WO2016084186A1 - 空調給湯複合システム - Google Patents
空調給湯複合システム Download PDFInfo
- Publication number
- WO2016084186A1 WO2016084186A1 PCT/JP2014/081348 JP2014081348W WO2016084186A1 WO 2016084186 A1 WO2016084186 A1 WO 2016084186A1 JP 2014081348 W JP2014081348 W JP 2014081348W WO 2016084186 A1 WO2016084186 A1 WO 2016084186A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- water supply
- hot water
- unit
- temperature
- mode
- Prior art date
Links
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 title claims abstract description 291
- 238000004378 air conditioning Methods 0.000 title claims abstract description 52
- 238000010438 heat treatment Methods 0.000 claims abstract description 68
- 230000005494 condensation Effects 0.000 claims abstract description 52
- 238000009833 condensation Methods 0.000 claims abstract description 52
- 239000003507 refrigerant Substances 0.000 claims description 107
- 238000004891 communication Methods 0.000 claims description 29
- 230000008859 change Effects 0.000 claims description 12
- 239000007788 liquid Substances 0.000 description 41
- 238000001816 cooling Methods 0.000 description 33
- 238000000034 method Methods 0.000 description 24
- 230000008569 process Effects 0.000 description 24
- 238000010586 diagram Methods 0.000 description 9
- 239000000203 mixture Substances 0.000 description 8
- 239000012071 phase Substances 0.000 description 7
- 230000007704 transition Effects 0.000 description 7
- 230000009471 action Effects 0.000 description 5
- 230000006866 deterioration Effects 0.000 description 5
- VOPWNXZWBYDODV-UHFFFAOYSA-N Chlorodifluoromethane Chemical compound FC(F)Cl VOPWNXZWBYDODV-UHFFFAOYSA-N 0.000 description 4
- LYCAIKOWRPUZTN-UHFFFAOYSA-N Ethylene glycol Chemical compound OCCO LYCAIKOWRPUZTN-UHFFFAOYSA-N 0.000 description 3
- DNIAPMSPPWPWGF-UHFFFAOYSA-N Propylene glycol Chemical compound CC(O)CO DNIAPMSPPWPWGF-UHFFFAOYSA-N 0.000 description 3
- 230000002528 anti-freeze Effects 0.000 description 3
- 238000001704 evaporation Methods 0.000 description 3
- 230000008020 evaporation Effects 0.000 description 3
- 238000005057 refrigeration Methods 0.000 description 3
- OHMHBGPWCHTMQE-UHFFFAOYSA-N 2,2-dichloro-1,1,1-trifluoroethane Chemical compound FC(F)(F)C(Cl)Cl OHMHBGPWCHTMQE-UHFFFAOYSA-N 0.000 description 2
- QGZKDVFQNNGYKY-UHFFFAOYSA-N Ammonia Chemical compound N QGZKDVFQNNGYKY-UHFFFAOYSA-N 0.000 description 2
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 2
- ATUOYWHBWRKTHZ-UHFFFAOYSA-N Propane Chemical compound CCC ATUOYWHBWRKTHZ-UHFFFAOYSA-N 0.000 description 2
- 239000002826 coolant Substances 0.000 description 2
- RWRIWBAIICGTTQ-UHFFFAOYSA-N difluoromethane Chemical compound FCF RWRIWBAIICGTTQ-UHFFFAOYSA-N 0.000 description 2
- 238000002474 experimental method Methods 0.000 description 2
- 238000002309 gasification Methods 0.000 description 2
- 230000006872 improvement Effects 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- NNPPMTNAJDCUHE-UHFFFAOYSA-N isobutane Chemical compound CC(C)C NNPPMTNAJDCUHE-UHFFFAOYSA-N 0.000 description 2
- 238000004781 supercooling Methods 0.000 description 2
- UJPMYEOUBPIPHQ-UHFFFAOYSA-N 1,1,1-trifluoroethane Chemical group CC(F)(F)F UJPMYEOUBPIPHQ-UHFFFAOYSA-N 0.000 description 1
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 1
- 206010037660 Pyrexia Diseases 0.000 description 1
- 229910000831 Steel Inorganic materials 0.000 description 1
- BZHJMEDXRYGGRV-UHFFFAOYSA-N Vinyl chloride Chemical compound ClC=C BZHJMEDXRYGGRV-UHFFFAOYSA-N 0.000 description 1
- 229910021529 ammonia Inorganic materials 0.000 description 1
- 238000009835 boiling Methods 0.000 description 1
- 239000012267 brine Substances 0.000 description 1
- 229910002092 carbon dioxide Inorganic materials 0.000 description 1
- 239000001569 carbon dioxide Substances 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 229910052802 copper Inorganic materials 0.000 description 1
- 239000010949 copper Substances 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 239000008236 heating water Substances 0.000 description 1
- 239000001282 iso-butane Substances 0.000 description 1
- 239000007791 liquid phase Substances 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012544 monitoring process Methods 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 239000001294 propane Substances 0.000 description 1
- 238000010079 rubber tapping Methods 0.000 description 1
- HPALAKNZSZLMCH-UHFFFAOYSA-M sodium;chloride;hydrate Chemical compound O.[Na+].[Cl-] HPALAKNZSZLMCH-UHFFFAOYSA-M 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 238000010792 warming Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H9/00—Details
- F24H9/20—Arrangement or mounting of control or safety devices
- F24H9/2007—Arrangement or mounting of control or safety devices for water heaters
-
- 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
-
- 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
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H15/00—Control of fluid heaters
- F24H15/30—Control of fluid heaters characterised by control outputs; characterised by the components to be controlled
- F24H15/375—Control of heat pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H15/00—Control of fluid heaters
- F24H15/30—Control of fluid heaters characterised by control outputs; characterised by the components to be controlled
- F24H15/375—Control of heat pumps
- F24H15/38—Control of compressors of heat pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H4/00—Fluid heaters characterised by the use of heat pumps
- F24H4/02—Water heaters
- F24H4/04—Storage heaters
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
- F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
-
- 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
-
- 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
- F25B49/022—Compressor control arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H15/00—Control of fluid heaters
- F24H15/20—Control of fluid heaters characterised by control inputs
- F24H15/242—Pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H15/00—Control of fluid heaters
- F24H15/40—Control of fluid heaters characterised by the type of controllers
- F24H15/414—Control of fluid heaters characterised by the type of controllers using electronic processing, e.g. computer-based
- F24H15/421—Control of fluid heaters characterised by the type of controllers using electronic processing, e.g. computer-based using pre-stored data
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H15/00—Control of fluid heaters
- F24H15/40—Control of fluid heaters characterised by the type of controllers
- F24H15/414—Control of fluid heaters characterised by the type of controllers using electronic processing, e.g. computer-based
- F24H15/45—Control of fluid heaters characterised by the type of controllers using electronic processing, e.g. computer-based remotely accessible
-
- 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
- F25B2313/003—Indoor unit with water as a heat sink or heat source
-
- 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
-
- 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
-
- 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
- F25B2313/0315—Temperature sensors near the outdoor heat exchanger
-
- 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
-
- 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
-
- 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
- F25B2700/1933—Suction pressures
-
- 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
- F25B2700/21—Temperatures
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
-
- 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
- F25B2700/21—Temperatures
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
Definitions
- the present invention relates to an air-conditioning and hot-water supply complex system that is equipped with a heat pump cycle and performs a heating operation and a hot-water supply operation.
- Patent Document 1 discloses a heat source unit in which a compressor and a heat source side heat exchanger are mounted, an indoor unit in which an indoor side heat exchanger and an indoor expansion device are mounted, a hot water supply side heat exchanger, and a hot water supply side.
- An air-conditioning and hot-water supply combined system including a hot-water supply unit equipped with a throttle device has been proposed.
- the hot water supply unit preheats the water in the tank with the excess heat from the heating operation, thereby reducing the fuel cost of the gas boiler It is used as hot water preheating for the purpose of making it. Therefore, although the heating operation and the hot water supply operation can be performed simultaneously, the refrigerant control of the heat source unit is specialized for the air conditioning application. Therefore, in a conventional air-conditioning and hot-water supply complex system, when a hot water supply unit is handled as a hot water heater, the temperature control of the hot water at low temperatures is not stable, and the efficiency at high temperatures (COP: Coefficient Of Performance) deteriorates. .
- COP Coefficient Of Performance
- the present invention has been made to solve the above-described problems, and an object of the present invention is to provide an air-conditioning and hot water supply combined system that realizes stable hot water temperature control and improvement of COP in a hot water supply unit.
- the combined air conditioning and hot water supply system is a heat source unit in which a compressor and a heat source side heat exchanger are mounted, and an indoor unit that is connected to the heat source unit and in which an indoor heat exchanger and an indoor expansion device are mounted.
- a hot water supply unit connected to the indoor unit that performs the heating operation, the hot water supply side heat exchanger and the hot water supply side expansion device, and a control that controls the heat source unit.
- a control unit that switches the control mode to a hot water supply control mode mainly for hot water supply operation or a hot water supply preheating mode mainly for heating operation, and sets a target condensing temperature according to the control mode.
- a condensing temperature control unit, and the condensing temperature control unit has a target according to the temperature of the heat medium exchanged by the hot water supply unit in the hot water supply control mode. It is to set the condensation temperature.
- the hot water supply control mode by setting the target condensing temperature according to the temperature of the heat medium exchanged by the hot water supply unit, stable hot water temperature control and improvement of COP in the hot water supply unit Can be realized.
- FIG. 1 is a refrigerant circuit diagram illustrating a refrigerant circuit configuration of an air-conditioning and hot water supply complex system 10 according to Embodiment 1 of the present invention.
- the combined air conditioning and hot water supply system 10 according to the present embodiment is installed in a building, a condominium, a hotel, or the like, and uses an air pump load (heating load and cooling load) and hot water supply load (refrigeration cycle) that circulates refrigerant. Heating load and cooling load) can be supplied simultaneously.
- the air conditioning and hot water supply combined system 10 includes a heat source unit 110, an indoor unit 210, and a hot water supply unit 310.
- the indoor unit 210 and the hot water supply unit 310 are connected to the heat source unit 110 in parallel.
- the heat source unit 110 and the indoor unit 210 are connected by a liquid main pipe 1, a liquid branch pipe 4a, a gas branch pipe 3a, and a gas main pipe 2 which are refrigerant pipes.
- the heat source unit 110 and the hot water supply unit 310 are connected by a liquid main pipe 1, a liquid branch pipe 4 b, a gas branch pipe 3 b and a gas main pipe 2 which are refrigerant pipes.
- a heat medium circuit 400 is connected to the hot water supply unit 310 by a heat medium pipe 411 and a heat medium pipe 412.
- the air conditioning and hot water supply complex system 10 can be configured by connecting two or more heat source units 110, two or more indoor units 210, or two or more hot water supply units 310.
- the heat source unit 110 has a function of supplying hot or cold heat to the indoor unit 210 and the hot water supply unit 310.
- a compressor 111 In the heat source unit 110, a compressor 111, a flow path switching device 112, a heat source side heat exchanger 113, and an accumulator 115 are connected in series and mounted. Further, the heat source unit 110 is provided with a blower 114 for supplying air to the heat source side heat exchanger 113 in the vicinity of the heat source side heat exchanger 113. Further, a pressure sensor 116 for detecting the refrigerant discharge pressure is connected to the discharge side of the compressor 111.
- Compressor 111 sucks refrigerant and compresses it into a high temperature and high pressure state.
- the compressor 111 is not particularly limited as long as it can compress the sucked refrigerant into a high-pressure state.
- the compressor 111 can be configured using various types such as reciprocating, rotary, scroll, or screw.
- the compressor 111 is variably controlled by a control device 120 (FIG. 2) described later.
- the flow path switching device 112 switches the flow of the refrigerant according to a required operation mode (cooling or heating), and is configured by, for example, a four-way valve.
- the heat source side heat exchanger 113 functions as a radiator (condenser) during the cooling cycle, and functions as an evaporator during the heating cycle, and performs heat exchange between the air supplied from the blower 114 and the refrigerant to condense or liquefy the refrigerant. Evaporative gasification.
- the blower 114 includes a centrifugal fan or a multiblade fan driven by a motor (not shown). The amount of air blown from the blower 114 is adjusted by the control device 120.
- the accumulator 115 is disposed on the suction side of the compressor 111.
- refrigerant remains in the heating operation. Therefore, surplus refrigerant is stored in the accumulator 115.
- the accumulator 115 may be any container that can store excess refrigerant.
- the indoor unit 210 has a function of receiving heating or cooling supply from the heat source unit 110 and taking charge of heating load or cooling load.
- the indoor unit 210 includes an indoor expansion device 212 and an indoor heat exchanger 211 connected in series.
- a gas pipe temperature sensor 213G is disposed in the gas branch pipe 3a of the indoor unit 210.
- a liquid pipe temperature sensor 213L is disposed between the indoor side expansion device 212 of the liquid branch pipe 4a and the indoor side heat exchanger 211.
- a blower 214 for supplying air to the indoor heat exchanger 211 is disposed in the vicinity of the indoor heat exchanger 211.
- the indoor heat exchanger 211 functions as a radiator (condenser) during the heating cycle and as an evaporator during the cooling cycle, and performs heat exchange between the air supplied from the blower 214 and the refrigerant to condense or liquefy the refrigerant. Evaporative gasification.
- the indoor expansion device 212 has a function as a pressure reducing valve or an expansion valve, and expands the refrigerant by reducing the pressure.
- the indoor side expansion device 212 is composed of, for example, an electronic expansion valve capable of precise flow rate control or an inexpensive capillary tube, and the opening degree (throttle) is variably controlled by a control device 220 (FIG. 2) described later.
- the gas pipe temperature sensor 213G detects the temperature of the refrigerant flowing through the gas branch pipe 3a
- the liquid pipe temperature sensor 213L detects the temperature of the refrigerant flowing through the liquid branch pipe 4a.
- the temperature information detected by the gas pipe temperature sensor 213G and the liquid pipe temperature sensor 213L is output to the control device 220.
- the hot water supply unit 310 has a function of supplying hot or cold heat from the heat source unit 110 to the heat medium circuit 400 via the hot water supply side heat exchanger 311.
- a hot water supply side expansion device 312 and a hot water supply side heat exchanger (refrigerant-heat medium heat exchanger) 311 are mounted in series in the hot water supply unit 310.
- a gas pipe temperature sensor 313G is disposed in the gas branch pipe 3b of the hot water supply unit 310.
- a liquid pipe temperature sensor 313L is disposed between the hot water supply side expansion device 312 and the hot water supply side heat exchanger 311 of the liquid branch pipe 4b.
- an inlet temperature sensor 314 is disposed in the heat medium pipe 412, and an outlet temperature sensor 315 is disposed in the heat medium pipe 412.
- the hot water supply side heat exchanger 311 functions as a radiator (condenser) during the heating (heating) cycle and as an evaporator during the cooling (cooling) cycle, and exchanges heat between the heat medium flowing through the heat medium circuit 400 and the refrigerant. Is what you do.
- the hot water supply side throttle device 312 has a function as a pressure reducing valve or an expansion valve, and expands the refrigerant by reducing the pressure.
- the hot water supply side throttling device 312 is composed of, for example, an electronic expansion valve capable of precise flow rate control, an inexpensive capillary tube, or the like, and the opening degree (throttle) is variably controlled by a control device 320 (FIG. 2) described later. .
- the gas pipe temperature sensor 313G detects the temperature of the refrigerant flowing through the gas branch pipe 3b
- the liquid pipe temperature sensor 313L detects the temperature of the refrigerant flowing through the liquid branch pipe 4b.
- the temperature information detected by the gas pipe temperature sensor 313G and the liquid pipe temperature sensor 313L is output to the control device 320.
- the inlet temperature sensor 314 detects the temperature of the heat medium at the inlet of the hot water supply unit 310
- the outlet temperature sensor 315 detects the temperature of the heat medium at the outlet.
- the temperature information detected by the inlet temperature sensor 314 and the outlet temperature sensor 315 is output to the control device 320.
- the heat medium circuit 400 includes a pump 415 and a hot water storage tank 420.
- the heat medium circuit 400 includes a heat medium pipe 411, a hot water supply side heat exchanger 311, a heat medium pipe 412, a heat medium-water heat exchanger 413 in the hot water storage tank 420, a heat medium pipe 414, and a pump 415 connected in series. Composed.
- the heat medium heated or cooled by the hot water supply side heat exchanger 311 is circulated by the pump 415, thereby realizing the use of hot water or cold water.
- the hot water storage tank 420 is connected to a water pipe 421 that is a water supply pipe (or return pipe) and a water pipe 422 for supplying heated hot water, and is supplied to the load side using a pump (not shown).
- the hot water storage tank 420 is provided with a water temperature sensor 423 that detects the water temperature in the tank.
- the installation position of the water temperature sensor 423 may be anywhere, and may be determined appropriately according to the application.
- the heat medium pipe constituting the heat medium circuit 400 may be constituted by a copper pipe, a stainless pipe, a steel pipe, a vinyl chloride pipe, or the like. Further, water is used as the heat medium circulating through the heat medium circuit 400, but the heat medium is not limited to water, and an antifreeze liquid or the like may be used. Further, when there is a possibility that the heat medium pipe 411 and the heat medium pipe 412 are frozen in an environment where the water temperature is low, an antifreeze (brine) may be added to the water.
- the antifreeze is not particularly limited in kind or concentration, and may be selected according to availability or use such as ethylene glycol and propylene glycol.
- the refrigerant that can be used in the refrigeration cycle of the air conditioning and hot water supply complex system 10 includes a non-azeotropic refrigerant mixture, a pseudo-azeotropic refrigerant mixture, a single refrigerant, and the like.
- Non-azeotropic refrigerant mixture includes R407C (R32 / R125 / R134a) which is an HFC (hydrofluorocarbon) refrigerant. Since this non-azeotropic refrigerant mixture is a mixture of refrigerants having different boiling points, it has a characteristic that the composition ratio of the liquid-phase refrigerant and the gas-phase refrigerant is different.
- the pseudo azeotropic refrigerant mixture includes R410A (R32 / R125), R404A (R125 / R143a / R134a), which are HFC refrigerants, and the like.
- This pseudo azeotrope refrigerant has the same characteristic as that of the non-azeotrope refrigerant and has an operating pressure of about 1.6 times that of R22.
- the single refrigerant includes R22 which is an HCFC (hydrochlorofluorocarbon) refrigerant, R134a which is an HFC refrigerant, and the like. Since this single refrigerant is not a mixture, it has the property of being easy to handle. In addition, carbon dioxide or propane, isobutane, ammonia, etc., which are natural refrigerants, can also be used.
- R22 represents chlorodifluoromethane
- R32 represents difluoromethane
- R125 represents pentafluoromethane
- R134a represents 1,1,1,2-tetrafluoromethane
- R143a represents 1,1,1-trifluoroethane. ing. Therefore, it is good to use the refrigerant
- FIG. 2 is a control block diagram of the combined air-conditioning and hot water supply system 10 in the present embodiment.
- the heat source unit 110, the indoor unit 210, and the hot water supply unit 310 of the present embodiment include a control device 120, a control device 220, and a control device 320, respectively.
- the control device 120, the control device 220, and the control device 320 are each configured by a microcomputer, a DSP (Digital Signal Processor), or the like.
- DSP Digital Signal Processor
- the control device 120 of the heat source unit 110 includes a control unit 121, a communication unit 122, and a storage unit 123.
- the control unit 121 has a function of controlling the refrigerant pressure state and the refrigerant temperature state in the air conditioning and hot water supply complex system 10. Specifically, in the case of heating and heating operation, the control unit 121 controls the refrigerant circulation amount of the compressor 111 by an inverter (not shown) so as to converge to the target condensation temperature CTm, and also sets the target evaporation temperature ETm.
- the heat exchange capacity control is performed by changing the rotational speed of the blower 114 by means of an inverter (not shown) so as to converge.
- the refrigerant circulation amount control of the compressor 111 by the inverter is converged so as to converge to the target evaporation temperature ETm, and the rotation speed of the blower 114 due to the inverter is varied so as to converge to the target condensation temperature CTm.
- the heat exchange capacity is controlled.
- the control unit 121 performs switching control of the flow path switching device 112 in order to switch between heating (heating) and cooling (cooling).
- the control unit 121 The on / off valve is controlled to change the heat exchange area of the heat source side heat exchanger 113.
- control unit 121 of the present embodiment has a mode switching unit 124 and a condensation temperature control unit 125.
- the mode switching unit 124 switches the control mode of the heat source unit 110 in accordance with the operating state of the air conditioning and hot water supply complex system 10 and the temperature of the heat medium exchanged with the hot water supply unit 310.
- a “hot water supply preheating mode” mainly including heating operation by the indoor unit 210
- a “hot water supply control mode” mainly including hot water supply operation by the hot water supply unit 310 are used.
- the condensing temperature control unit 125 sets the target condensing temperature CTm in the refrigeration cycle according to the control mode of the heat source unit 110, and controls the compressor 111.
- the mode switching unit 124 and the condensing temperature control unit 125 are realized by a functional block realized by executing a program, or realized by an electronic circuit such as ASIC (Application Specific IC).
- the communication unit 122 performs wireless or wired communication with each unit of the heat source unit 110 connected to the control device 120, the control device 220 of the indoor unit 210, and the control device 320 of the hot water supply unit 310, and transmits and receives information.
- the storage unit 123 stores various information used for control of the control unit 121.
- the storage unit 123 stores, for example, a target condensation temperature CTm and a target evaporation temperature ETm, a first threshold value A, a second threshold value B, and a constant ⁇ that will be described later.
- the control device 220 of the indoor unit 210 includes a control unit 221, a communication unit 222, and a storage unit 223. Based on the information output from the gas pipe temperature sensor 213G and the liquid pipe temperature sensor 213L, the control unit 221 determines the degree of superheat during the cooling operation of the indoor unit 210 and the degree of supercooling during the heating operation of the indoor unit 210. It has a function to control. Specifically, the control device 220 determines the control amount of the indoor expansion device 212 and controls the refrigerant flow rate of the indoor expansion device 212.
- the control unit 221 is controlled to change the heat exchange area of the indoor heat exchanger 211.
- the communication unit 222 performs wireless or wired communication with each unit of the indoor unit 210 connected to the control device 220, the control device 120 of the heat source unit 110, and the control device 320 of the hot water supply unit 310, and transmits and receives information.
- the storage unit 223 stores various information used for control of the control unit 221.
- the control device 320 of the hot water supply unit 310 includes a control unit 321, a communication unit 322, and a storage unit 323. Based on information output from the gas pipe temperature sensor 313G, the liquid pipe temperature sensor 313L, the inlet temperature sensor 314, and the outlet temperature sensor 315, the control unit 321 determines the degree of superheat during the cooling operation of the hot water supply unit 310 and the heating of the hot water supply unit 310. It has a function of controlling the degree of supercooling during operation and the temperature of tapping water. Specifically, the control amount of the hot water supply side expansion device 312 is determined by the control device 320, and the refrigerant flow rate control of the hot water supply side expansion device 312 is performed.
- the control unit 321 The open / close valve is controlled to change the heat exchange area of the hot water supply side heat exchanger 311.
- the communication unit 322 performs wireless or wired communication with each unit of the hot water supply unit 310 connected to the control device 320, the control device 120 of the heat source unit 110, and the control device 220 of the indoor unit 210, and transmits and receives information.
- the storage unit 323 stores various types of information used for the control of the control unit 321.
- the heat source unit 110, the indoor unit 210, and the hot water supply unit 310 are individually provided with a control device and transmit information to each other to perform cooperation processing. It is good also as a structure provided with one control apparatus to control.
- the air-conditioning and hot water supply combined system 10 includes a sensor for detecting the refrigerant suction pressure, a sensor for detecting the refrigerant discharge temperature, a sensor for detecting the refrigerant suction temperature, and a heat source.
- a sensor for detecting the air temperature may be provided.
- Information (measurement information such as temperature information and pressure information) detected by these various sensors is transmitted to the control devices of the heat source unit 110, the indoor unit 210, and the hot water supply unit 310, and each actuator (ie, the compressor 111, the flow information). Used for controlling the path switching device 112, the blower 114, the indoor side expansion device 212, the hot water supply side expansion device 312 and the like.
- the operation of the air conditioning and hot water supply complex system 10 will be described.
- heating operation, cooling operation, heating operation, and cooling operation are possible.
- simultaneous operation of heating operation and heating operation, and simultaneous operation of cooling operation and cooling operation are possible.
- the flow path switching device 112 is switched to the dotted line side in FIG. 1, and in the cooling operation and the cooling operation, the flow path switching device 112 is switched to the solid line side in FIG.
- the switching between the air conditioning operation (heating or cooling) and the hot water supply operation (heating or cooling) is performed by fully closing either the indoor side expansion device 212 or the hot water supply side expansion device 312.
- the air conditioning and hot water supply complex system 10 of the present embodiment is a system in which the hot water supply unit 310 and the indoor unit 210 are connected to a single refrigerant system (heat source unit 110).
- a high temperature and high pressure refrigerant from the compressor 111 is supplied to the hot water supply unit 310 side to boil water in the hot water storage tank 420 (a hot water supply operation), and a high temperature and high pressure refrigerant from the compressor 111.
- the heating operation is performed for 1 to 2 hours corresponding to midnight or midnight
- the air conditioning operation is performed from morning to midnight.
- the boiled hot water is stored in a tank and used over a day.
- the high-pressure gas refrigerant heated and compressed by the compressor 111 is conveyed to the indoor unit 210 through the flow path switching device 112, the gas main pipe 2, and the gas branch pipe 3a.
- the refrigerant conveyed to the indoor unit 210 changes into high-pressure liquid refrigerant by the condensation action by radiating heat to the indoor air in the indoor heat exchanger 211.
- the high-pressure liquid refrigerant is changed into a low-pressure two-phase refrigerant (a refrigerant mixed with liquid and gas) by an expansion action in the indoor expansion device 212 on the secondary side of the indoor heat exchanger 211.
- the low-pressure two-phase refrigerant is conveyed to the heat source side heat exchanger 113 in the heat source unit 110 via the liquid branch pipe 4 a and the liquid main pipe 1. And it changes to a low-pressure gas refrigerant by transferring heat from the air in the heat source side heat exchanger 113.
- the low-pressure gas refrigerant passes through the flow path switching device 112 and the accumulator 115, is sucked in by the compressor 111, and is heated and compressed again.
- the high-pressure gas refrigerant heated and compressed by the compressor 111 is conveyed to the hot water supply unit 310 via the flow path switching device 112, the gas main pipe 2, and the gas branch pipe 3b.
- the refrigerant conveyed to the hot water supply unit 310 changes into high-pressure liquid refrigerant by the condensation action by radiating heat to the heat medium of the heat medium circuit 400 in the hot water supply side heat exchanger 311.
- the high-pressure liquid refrigerant is changed into a low-pressure two-phase refrigerant by the expansion action in the hot water supply side expansion device 312 on the secondary side of the hot water supply side heat exchanger 311.
- the low-pressure two-phase refrigerant is conveyed to the heat source side heat exchanger 113 in the heat source unit 110 via the liquid branch pipe 4 b and the liquid main pipe 1.
- the subsequent movements are the same as in the heating operation.
- the high-pressure gas refrigerant heated and compressed by the compressor 111 is transferred to the heat source side heat exchanger 113 in the heat source unit 110 through the flow path switching device 112.
- the high-pressure gas refrigerant is condensed and changed into a high-pressure liquid refrigerant.
- the high-pressure liquid refrigerant is conveyed to the indoor unit 210 through the liquid main pipe 1 and the liquid branch pipe 4a.
- the high-pressure liquid refrigerant conveyed to the indoor unit 210 changes into a low-pressure two-phase refrigerant by the expansion action in the indoor expansion device 212 and is conveyed to the indoor heat exchanger 211.
- the indoor heat exchanger 211 changes into a low-pressure gas refrigerant by transferring heat from the air. At this time, the air is cooled by removing heat.
- the low-pressure gas refrigerant exiting the indoor unit 210 is transported to the heat source unit 110 via the gas branch pipe 3a and the gas main pipe 2.
- the low-pressure gas refrigerant that has flowed into the heat source unit 110 is sucked into the compressor 111 via the flow path switching device 112 and the accumulator 115, and is heated and compressed again.
- the high-pressure gas refrigerant heated and compressed by the compressor 111 is transferred to the heat source side heat exchanger 113 in the heat source unit 110 via the flow path switching device 112 as in the cooling operation.
- the refrigerant changes to a high-pressure liquid refrigerant, and is conveyed to the hot water supply unit 310 through the liquid main pipe 1 and the liquid branch pipe 4b.
- the refrigerant conveyed to the hot water supply unit 310 is expanded by the hot water supply side expansion device 312 to change the high pressure liquid refrigerant into a low pressure two-phase refrigerant, and the hot water supply side heat exchanger 311 receives heat from the heat medium.
- the heat medium is cooled by removing heat.
- the low-pressure gas refrigerant exiting the hot water supply unit 310 is conveyed to the heat source unit 110 via the gas branch pipe 3b and the gas main pipe 2. Subsequent movement is the same as in the cooling operation.
- the high-pressure gas refrigerant heated and compressed by the compressor 111 is divided into the gas branch pipe 3a and the gas branch pipe 3b through the flow path switching device 112 and the gas main pipe 2. . Then, the refrigerant passes through the indoor heat exchanger 211 and the indoor expansion device 212 of the indoor unit 210, and the hot water supply heat exchanger 311 and the hot water supply expansion device 312 of the hot water supply unit 310, respectively. Heat exchange, heating and hot water supply. Thereafter, the refrigerant flows into the liquid branch pipe 4a and the liquid branch pipe 4b, joins in the liquid main pipe 1, and then goes to the heat source side heat exchanger 113. The subsequent movement is the same as in the heating operation and the heating operation.
- a constant target condensing temperature CTm for exerting a heating capability in the indoor unit 210. Is set. And each refrigerant
- the hot water supply unit 310 wants to perform a movement like a circulating warming type hot water heater, if the control is performed so that the target condensation temperature CTm is constant according to the indoor unit 210, the stability of the control at the time of low water temperature is reduced. Decrease and deterioration of COP at high water temperature.
- FIG. 3A is a diagram showing the relationship between the target condensation temperature CTm and the heat medium temperature WT in the conventional technique (when the target condensation temperature CTm is constant), and FIG. 3B shows the transition of COP.
- FIG. 3A the vertical axis indicates temperature and the horizontal axis indicates time, and in FIG. 3B, the vertical axis indicates COP and the horizontal axis indicates time.
- the heat medium temperature WT is the temperature of the heat medium that exchanges heat in the hot water supply unit 310, for example, the temperature detected by the inlet temperature sensor 314 of the hot water supply unit 310.
- the temperature difference DT between the constant target condensation temperature CTm and the heat medium temperature WT is small.
- the temperature difference DT becomes small in this way, the heating capability cannot be obtained for the power of the compressor 111, and the COP deteriorates as shown in FIG.
- the heat medium temperature WT when the heat medium temperature WT is low, the temperature difference DT between the target condensation temperature CTm and the heat medium temperature WT becomes large. Thereby, the heating capability with respect to the power of the compressor 111 is increased, and the COP is increased.
- the load required for the hot water supply unit 310 is small (for example, in the case of floor heating (25 ° C. to 30 ° C.))
- the capacity control of the compressor 111 cannot be performed.
- the heat medium temperature WT immediately reaches the set temperature, the hot water supply unit 310 (for example, the pump 415) repeatedly starts and stops, and the hot water temperature control at low temperatures becomes unstable.
- the refrigerant pipe length is short or long depending on the local installation contractor, so the time constant from the start to the stable transition is larger than that of the room air conditioner or chiller. Therefore, for example, in a system that becomes stable in 30 minutes after startup, if the required hot water supply load is satisfied within 15 minutes and the hot water supply unit 310 is stopped, the COP can be exhibited only by about 50%.
- target condensation is performed according to heat medium temperature WT of hot water supply unit 310.
- a “hot water supply control mode” for changing the temperature CTm and a “hot water preheating mode” for maintaining the target condensation temperature CTm constant are provided.
- the “hot water supply control mode” and the “hot water supply preheating mode” are automatically switched by the mode switching unit 124 of the control device 120. Specifically, mode switching unit 124 sets the hot water supply preheating mode during the heating operation, and sets the hot water supply control mode during the heating operation. Furthermore, in the case of simultaneous operation of heating and heating, the hot water supply control mode or the hot water supply preheating mode is set according to the heat medium temperature WT.
- FIG. 4A is a diagram showing the relationship between the target condensation temperature CTm and the heat medium temperature WT in the hot water supply control mode
- FIG. 4B is a diagram showing the transition of COP.
- the condensing temperature control unit 125 of the control device 120 sets the target condensing temperature CTm variably according to the heat medium temperature WT.
- the target condensation temperature CTm is set using the following formula (1).
- the compressor 111 is controlled so that the refrigerant condensation temperature CT of the hot water supply unit 310 (and the indoor unit 210) matches the target condensation temperature CTm.
- the value of the inlet temperature sensor 314 received from the hot water supply unit 310 is used as the heat medium temperature WT.
- the value of the outlet temperature sensor 315, the average temperature of the value of the inlet temperature sensor 314 and the value of the outlet temperature sensor 315, or the value of the water temperature sensor 423 in the hot water storage tank 420 may be used.
- the constant ⁇ is a value that can be arbitrarily determined, but an experiment or the like is performed so that the temperature difference DT between the heat medium temperature WT and the target condensing temperature CTm is the most efficient value so that deterioration of COP can be avoided. Determined by.
- the temperature difference DT from the heat medium temperature WT can be made constant. Therefore, as shown in FIG. 4A, the temperature difference DT at the low temperature is smaller than that shown in FIG. Thereby, the frequency of starting and stopping of hot water supply unit 310 can be reduced, and stable control is possible. Further, the temperature difference DT at the time of high temperature becomes larger than that shown in FIG. 3A, and it is possible to ensure the heating capacity. Thereby, as shown in FIG.4 (b), the deterioration of COP can be suppressed compared with the case where target condensation temperature CTm is made constant (FIG.3 (b)).
- the indoor unit 210 and the hot water supply unit 310 are simultaneously operated and the indoor load is high. In some cases, hot water cannot be supplied to the hot water supply unit 310. In this case, the indoor unit 210 may be stopped as necessary while observing the temperature difference between the refrigerant condensation temperature CT and the indoor temperature sensor of the indoor unit 210.
- the condensing temperature control unit 125 sets a certain target condensing temperature CTm necessary for performing heating as shown in FIG.
- FIG. 5 is a flowchart showing the mode switching process executed by the mode switching unit 124 of the present embodiment.
- the control mode is arbitrarily set to either the “hot water supply control mode” or the “hot water supply preheating mode” as the initial mode.
- the first threshold value A and the second threshold value B are acquired from the storage unit 123 (S1).
- the first threshold value A and the second threshold value B are temperatures for comparison with the heat medium temperature WT, and a temperature suitable for switching the control mode is obtained in advance by experiments or the like and stored in the storage unit 123.
- the first threshold value A and the second threshold value B have a relationship of B> A.
- hot water supply unit 310 is in operation (S2).
- the control mode is set to "hot water preheating mode" (S7).
- hot water supply unit 310 is in operation (S2: YES)
- indoor unit 210 is in operation (S3). If the air conditioning and hot water supply complex system 10 includes a plurality of hot water supply units 310, it is determined in S2 whether or not there are one or more hot water supply units 310 in operation. If there are one or more hot water supply units 310 being operated (S2: YES), the process proceeds to S3, and if there is no hot water supply unit 310 being operated (S2: NO), the process proceeds to S7.
- the indoor unit 210 when the indoor unit 210 is in operation (S3: YES), the heat medium temperature WT is acquired from the hot water supply unit 310 (S4).
- the control mode is set to the “hot water supply control mode” (S8).
- Heat medium temperature WT is the value of inlet temperature sensor 314 received from hot water supply unit 310.
- the air conditioning and hot water supply complex system 10 includes a plurality of hot water supply units 310, the average value of the heat medium temperature WT of the representative hot water supply unit 310 or the heat medium temperature WT of the plurality of hot water supply units 310 is acquired.
- the control mode is set to the “hot water preheating mode” (S7).
- the control mode is set to “hot water supply control mode” (S8).
- the current control mode is maintained (S9).
- the control mode is maintained even if the heat medium temperature WT varies.
- a condensation temperature control process according to the set control mode is performed (S10), and it is determined whether or not to stop the heat source unit 110 (S11). Specifically, when an instruction to thermo-off or stop operation of the heat source unit 110 is given, it is determined that the heat source unit 110 is stopped. And when not stopping the heat source unit 110 (S11: NO), it returns to S3.
- the processes from S3 to S11 are sequentially performed at arbitrarily set control time intervals until the heat source unit 110 is stopped (S11: YES).
- FIG. 6 is a flowchart showing a condensation temperature control process executed by the condensation temperature control unit 125 of the present embodiment.
- the currently set control mode is the “hot water supply control mode” (S21).
- the heat medium temperature WT is acquired from the hot water supply unit 310 (S22).
- the target condensing temperature CTm is set according to the acquired heat medium temperature WT (S23).
- a value obtained by adding a constant ⁇ to the acquired heat medium temperature WT is set as the target condensation temperature CTm.
- the currently set control mode is not the “hot water supply control mode” (S21: NO)
- it is determined that the current control mode is the “hot water supply preheating mode” and a constant target condensation temperature CTm is set ( S24).
- the target condensation temperature CTm stored in the storage unit 123 is used as the target condensation temperature CTm as it is.
- a difference DCT between the target condensation temperature CTm set in S23 or S24 and the refrigerant condensation temperature CT is calculated (S25).
- the difference DCT between the refrigerant condensation temperature CT of the hot water supply unit 310 and the target condensation temperature CTm set in S23 is calculated.
- the refrigerant of the indoor unit 210 is calculated.
- a difference DCT between the condensation temperature CT and the target condensation temperature CTm set in S24 is calculated.
- a capacity control value (for example, drive frequency) of the compressor 111 is determined according to the calculated difference DCT, and the compressor 111 is controlled so as to be the determined capacity value (S26).
- a hot water supply control mode for mainly hot water supply operation is provided, and the automatic switching is performed according to the operation state of the indoor unit 210 and the hot water supply unit 310 and the heat medium temperature WT. ing.
- the target condensing temperature CTm is variably set according to the heat medium temperature WT, so that the difference between the target condensing temperature CTm and the heat medium temperature WT is constant, stable control in the hot water supply unit 310 and COP deterioration can be suppressed.
- FIG. 7 is a control block diagram illustrating an electrical configuration of the air conditioning and hot water supply complex system 10A of the second embodiment.
- the air conditioning and hot water supply complex system 10 ⁇ / b> A according to the present embodiment is different from the first embodiment in that it includes an external communication device 50.
- the refrigerant circuit configuration and operation in the combined air conditioning and hot water supply system 10A of the second embodiment are the same as those of the first embodiment.
- the external communication device 50 is connected to the heat source unit 110, the indoor unit 210, and the hot water supply unit 310 so as to be capable of wired or wireless communication.
- the external communication device 50 includes a control unit 510, a communication unit 520, and a storage unit 530.
- the control unit 510 performs state monitoring and various operation controls of the heat source unit 110, the indoor unit 210, and the hot water supply unit 310.
- the communication unit 520 performs wireless or wired communication with the control devices of the heat source unit 110, the indoor unit 210, and the hot water supply unit 310, and transmits and receives information.
- the storage unit 530 stores various information used for control by the control unit 510.
- the mode switching unit 124 of the heat source unit 110 switches between the “hot water control mode” and the “hot water preheating mode” in accordance with the operating states of the indoor unit 210 and the hot water supply unit 310 and the heat medium temperature WT.
- a mode change signal instructing switching between the “hot-water supply control mode” and the “hot-water supply preheating mode” is transmitted from the external communication device 50 to the control device 120.
- FIG. 8 is a flowchart of the mode switching process in the present embodiment.
- the mode switching process in the present embodiment is executed by the mode switching unit 124 of the heat source unit 110 as in the first embodiment.
- the same reference numerals are given to the same processes as those in the first embodiment.
- the control mode is arbitrarily set to either the “hot water supply control mode” or the “hot water supply preheating mode” as the initial mode.
- this process it is determined whether a mode change signal is received from the external communication device 50 (S31).
- the mode change signal when the mode change signal is received (S31: YES), it is determined whether or not the content of the mode change signal indicates “hot water supply control mode” (S32). When the content of the mode change signal indicates “hot water supply control mode” (S32: YES), the control mode is set to “hot water supply control mode” (S34). On the other hand, when the content of the mode change signal does not indicate “hot water supply control mode” (S33: NO), it is determined that “hot water supply preheating mode” is specified, and the control mode is set to “hot water supply preheating mode”. (S33). If the mode change signal is not received from the external communication device 50 (S31: NO), the current control mode is maintained (S35).
- the condensation temperature control process according to control mode is performed (S10), and it is judged whether the heat source unit 110 is stopped (S11). And when not stopping the heat source unit 110 (S11: NO), it returns to S3.
- the processes from S3 to S11 are sequentially performed at arbitrarily set control time intervals until the heat source unit 110 is stopped (S11: YES).
- the control mode is switched based on the instruction from the external communication device 50.
- the user or administrator can switch the control mode arbitrarily by operating the external communication device 50.
- the mode switching unit 124 of the heat source unit 110 or the external communication device 50 is configured to switch between the “hot water supply control mode” and the “hot water supply preheating mode”, but the present invention is not limited to this. It is good also as a structure which provides the dip switch which switches a mode in the air-conditioning / hot-water supply complex system 10, and switches manually.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Signal Processing (AREA)
- Fuzzy Systems (AREA)
- Mathematical Physics (AREA)
- Heat-Pump Type And Storage Water Heaters (AREA)
- Air Conditioning Control Device (AREA)
- Central Heating Systems (AREA)
Abstract
Description
図1は、本発明の実施の形態1における空調給湯複合システム10の冷媒回路構成を示す冷媒回路図である。本実施の形態の空調給湯複合システム10は、ビル、マンションまたはホテル等に設置され、冷媒を循環させるヒートポンプサイクル(冷凍サイクル)を利用することで空調負荷(暖房負荷および冷房負荷)および給湯負荷(加熱負荷および冷却負荷)を同時に供給できるものである。
熱源ユニット110は、室内ユニット210および給湯ユニット310に温熱または冷熱を供給する機能を有している。熱源ユニット110には、圧縮機111と、流路切替装置112と、熱源側熱交換器113と、アキュムレーター115とが直列に接続されて搭載されている。また、熱源ユニット110には、熱源側熱交換器113に空気を供給するための送風機114が熱源側熱交換器113の近傍に配置されている。さらに、圧縮機111の吐出側には冷媒の吐出圧力を検知する圧力センサー116が接続されている。
室内ユニット210は、熱源ユニット110からの温熱または冷熱の供給を受けて暖房負荷または冷房負荷を担当する機能を有している。室内ユニット210には、室内側絞り装置212と、室内側熱交換器211とが直列に接続されて搭載されている。また、室内ユニット210のガス枝管3aには、ガス管温度センサー213Gが配置されている。さらに、液枝管4aの室内側絞り装置212と室内側熱交換器211との間には、液管温度センサー213Lが配置されている。さらに、室内側熱交換器211の近傍には、室内側熱交換器211に空気を供給するための送風機214が配置されている。
給湯ユニット310は、熱源ユニット110からの温熱または冷熱を、給湯側熱交換器311を介して熱媒体回路400に供給する機能を有している。給湯ユニット310には、給湯側絞り装置312と、給湯側熱交換器(冷媒-熱媒体熱交換器)311とが、直列に接続されて搭載されている。また、給湯ユニット310のガス枝管3bには、ガス管温度センサー313Gが配置されている。さらに、液枝管4bの給湯側絞り装置312と給湯側熱交換器311との間には、液管温度センサー313Lが配置されている。さらに、熱媒体配管412には入口温度センサー314が配置され、熱媒体配管412には出口温度センサー315が配置されている。
熱媒体回路400はポンプ415および貯湯タンク420を備えている。熱媒体回路400は、熱媒体配管411、給湯側熱交換器311、熱媒体配管412、貯湯タンク420内の熱媒体-水熱交換器413、熱媒体配管414およびポンプ415が直列に接続されて構成される。熱媒体回路400では、給湯側熱交換器311で加熱または冷却された熱媒体をポンプ415で循環させることで、給湯利用または冷水利用を実現している。また、貯湯タンク420には、給水管(または戻し管)である水配管421、および加熱された温水を供給するための水配管422が接続され、図示しないポンプ等を用いて負荷側へ供給される。また、貯湯タンク420には、タンク内の水温を検知する水温センサー423が配置されている。水温センサー423の設置位置はどこでもよく、用途に応じて適宜決めればよい。
暖房運転では、圧縮機111にて加熱圧縮された高圧のガス冷媒は流路切替装置112、ガス主管2、ガス枝管3aを経て、室内ユニット210へ搬送される。室内ユニット210に搬送された冷媒は、室内側熱交換器211において室内空気に熱を放熱することで、凝縮作用により高圧の液冷媒へと変化する。高圧の液冷媒は室内側熱交換器211の二次側にある室内側絞り装置212にて膨張作用により低圧の二相冷媒(液とガスが入り混じった冷媒)へと変化する。
加熱運転では、圧縮機111にて加熱圧縮された高圧のガス冷媒は流路切替装置112、ガス主管2、ガス枝管3bを経て、給湯ユニット310へ搬送される。給湯ユニット310に搬送された冷媒は、給湯側熱交換器311において熱媒体回路400の熱媒体に熱を放熱することで、凝縮作用により高圧の液冷媒へと変化する。高圧の液冷媒は給湯側熱交換器311の二次側にある給湯側絞り装置312にて膨張作用により低圧の二相冷媒へと変化する。低圧の二相冷媒は液枝管4bおよび液主管1を経由して、熱源ユニット110内の熱源側熱交換器113に搬送される。以降の動きは、暖房運転と同様である。
冷房運転では、圧縮機111にて加熱圧縮された高圧のガス冷媒は流路切替装置112を経て、熱源ユニット110内の熱源側熱交換器113に搬送される。熱源側熱交換器113において、熱を空気へ放出することで、高圧のガス冷媒は凝縮され、高圧の液冷媒へと変化する。高圧の液冷媒は液主管1および液枝管4aを経て、室内ユニット210へ搬送される。
冷却運転では、冷房運転時と同様に圧縮機111にて加熱圧縮された高圧のガス冷媒は流路切替装置112を経て、熱源ユニット110内の熱源側熱交換器113に搬送される。熱源側熱交換器113において、高圧の液冷媒へと変化し、液主管1および液枝管4bを経て、給湯ユニット310へ搬送される。給湯ユニット310に搬送された冷媒は、給湯側絞り装置312にて膨張作用により高圧の液冷媒は低圧の二相冷媒へと変化し、給湯側熱交換器311にて、熱媒体から熱を授受することで低圧のガス冷媒へと変化する。このとき熱媒体は熱が奪われることで冷却される。給湯ユニット310を出た低圧のガス冷媒は、ガス枝管3bおよびガス主管2を経て、熱源ユニット110へ搬送される。以降の動きは冷房運転と同様である。
暖房および加熱の同時運転では、圧縮機111にて加熱圧縮された高圧のガス冷媒は流路切替装置112、およびガス主管2を経て、ガス枝管3aおよびガス枝管3bのそれぞれに分流される。そして、冷媒は、室内ユニット210の室内側熱交換器211および室内側絞り装置212、ならびに給湯ユニット310の給湯側熱交換器311および給湯側絞り装置312をそれぞれ通過し、空気および熱媒体とそれぞれ熱交換を行い、暖房および給湯を行う。その後、冷媒は液枝管4aおよび液枝管4bに流入し、液主管1で合流した後、熱源側熱交換器113に向かう。以降の動きは、暖房運転および加熱運転と同様である。
目標凝縮温度CTm=熱媒体温度WT+α ・・・(1)
図5は、本実施の形態のモード切替部124によって実行されるモード切替処理を示すフローチャートである。本処理の開始時において、制御モードは、初期モードとして「給湯制御モード」または「給湯予熱モード」の何れかに任意に設定されている。そして、本処理が開始されると、第1の閾値Aおよび第2の閾値Bが記憶部123から取得される(S1)。第1の閾値Aおよび第2の閾値Bは、熱媒体温度WTと比較するための温度であり、制御モードの切り替えに適した温度が実験等によりあらかじめ求められ、記憶部123に記憶される。第1の閾値Aおよび第2の閾値Bは、B>Aの関係である。
続いて、S10の凝縮温度制御処理について説明する。図6は、本実施の形態の凝縮温度制御部125にて実行される凝縮温度制御処理を示すフローチャートである。本処理では、まず、現在設定されている制御モードが「給湯制御モード」であるか否かが判断される(S21)。現在設定されている制御モードが「給湯制御モード」である場合(S21:YES)、給湯ユニット310から熱媒体温度WTが取得される(S22)。そして、取得された熱媒体温度WTに応じて、目標凝縮温度CTmが設定される(S23)。ここでは、上記の式(1)に示すように、取得された熱媒体温度WTに定数αを加算した値が目標凝縮温度CTmとして設定される。
次に本発明の実施の形態2における空調給湯複合システム10Aについて説明する。図7は、実施の形態2の空調給湯複合システム10Aの電気的な構成を示す制御ブロック図である。図7に示すように、本実施の形態における空調給湯複合システム10Aは、外部通信機器50を備える点において、実施の形態1と相違する。実施の形態2の空調給湯複合システム10Aにおける冷媒回路構成および動作については、実施の形態1と同様である。
Claims (9)
- 圧縮機および熱源側熱交換器が搭載された熱源ユニットと、
前記熱源ユニットに接続され、室内側熱交換器および室内側絞り装置が搭載された室内ユニットであって、暖房運転を行う室内ユニットと、
前記熱源ユニットに接続され、給湯側熱交換器および給湯側絞り装置が搭載された給湯ユニットであって、給湯運転を行う給湯ユニットと、
前記熱源ユニットを制御する制御装置と、を備え、
前記制御装置は、
制御モードを、前記給湯運転を主とする給湯制御モードまたは前記暖房運転を主とする給湯予熱モードに切り替えるモード切替部と、
前記制御モードに応じて目標凝縮温度を設定する凝縮温度制御部と、を有し、
前記凝縮温度制御部は、前記給湯制御モードにおいて、前記給湯ユニットによって熱交換される熱媒体の温度に応じて前記目標凝縮温度を設定するものである空調給湯複合システム。 - 前記凝縮温度制御部は、前記給湯制御モードにおいて、前記熱媒体の温度に定数を加算した値を前記目標凝縮温度に設定するものである請求項1に記載の空調給湯複合システム。
- 前記凝縮温度制御部は、前記給湯予熱モードにおいて、前記目標凝縮温度を一定に設定するものである請求項1または2の何れか一項に記載の空調給湯複合システム。
- 前記凝縮温度制御部は、前記室内ユニットまたは前記給湯ユニットの冷媒凝縮温度が前記目標凝縮温度に収束するよう前記圧縮機を制御するものである請求項1~3の何れか一項に記載の空調給湯複合システム。
- 前記モード切替部は、前記室内ユニットおよび前記給湯ユニットの運転状態に応じて、前記給湯制御モードおよび前記給湯予熱モードを自動的に切り替えるものである請求項1~4の何れか一項に記載の空調給湯複合システム。
- 前記モード切替部は、前記室内ユニットが運転し、前記給湯ユニットが停止している場合に、前記給湯予熱モードに切り替え、前記給湯ユニットが運転し、前記室内ユニットが停止している場合に、前記給湯制御モードに切り替えるものである請求項5に記載の空調給湯複合システム。
- 前記モード切替部は、前記室内ユニットおよび前記給湯ユニットが同時に運転している場合、前記熱媒体の温度に応じて前記給湯制御モードおよび前記給湯予熱モードを自動的に切り替えるものである請求項5または6に記載の空調給湯複合システム。
- 前記モード切替部は、前記熱媒体の温度が、第1の閾値以上であって第2の閾値未満である場合に、前記給湯制御モードまたは前記給湯予熱モードを維持するものである請求項7に記載の空調給湯複合システム。
- 前記制御装置は、外部通信機器と通信可能な通信部をさらに有し、
前記モード切替部は、前記通信部を介して前記制御モードの変更を指示する信号を前記外部通信機器から受信した場合、前記制御モードを、前記受信した信号で指示された制御モードに切り替えるものである請求項1~8の何れか一項に記載の空調給湯複合システム。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US15/518,629 US10088198B2 (en) | 2014-11-27 | 2014-11-27 | Air-conditioning and hot water supplying composite system |
EP14907085.6A EP3236174B1 (en) | 2014-11-27 | 2014-11-27 | Combined air conditioning and hot-water supply system |
PCT/JP2014/081348 WO2016084186A1 (ja) | 2014-11-27 | 2014-11-27 | 空調給湯複合システム |
JP2016561158A JP6289668B2 (ja) | 2014-11-27 | 2014-11-27 | 空調給湯複合システム |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2014/081348 WO2016084186A1 (ja) | 2014-11-27 | 2014-11-27 | 空調給湯複合システム |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2016084186A1 true WO2016084186A1 (ja) | 2016-06-02 |
Family
ID=56073805
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2014/081348 WO2016084186A1 (ja) | 2014-11-27 | 2014-11-27 | 空調給湯複合システム |
Country Status (4)
Country | Link |
---|---|
US (1) | US10088198B2 (ja) |
EP (1) | EP3236174B1 (ja) |
JP (1) | JP6289668B2 (ja) |
WO (1) | WO2016084186A1 (ja) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2018100729A1 (ja) * | 2016-12-02 | 2018-06-07 | 三菱電機株式会社 | 冷凍サイクル装置 |
WO2018216112A1 (ja) * | 2017-05-23 | 2018-11-29 | 三菱電機株式会社 | 冷凍サイクル装置 |
EP3553435A4 (en) * | 2016-12-08 | 2020-08-19 | Kawasaki Jukogyo Kabushiki Kaisha | RAW MATERIAL GAS LIQUIDGE DEVICE AND CONTROL PROCEDURE FOR IT |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP6289734B2 (ja) * | 2015-03-16 | 2018-03-07 | 三菱電機株式会社 | 空調給湯複合システム |
ES2737673A1 (es) * | 2018-07-13 | 2020-01-15 | Robert Art En Pedra S L | Sistema para el control de la temperatura de al menos un módulo de almacenamiento energético y método asociado |
CN110657611A (zh) * | 2019-09-27 | 2020-01-07 | 广东芬尼克兹节能设备有限公司 | 一种热泵***的控制方法及热泵*** |
US11781760B2 (en) * | 2020-09-23 | 2023-10-10 | Rheem Manufacturing Company | Integrated space conditioning and water heating systems and methods thereto |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2005016947A (ja) * | 2000-06-21 | 2005-01-20 | Matsushita Electric Ind Co Ltd | ヒートポンプ給湯機 |
JP2013032883A (ja) * | 2011-08-02 | 2013-02-14 | Osaka Gas Co Ltd | ヒートポンプ給湯システム |
JP2013117373A (ja) * | 2013-03-18 | 2013-06-13 | Mitsubishi Electric Corp | 冷凍サイクル装置及び冷凍サイクル制御方法 |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2008232508A (ja) * | 2007-03-19 | 2008-10-02 | Mitsubishi Electric Corp | 給湯器 |
JP5042262B2 (ja) * | 2009-03-31 | 2012-10-03 | 三菱電機株式会社 | 空調給湯複合システム |
JP5634502B2 (ja) * | 2010-04-05 | 2014-12-03 | 三菱電機株式会社 | 空調給湯複合システム |
JP5414638B2 (ja) * | 2010-08-25 | 2014-02-12 | 日立アプライアンス株式会社 | 空気調和システム |
WO2012081052A1 (ja) * | 2010-12-15 | 2012-06-21 | 三菱電機株式会社 | 空調給湯複合システム |
EP2657628B1 (en) * | 2010-12-22 | 2023-07-05 | Mitsubishi Electric Corporation | Hot-water-supplying, air-conditioning composite device |
WO2013046269A1 (ja) | 2011-09-29 | 2013-04-04 | 三菱電機株式会社 | 空調給湯複合システム |
WO2013136368A1 (ja) * | 2012-03-15 | 2013-09-19 | 三菱電機株式会社 | 冷凍サイクル装置 |
WO2014106895A1 (ja) * | 2013-01-07 | 2014-07-10 | 三菱電機株式会社 | ヒートポンプシステム |
-
2014
- 2014-11-27 EP EP14907085.6A patent/EP3236174B1/en active Active
- 2014-11-27 US US15/518,629 patent/US10088198B2/en active Active
- 2014-11-27 WO PCT/JP2014/081348 patent/WO2016084186A1/ja active Application Filing
- 2014-11-27 JP JP2016561158A patent/JP6289668B2/ja active Active
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2005016947A (ja) * | 2000-06-21 | 2005-01-20 | Matsushita Electric Ind Co Ltd | ヒートポンプ給湯機 |
JP2013032883A (ja) * | 2011-08-02 | 2013-02-14 | Osaka Gas Co Ltd | ヒートポンプ給湯システム |
JP2013117373A (ja) * | 2013-03-18 | 2013-06-13 | Mitsubishi Electric Corp | 冷凍サイクル装置及び冷凍サイクル制御方法 |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2018100729A1 (ja) * | 2016-12-02 | 2018-06-07 | 三菱電機株式会社 | 冷凍サイクル装置 |
JPWO2018100729A1 (ja) * | 2016-12-02 | 2019-06-27 | 三菱電機株式会社 | 冷凍サイクル装置 |
EP3553435A4 (en) * | 2016-12-08 | 2020-08-19 | Kawasaki Jukogyo Kabushiki Kaisha | RAW MATERIAL GAS LIQUIDGE DEVICE AND CONTROL PROCEDURE FOR IT |
WO2018216112A1 (ja) * | 2017-05-23 | 2018-11-29 | 三菱電機株式会社 | 冷凍サイクル装置 |
Also Published As
Publication number | Publication date |
---|---|
EP3236174A1 (en) | 2017-10-25 |
JPWO2016084186A1 (ja) | 2017-04-27 |
US20170234576A1 (en) | 2017-08-17 |
EP3236174B1 (en) | 2020-07-01 |
EP3236174A4 (en) | 2018-10-24 |
JP6289668B2 (ja) | 2018-03-07 |
US10088198B2 (en) | 2018-10-02 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP6289668B2 (ja) | 空調給湯複合システム | |
EP2878902B1 (en) | Air-conditioning device | |
US9625187B2 (en) | Combined air-conditioning and hot-water supply system | |
WO2015104815A1 (ja) | 空調給湯複合システム | |
JP5759017B2 (ja) | 空気調和装置 | |
US9080778B2 (en) | Air-conditioning hot-water supply combined system | |
JP6289734B2 (ja) | 空調給湯複合システム | |
JP5893151B2 (ja) | 空調給湯複合システム | |
EP2781848B1 (en) | Combined air-conditioning/hot water supply system | |
JP6257809B2 (ja) | 冷凍サイクル装置 | |
US9599380B2 (en) | Refrigerant charging method for air-conditioning apparatus and air-conditioning apparatus | |
JP6567086B2 (ja) | 空気調和装置 | |
WO2017109905A1 (ja) | 空調給湯複合システム | |
JPWO2013046269A1 (ja) | 空調給湯複合システム |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 14907085 Country of ref document: EP Kind code of ref document: A1 |
|
ENP | Entry into the national phase |
Ref document number: 2016561158 Country of ref document: JP Kind code of ref document: A |
|
WWE | Wipo information: entry into national phase |
Ref document number: 15518629 Country of ref document: US |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
REEP | Request for entry into the european phase |
Ref document number: 2014907085 Country of ref document: EP |