex system 100 when high-temperature hot water supply (for example, 60 ° C. hot water supply) is performed when the outside air temperature is high in the warm main operation mode, the amount of liquid refrigerant flowing through the low pressure bypass pipe 24 is the same as in the full warm operation mode.
- the low pressure bypass pressure reduction mechanism 23 the degree of superheat on the gas side of the outdoor heat exchanger 15 can be controlled, and the low pressure side pressure rise and the discharge temperature rise can be avoided. Further, by controlling the degree of supercooling on the liquid side of the hot water supply side heat exchanger 5, it is possible to avoid an increase in the high pressure side pressure and realize an efficient operation state.
- the difference between the outside air temperature detected by the outside air temperature sensor 214 and the evaporation temperature is equal to or less than a predetermined value (5th predetermined value or less) (for example, 2 ° C. or less)
- a predetermined value for example, 2 ° C. or less
- the opening degree of the outdoor decompression mechanism 19 is made smaller than a predetermined value or is fully closed, and the exhaust heat recovery operation is performed by the indoor heat exchanger 14, thereby improving the efficiency.
- a good driving condition can be realized.
- the opening degree of the suction pressure reducing mechanism 25 is increased to be larger than a predetermined value. A rise can be avoided.
- the four-way valve 11 is indicated by a broken line, that is, the discharge side of the compressor 1 is connected to the outdoor heat exchanger 20, and the suction side of the compressor 1 is connected to the indoor gas pipe via the gas extension pipe 12. 13 is controlled to be connected.
- the use unit 303 is in the cooling operation mode, the hot water supply unit 304 is not performing the hot water supply operation, the first solenoid valve 2 is closed, the second solenoid valve 10 is opened, and the third solenoid valve 27 is closed. ing.
- the compressor 1, the indoor blower 15, and the outdoor blower 21 are started. Then, the low-pressure gas refrigerant is sucked into the compressor 1 and compressed to become a high-temperature / high-pressure gas refrigerant. Thereafter, the high-temperature and high-pressure gas refrigerant flows through the second electromagnetic valve 10. In addition, since the hot water supply operation is not performed in the hot water supply unit 304, the water supply pump 6 is controlled to be stopped.
- the refrigerant flowing into the second electromagnetic valve 10 flows into the outdoor heat exchanger 20 via the four-way valve 11 and is condensed by exchanging heat with the outdoor air supplied by the outdoor blower 21 to become a high-pressure liquid refrigerant. .
- the high-pressure liquid refrigerant flows through the outdoor decompression mechanism 19 whose opening degree is fully open, and then is distributed to one that flows through the high-pressure side of the supercooling heat exchanger 18 and one that flows through the suction bypass pipe 26.
- the refrigerant that has flowed into the high pressure side of the supercooling heat exchanger 18 is cooled by the refrigerant that flows through the low pressure side, flows out of the supercooling heat exchanger 18, and then flows through the liquid extension pipe 9 and the low pressure bypass pipe 24. And distributed.
- the refrigerant that has flowed into the liquid extension pipe 9 flows into the branch unit 302, flows through the indoor liquid pipe 16, is decompressed by the indoor decompression mechanism 17, enters a low-pressure gas-liquid two-phase state, and flows out of the branch unit 302. , Flows into the usage unit 303.
- the refrigerant that has flowed into the utilization unit 303 flows into the indoor heat exchanger 14 and is evaporated by exchanging heat with the indoor air supplied by the indoor blower 15 to become a low-pressure gas refrigerant.
- the indoor decompression mechanism 17 is controlled by the control unit 103 so that the degree of superheat of the refrigerant on the gas side of the indoor heat exchanger 14 becomes a predetermined value.
- the method for obtaining the degree of superheat is as described in the heating only operation mode.
- the hot water supply pressure reducing mechanism 8 is controlled to be fully closed.
- the indoor decompression mechanism 17 controls the flow rate of the refrigerant flowing through the indoor heat exchanger 14 so that the degree of superheat of the refrigerant on the gas side of the indoor heat exchanger 14 becomes a predetermined value, it evaporates in the indoor heat exchanger 14.
- the low-pressure gas refrigerant thus obtained has a predetermined degree of superheat.
- required in the air-conditioning space in which the utilization unit 303 was installed flows through the indoor heat exchanger 14.
- the refrigerant that has flowed out of the indoor heat exchanger 14 then flows through the gas extension pipe 12 after passing through the indoor gas pipe 13 and the branch unit 302, and merges with the refrigerant that has flowed through the low-pressure bypass pipe 24 via the four-way valve 11. To do.
- the refrigerant flowing into the low-pressure bypass pipe 24 is depressurized by the low-pressure bypass depressurization mechanism 23, and then heated by the refrigerant flowing on the high-pressure side on the low-pressure side of the supercooling heat exchanger 18 and passes through the four-way valve 11. Merge with the refrigerant. Thereafter, it flows into the accumulator 22.
- the low pressure bypass pressure reducing mechanism 23 is controlled by the control unit 103 so that the degree of supercooling of the refrigerant on the high pressure liquid side of the supercooling heat exchanger 18 becomes a predetermined value.
- the degree of supercooling of the refrigerant on the high pressure liquid side of the supercooling heat exchanger 18 is obtained from the difference in temperature detected by the intermediate pressure liquid temperature sensor 210 from the condensation temperature calculated from the pressure detected by the discharge pressure sensor 201. .
- the refrigerant flowing into the suction bypass pipe 26 is decompressed by the suction decompression mechanism 25 and then merges with the refrigerant that has flowed out of the accumulator 22.
- the opening degree of the suction pressure reducing mechanism 25 is controlled by the control unit 103 to be fully closed during normal operation.
- the refrigerant that has flowed into the accumulator 22 then merges with the refrigerant that has flowed through the suction bypass pipe 26 and is sucked into the compressor 1 again.
- the utilization unit 303 in the compressor 1, it is controlled by the control part 103 so that evaporation temperature may become a predetermined value.
- the outdoor air blower 21 is controlled by the control unit 103 so that the condensation temperature becomes a predetermined value in accordance with the outside air temperature detected by the outside air temperature sensor 214.
- the four-way valve 11 is indicated by a broken line, that is, the discharge side of the compressor 1 is connected to the outdoor heat exchanger 20, and the suction side of the compressor 1 is connected to the indoor gas pipe via the gas extension pipe 12. 13 is controlled to be connected.
- the utilization unit 303 is in the cooling operation mode
- the hot water supply unit 304 is in the hot water operation mode
- the first solenoid valve 2 is controlled to open
- the second solenoid valve 10 is opened
- the third solenoid valve 27 is controlled to close. .
- the compressor 1, the feed water pump 6, the indoor blower 15, and the outdoor blower 21 are started. Then, the low-pressure gas refrigerant is sucked into the compressor 1 and compressed to become a high-temperature / high-pressure gas refrigerant. Thereafter, the high-temperature and high-pressure gas refrigerant is distributed so as to flow through the first electromagnetic valve 2 or the second electromagnetic valve 10.
- the refrigerant that has flowed into the first solenoid valve 2 flows into the hot water supply unit 304 via the hot water supply extension pipe 3 and the hot water supply gas pipe 4.
- the refrigerant that has flowed into the hot water supply unit 304 flows into the hot water supply side heat exchanger 5, performs heat exchange with the water supplied by the water supply pump 6, is condensed, becomes a high-pressure liquid refrigerant, and flows out of the hot water supply side heat exchanger 5. To do.
- the refrigerant that has heated water in the hot water supply side heat exchanger 5 flows into the branch unit 302 via the hot water supply liquid pipe 7 and is depressurized by the hot water supply depressurization mechanism 8, and the intermediate-pressure gas-liquid two-phase or liquid-phase refrigerant and Become. Thereafter, it merges with the refrigerant flowing through the liquid extension pipe 9 and flows into the indoor decompression mechanism 17.
- the hot water supply depressurization mechanism 8 controls the flow rate of the refrigerant flowing through the hot water supply side heat exchanger 5, and the hot water supply side heat exchanger 5 has hot water supply required in the use situation of hot water in the space where the hot water supply unit 304 is installed. A refrigerant having a flow rate corresponding to the load flows.
- the hot water supply decompression mechanism 8 is controlled by the control unit 103 so that the degree of supercooling on the liquid side of the hot water supply side heat exchanger 5 becomes a predetermined value.
- the method for obtaining the degree of supercooling is as described in the heating only operation mode.
- the refrigerant flowing into the second electromagnetic valve 10 flows into the outdoor heat exchanger 20 via the four-way valve 11 and is condensed by exchanging heat with the outdoor air supplied by the outdoor blower 21. Becomes a refrigerant.
- the high-pressure liquid refrigerant is decompressed by the outdoor decompression mechanism 19, and then distributed to the refrigerant flowing through the high-pressure side of the supercooling heat exchanger 18 and the refrigerant flowing through the suction bypass pipe 26.
- the refrigerant flowing into the high pressure side of the supercooling heat exchanger 18 is cooled by the refrigerant flowing on the low pressure side, flows out of the supercooling heat exchanger 18, and then flows into the liquid extension pipe 9 and into the low pressure bypass pipe 24. And distributed.
- the outdoor pressure reducing mechanism 19 is controlled by the control unit 103 so that the degree of supercooling on the liquid side of the outdoor heat exchanger 20 becomes a predetermined value.
- the degree of supercooling on the liquid side of the outdoor heat exchanger 20 is obtained from the difference in temperature detected by the outdoor liquid temperature sensor 212 from the condensation temperature calculated from the pressure detected by the discharge pressure sensor 201.
- the refrigerant flowing through the liquid extension pipe 9 flows into the branch unit 302 and merges with the refrigerant that has passed through the hot water supply decompression mechanism 8. Thereafter, it flows through the indoor liquid piping 16 and is decompressed by the indoor decompression mechanism 17 to be in a low-pressure gas-liquid two-phase state and flows into the utilization unit 303.
- the refrigerant that has flowed into the utilization unit 303 flows into the indoor heat exchanger 14 and is evaporated by exchanging heat with the indoor air supplied by the indoor blower 15 to become a low-pressure gas refrigerant.
- the indoor decompression mechanism 17 is controlled by the control unit 103 so that the degree of superheat of the refrigerant on the gas side of the indoor heat exchanger 14 becomes a predetermined value.
- the method for obtaining the degree of superheat is as described in the heating only operation mode.
- the indoor decompression mechanism 17 controls the flow rate of the refrigerant flowing through the indoor heat exchanger 14 so that the degree of superheat of the refrigerant on the gas side of the indoor heat exchanger 14 becomes a predetermined value, it evaporates in the indoor heat exchanger 14.
- the low-pressure gas refrigerant thus obtained has a predetermined degree of superheat.
- required in the air-conditioning space in which the utilization unit 303 was installed flows through the indoor heat exchanger 14.
- the refrigerant that has flowed out of the indoor heat exchanger 14 then flows through the indoor gas pipe 13 and the branch unit 302 and then through the gas extension pipe 12, and then merges with the refrigerant that has flowed through the low-pressure bypass pipe 24 through the four-way valve 11. .
- the refrigerant flowing into the low-pressure bypass pipe 24 is depressurized by the low-pressure bypass depressurization mechanism 23 and then heated by the refrigerant flowing on the high-pressure side on the low-pressure side of the supercooling heat exchanger 18 and passes through the four-way valve 11. Merge with the refrigerant. Thereafter, it flows into the accumulator 22.
- the low-pressure bypass pressure-reducing mechanism 23 is controlled by the controller 103 so that the intermediate pressure and the low-pressure differential pressure have a predetermined value.
- the method for obtaining the differential pressure between the intermediate pressure and the low pressure is as described in the heating only operation mode.
- the refrigerant flowing into the suction bypass pipe 26 is decompressed by the suction decompression mechanism 25 and then merges with the refrigerant that has flowed out of the accumulator 22.
- the opening degree of the suction pressure reducing mechanism 25 is controlled by the control unit 103 to be fully closed.
- the refrigerant that has flowed into the accumulator 22 then merges with the refrigerant that has flowed through the suction bypass pipe 26 and is sucked into the compressor 1 again.
- the indoor pressure reducing mechanism 17 controls the amount of liquid refrigerant flowing through the low pressure bypass pipe 24.
- the degree of superheat on the gas side of the indoor heat exchanger 14 can be controlled to avoid an increase in the low-pressure side pressure.
- the degree of superheat on the gas side of the indoor heat exchanger 14 has become a predetermined value by controlling the opening degree of the indoor decompression mechanism 17, but the target value of this degree of superheat is By increasing the size, the indoor pressure reducing mechanism 17 controls the amount of liquid refrigerant flowing through the low pressure bypass pipe 24.
- the opening of the indoor decompression mechanism 17 is made smaller than a predetermined value, whereby the liquid refrigerant is bypassed to the low-pressure bypass pipe 24 and the refrigerant flow rate of the indoor heat exchanger 14 is reduced. Since the refrigerant becomes a saturated gas at the inlet of the accumulator 22, as the liquid refrigerant flows through the low-pressure bypass pipe 24, the degree of superheat (SH) of the refrigerant on the indoor heat exchanger 14 gas side increases. When the degree of superheat of the indoor heat exchanger 14 increases, the amount of gas refrigerant increases in the indoor heat exchanger 14, and the low-pressure side pressure can be reduced.
- the low-pressure bypass pressure reducing device 23 is adjusted so that the degree of supercooling on the high-pressure liquid side of the supercooling heat exchanger 18 is not more than a predetermined value, and the degree of superheating of the indoor heat exchanger 14 is increased so Can be reduced.
- the refrigerant on the outdoor heat exchanger 20 liquid side is a supercooled liquid by controlling the opening degree of the outdoor decompression mechanism 19 by the normal operation control by the control unit 103. Therefore, the liquid refrigerant is secured at the inlet of the low pressure bypass pressure reducing mechanism 23, and the liquid refrigerant can flow through the low pressure bypass pipe by making the opening of the indoor pressure reducing mechanism 17 smaller than a predetermined value. It can flow to the entrance of the accumulator 22.
- the amount of liquid refrigerant flowing through the low pressure bypass pipe 24 is controlled by the indoor pressure reducing mechanism 17 or the low pressure bypass pressure reducing device 23, whereby the degree of superheat on the gas side of the indoor heat exchanger 14 is controlled. It is possible to control and avoid an increase in pressure on the low pressure side. Therefore, a high hot water supply capability can be obtained even under high outside air conditions.
- the opening degree of the suction pressure reducing mechanism 25 is increased to be larger than a predetermined value. A rise can be avoided.
- the air conditioning and hot water supply complex system 100 can ensure hot water supply capacity in a state of high operating efficiency even under high outdoor air conditions. Therefore, in the air conditioning and hot water supply combined system 100, the use unit 303 performs the cooling operation or the heating operation in the normal operation including the full warm operation mode, the warm main operation mode, the full cool operation mode, and the cool main operation mode in the high outside air condition. At the same time, even when the hot water supply unit 304 performs a hot water supply operation, a highly efficient operation can be realized.
- the refrigerant When applying a refrigerant whose operating pressure is higher than the critical pressure, such as carbon dioxide, the refrigerant becomes a liquid refrigerant below the pseudocritical temperature, so the degree of supercooling is set by the pseudocritical temperature instead of the saturation temperature.
- the contents of the first embodiment can be applied.
- FIG. FIG. 6 is a refrigerant circuit diagram showing a refrigerant circuit configuration of an air conditioning and hot water supply complex system 200 according to Embodiment 2 of the present invention. Based on FIG. 6, a structure and operation
- the difference from the first embodiment described above will be mainly described, and parts having the same functions as those in the first embodiment will be denoted by the same reference numerals and description thereof will be omitted.
- This combined air-conditioning and hot-water supply system 200 is capable of simultaneously processing the cooling operation or heating operation selected in the use side unit and the hot-water supply operation in the hot water supply unit by performing the vapor compression refrigeration cycle operation. It is a multi-system air conditioning and hot water supply complex system. This combined air-conditioning and hot-water supply system 200 can perform an air-conditioning operation and a hot-water supply operation at the same time, and can maintain a high hot-water temperature even under a high outside air temperature condition, thereby realizing a highly efficient operation.
- the circuit configuration of the air conditioning and hot water supply complex system 200 is the same as that of the air conditioning and hot water supply complex system 100 according to the first embodiment except that the bypass circuit (low pressure bypass pipe 24), the low pressure bypass pressure reduction mechanism 23, the supercooling heat exchanger 18 and the accumulator 22 are removed.
- a receiver 28 having a function as a liquid receiver for storing an intermediate pressure or high pressure surplus refrigerant is connected to the liquid extension pipe 9 between the branch unit 302 and the branch portion between the outdoor pressure reducing mechanism 19 and the suction pressure reducing mechanism 25. It has been installed.
- the outdoor refrigerant circuit provided in the heat source unit 301 includes the compressor 1, the four-way valve 11, the outdoor heat exchanger 20, the three electromagnetic valves, the outdoor pressure reducing mechanism 19, and the suction pressure reducing mechanism 25. , And receiver 28 as element devices.
- the air-conditioning and hot water supply combined system 200 executes four operation modes (a warming operation mode, a warming main operation mode, a cooling main operation mode, and a cooling operation mode), similarly to the air conditioning and hot water supply complex system 100 according to the first embodiment. be able to.
- the degree of opening of the outdoor decompression mechanism 19 is made smaller than a predetermined value to overheat the gas side of the outdoor heat exchanger 20.
- the degree of superheat on the gas side of the indoor heat exchanger 14 is increased by reducing the opening of the indoor decompression mechanism 17 below a predetermined value, An increase in the low-pressure side pressure can be avoided.
- the degree of superheat on the gas side of the outdoor heat exchanger 20 is reduced by increasing the degree of opening of the outdoor pressure reducing mechanism 19 above a predetermined value.
- the degree of inhalation superheat can be reduced. Therefore, the discharge temperature of the compressor 1 can be lowered.
- the difference between the outside air temperature detected by the outside air temperature sensor 214 and the evaporation temperature is equal to or less than a predetermined value (for example, 2 ° C. or less).
- a predetermined value for example, 2 ° C. or less.
- the opening degree of the outdoor decompression mechanism 19 is made smaller than a predetermined value, or is fully closed, and the exhaust heat recovery operation is performed by the indoor heat exchanger 14, thereby improving the efficiency. A good driving condition can be obtained.
- the suction decompression mechanism 25 is opened by making the opening degree larger than a predetermined value. An increase in temperature can be avoided.
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Abstract
Description
実施の形態1.
図1は、本発明の実施の形態1に係る空調給湯複合システム100の冷媒回路構成を示す冷媒回路図である。図2は、空調給湯複合システム100の各種センサ情報の処理及び制御機器の対象を概略化して示した概略図である。図3は、熱源ユニット301の運転モードに対する四方弁11及び各電磁弁の動作内容を示した表である。図4は、空調給湯複合システム100が実行する高外気条件での低圧側圧力上昇、高圧側圧力上昇、吐出温度上昇を回避するための制御を説明するための概略説明図である。図5は、過熱度に対する蒸発温度の変化または過冷却度に対する凝縮温度及び運転効率の変化を説明するための概略図である。図1~図5に基づいて、空調給湯複合システム100の構成及び動作について説明する。なお、図1を含め、以下の図面では各構成部材の大きさの関係が実際のものとは異なる場合がある。
空調給湯複合システム100は、熱源ユニット301と、分岐ユニット302と、利用ユニット303と、を有している。熱源ユニット301と分岐ユニット302とは、冷媒配管である液延長配管9と冷媒配管であるガス延長配管12とで接続されている。給湯ユニット304は、一方が冷媒配管である給湯ガス配管4及び冷媒配管である給湯延長配管3を介して熱源ユニット301に接続され、他方が冷媒配管であり給湯液配管7を介して分岐ユニット302に接続されている。利用ユニット303と分岐ユニット302とは、冷媒配管である室内ガス配管13と冷媒配管である室内液配管16とで接続されている。
空調給湯複合システム100が実行可能な運転モードについて簡単に説明しておく。空調給湯複合システム100では、接続されている給湯ユニット304の給湯負荷、及び、利用ユニット303の冷房負荷及び暖房負荷の割合によって、熱源ユニット301の運転モードが決定されるようになっている。空調給湯複合システム100は、4つの運転モード(全暖運転モード、暖主運転モード、全冷運転モード、冷主運転モード)を実行するようになっている。
利用ユニット303は、空調対象域に調和空気を吹き出すことができる場所(たとえば、屋内の天井への埋め込みや吊り下げ等により、又は、壁面への壁掛け等)に設置されている。利用ユニット303は、分岐ユニット302と液延長配管9及びガス延長配管12を介して熱源ユニット301に接続されており、空調給湯複合システム100における冷媒回路の一部を構成している。
給湯ユニット304は、たとえば屋外等に設置された図示省略の給湯タンクに沸き上げた湯を供給する機能を有している。また、給湯ユニット304は、一方が給湯ガス配管4と給湯延長配管3とを介して熱源ユニット301に、他方が給湯液配管7を介して分岐ユニット302に接続されており、空調給湯複合システム100における冷媒回路の一部を構成している。
熱源ユニット301は、たとえば屋外に設置されており、液延長配管9、ガス延長配管12及び分岐ユニット302を介して利用ユニット303に接続され、給湯延長配管3、給湯ガス配管4及び分岐ユニット302を介して給湯ユニット304に、接続されており、空調給湯複合システム100における冷媒回路の一部を構成している。
分岐ユニット302は、たとえば屋内に設置され、液延長配管9とガス延長配管12とを介して熱源ユニット301に、室内ガス配管13と室内液配管16とを介して利用ユニット303に、給湯液配管7を介して給湯ユニット304に接続されており、空調給湯複合システム100における冷媒回路の一部を構成している。分岐ユニット302は、利用ユニット303及び給湯ユニット304に要求されている運転に応じて冷媒の流れを制御する機能を有している。
空調給湯複合システム100は、利用ユニット303に要求されるそれぞれの運転負荷に応じて熱源ユニット301、分岐ユニット302、利用ユニット303、及び、給湯ユニット304に搭載されている各機器(アクチュエーター)の制御を行ない、全暖運転モード、暖主運転モード、全冷運転モード、あるいは、冷主運転モードを実行する。各運転モードにおける四方弁及び各電磁弁の動作は、図3に示す通りである。
全暖運転モードでは四方弁11が実線で示される状態、すなわち圧縮機1の吐出側がガス延長配管12を経由して室内ガス配管13に接続され、かつ、圧縮機1の吸入側が室外熱交換器20に接続された状態に制御される。また、利用ユニット303は暖房運転モード、給湯ユニット304は給湯運転モードであり、第1電磁弁2は開、第2電磁弁10は開、第3電磁弁27は閉に制御されている。
暖主運転モードでは四方弁11が実線で示される状態、すなわち圧縮機1の吐出側がガス延長配管12を経由して室内ガス配管13に接続され、かつ、圧縮機1の吸入側が室外熱交換器20に接続された状態に制御される。また、利用ユニット303は冷房運転モード、給湯ユニット304は給湯運転モードであり、第1電磁弁2は開、第2電磁弁10は閉、第3電磁弁27は開に制御されている。
全冷運転モードでは四方弁11が破線で示される状態、すなわち圧縮機1の吐出側が室外熱交換器20に接続され、かつ、圧縮機1の吸入側がガス延長配管12を経由して室内ガス配管13に接続された状態に制御される。また、利用ユニット303は冷房運転モードであり、給湯ユニット304は給湯運転を行なっておらず、第1電磁弁2は閉、第2電磁弁10は開、第3電磁弁27は閉に制御されている。
冷主運転モードでは四方弁11が破線で示される状態、すなわち圧縮機1の吐出側が室外熱交換器20に接続され、かつ、圧縮機1の吸入側がガス延長配管12を経由して室内ガス配管13に接続された状態に制御される。また、利用ユニット303は冷房運転モードであり、給湯ユニット304は給湯運転モードであり、第1電磁弁2は開、第2電磁弁10は開、第3電磁弁27は閉に制御されている。
図6は、本発明の実施の形態2に係る空調給湯複合システム200の冷媒回路構成を示す冷媒回路図である。図6に基づいて、空調給湯複合システム200の構成及び動作について説明する。なお、この実施の形態2では上述した実施の形態1との相違点を中心に説明するものとし、実施の形態1と同一作用である部分には、同一符号を付して説明を省略するものとする。
空調給湯複合システム200の回路構成は、実施の形態1に係る空調給湯複合システム100からバイパス回路(低圧バイパス配管24)、低圧バイパス減圧機構23、過冷却熱交換器18及びアキュムレーター22を外し、中間圧又は高圧の余剰冷媒を貯留する受液器としての機能を有するレシーバー28を、分岐ユニット302と、室外減圧機構19と吸入減圧機構25との分岐部と、の間における液延長配管9に設置したものとなっている。つまり、熱源ユニット301に備えられている室外側冷媒回路は、圧縮機1と、四方弁11と、室外熱交換器20と、3つの電磁弁と、室外減圧機構19と、吸入減圧機構25と、レシーバー28と、を要素機器として有している。
空調給湯複合システム200は、実施の形態1に係る空調給湯複合システム100と同様に、4つの運転モード(全暖運転モード、暖主運転モード、冷主運転モード、全冷運転モード)を実行することができる。
Claims (10)
- 少なくとも利用側熱交換器が搭載された1台又は複数台の利用ユニットと、
少なくとも給湯側熱交換器が搭載された1台又は複数台の給湯ユニットと、
前記利用ユニットと前記給湯ユニットに接続され、圧縮機、熱源側熱交換器、熱源側減圧機構、高圧側の液冷媒を低圧側へとバイパスするバイパス回路、前記バイパス回路に設けられた低圧バイパス減圧機構、アキュムレーター、及び、高圧側の液冷媒と前記バイパス回路を流れる低圧側の冷媒とを熱交換させる過冷却熱交換器が搭載された1台又は複数台の熱源ユニットと、
前記利用ユニット及び前記給湯ユニットと前記熱源ユニットに接続され、前記利用ユニットの運転状態に応じて前記利用ユニットに流入させる冷媒の流れを制御する利用側減圧機構、及び、前記給湯ユニットの運転状態に応じて前記給湯ユニットに流入させる冷媒の流れを制御する給湯減圧機構が搭載された1台又は複数台の分岐ユニットと、を有し、
蒸発圧力又は該蒸発圧力から演算される蒸発温度が予め定められている第1所定値以上となったとき、前記低圧バイパス減圧機構の開度によって、前記過冷却熱交換器の低圧ガス側における冷媒の過熱度又は前記過冷却熱交換器の高圧液側における冷媒の過冷却度を制御し、蒸発圧力又は該蒸発圧力から演算される蒸発温度が前記第1所定値以下となるようにしている
ことを特徴とする空調給湯複合システム。 - 前記低圧バイパス減圧機構は、
前記熱源側熱交換器が冷媒の蒸発器となるとき、
前記過冷却熱交換器の低圧ガス側における冷媒の過熱度が予め定められている所定値になるような開度に制御され、
前記熱源側熱交換器が冷媒の凝縮器となるとき、
前記過冷却熱交換器の高圧液側における冷媒の過冷却度が予め定められている所定値になるような開度に制御される
ことを特徴とする請求項1に記載の空調給湯複合システム。 - 少なくとも利用側熱交換器が搭載された1台又は複数台の利用ユニットと、
少なくとも給湯側熱交換器が搭載された1台又は複数台の給湯ユニットと、
前記利用ユニットと前記給湯ユニットに接続され、圧縮機、熱源側熱交換器、熱源側減圧機構、及び、レシーバーが搭載された1台又は複数台の熱源ユニットと、
前記利用ユニット及び前記給湯ユニットと前記熱源ユニットに接続され、前記利用ユニットの運転状態に応じて前記利用ユニットに流入させる冷媒の流れを制御する利用側減圧機構、及び、前記給湯ユニットの運転状態に応じて前記給湯ユニットに流入させる冷媒の流れを制御する給湯減圧機構が搭載された1台又は複数台の分岐ユニットと、を有し、
蒸発圧力又は該蒸発圧力から演算される蒸発温度が予め定められている第1所定値以上となったとき、前記熱源側減圧機構又は前記利用側減圧機構の開度によって、前記熱源側熱交換器のガス側の過熱度又は前記利用側熱交換器のガス側の過熱度を制御し、蒸発圧力又は該蒸発圧力から演算される蒸発温度が前記第1所定値以下となるようにしている
ことを特徴とする空調給湯複合システム。 - 前記熱源側熱交換器が冷媒の蒸発器となるとき、
前記熱源側減圧機構が、
前記熱源側熱交換器のガス側の過熱度が予め定められている所定値になるような開度に制御され、
前記熱源側熱交換器が冷媒の凝縮器となるとき、
前記利用側減圧機構が、
前記利用側熱交換器のガス側の過熱度が予め定められている所定値になるような開度に制御される
ことを特徴とする請求項3に記載の空調給湯複合システム。 - 凝縮圧力又は前記圧縮機から吐出される冷媒の吐出圧力から演算される凝縮温度が予め定められている第2所定値以上となったとき、前記給湯減圧機構の開度によって、前記給湯側熱交換器の液側の過冷却度を制御し、凝縮圧力又は前記圧縮機から吐出される冷媒の吐出圧力から演算される凝縮温度が前記第2所定値以下となるようにしている
ことを特徴とする請求項1~4のいずれか一項に記載の空調給湯複合システム。 - 前記給湯減圧機構の開度によって、
運転効率が最も高くなるように前記給湯側熱交換器の液側の過冷却度が制御される
ことを特徴とする請求項5に記載の空調給湯複合システム。 - 前記熱源側熱交換器のガス側の過熱度が、予め定められている第3所定値以上、かつ、前記圧縮機から吐出される冷媒の吐出温度が、予め定められている第4所定値以上になったとき、
前記低圧バイパス減圧機構の開度を所定値よりも大きくして、前記熱源側熱交換器のガス側の過熱度を小さくし、前記吐出温度を前記第4所定値以下となるようにしている
ことを特徴とする請求項1、2、5又は6に記載の空調給湯複合システム。 - 前記利用側熱交換器が冷媒の蒸発器、前記給湯側熱交換器が冷媒の凝縮器、前記熱源側熱交換器が冷媒の蒸発器となる運転において、
外気温度と蒸発温度との差が予め定められている第5所定値以下となったとき、
前記熱源側減圧機構の開度を所定値よりも小さく又は全閉にし、完全排熱回収運転を行なうようにしている
ことを特徴とする請求項1~7のいずれか一項に記載の空調給湯複合システム。 - 前記過冷却熱交換器又は前記レシーバーと前記熱源側減圧機構との間から前記圧縮機の吸入部へとつなぐ第2バイパス回路と、前記第2バイパス回路に設けられている吸入減圧機構と、を備え、
前記圧縮機から吐出される冷媒の吐出温度が予め定められている第6所定値以上となったとき、前記吸入減圧機構の開度によって、前記吐出温度を前記第6所定値以下となるようにしている
ことを特徴とする請求項1~8のいずれか一項に記載の空調給湯複合システム。 - 作動圧力が臨界圧力以上となる冷媒を適用し、擬臨界温度によって過冷却度を求めるようにしている
ことを特徴とする請求項1~9のいずれか一項に記載の空調給湯複合システム。
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US20130019624A1 (en) | 2013-01-24 |
CN102844630A (zh) | 2012-12-26 |
JPWO2011125111A1 (ja) | 2013-07-08 |
ES2877210T3 (es) | 2021-11-16 |
US9068766B2 (en) | 2015-06-30 |
CN102844630B (zh) | 2015-01-28 |
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