WO2017109905A1 - 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
- WO2017109905A1 WO2017109905A1 PCT/JP2015/086090 JP2015086090W WO2017109905A1 WO 2017109905 A1 WO2017109905 A1 WO 2017109905A1 JP 2015086090 W JP2015086090 W JP 2015086090W WO 2017109905 A1 WO2017109905 A1 WO 2017109905A1
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- WIPO (PCT)
- Prior art keywords
- hot water
- water supply
- refrigerant
- heat medium
- heat
- Prior art date
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- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 title claims abstract description 192
- 238000004378 air conditioning Methods 0.000 title claims abstract description 48
- 239000003507 refrigerant Substances 0.000 claims abstract description 151
- 238000001816 cooling Methods 0.000 claims description 31
- 238000010438 heat treatment Methods 0.000 claims description 30
- 238000004781 supercooling Methods 0.000 claims description 26
- 230000006870 function Effects 0.000 claims description 25
- 238000000034 method Methods 0.000 description 36
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- 238000005259 measurement Methods 0.000 description 4
- LYCAIKOWRPUZTN-UHFFFAOYSA-N Ethylene glycol Chemical compound OCCO LYCAIKOWRPUZTN-UHFFFAOYSA-N 0.000 description 3
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- 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
- 230000002528 anti-freeze Effects 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
- NNPPMTNAJDCUHE-UHFFFAOYSA-N isobutane Chemical compound CC(C)C NNPPMTNAJDCUHE-UHFFFAOYSA-N 0.000 description 2
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- 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
- 229910000831 Steel Inorganic materials 0.000 description 1
- BZHJMEDXRYGGRV-UHFFFAOYSA-N Vinyl chloride Chemical compound ClC=C BZHJMEDXRYGGRV-UHFFFAOYSA-N 0.000 description 1
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- 239000001294 propane Substances 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
Images
Classifications
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- 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
- F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-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
- 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
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D19/00—Details
- F24D19/10—Arrangement or mounting of control or safety devices
- F24D19/1006—Arrangement or mounting of control or safety devices for water heating systems
- F24D19/1009—Arrangement or mounting of control or safety devices for water heating systems for central heating
- F24D19/1039—Arrangement or mounting of control or safety devices for water heating systems for central heating the system uses a heat pump
-
- 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
- F24H15/212—Temperature of the water
- F24H15/215—Temperature of the water before heating
-
- 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
- F24H15/212—Temperature of the water
- F24H15/219—Temperature of the water after heating
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- 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
- F24H15/227—Temperature of the refrigerant in heat pump cycles
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- 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
- F24H15/238—Flow rate
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- 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
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- 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
- F24H15/385—Control of expansion valves of heat pumps
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- 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
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- 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
- F24H6/00—Combined water and air heaters
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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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
- F25B30/00—Heat pumps
- F25B30/02—Heat pumps of the compression type
-
- 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
- F24D2200/00—Heat sources or energy sources
- F24D2200/16—Waste heat
- F24D2200/31—Air conditioning 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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
- F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2117—Temperatures of an evaporator
- F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
- F25B2700/21172—Temperatures of an evaporator of the fluid cooled by the evaporator at the inlet
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2117—Temperatures of an evaporator
- F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
- F25B2700/21173—Temperatures of an evaporator of the fluid cooled by the evaporator at the outlet
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2117—Temperatures of an evaporator
- F25B2700/21174—Temperatures of an evaporator of the refrigerant at the inlet of the evaporator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2117—Temperatures of an evaporator
- F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the evaporator
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B10/00—Integration of renewable energy sources in buildings
- Y02B10/20—Solar thermal
Definitions
- the present invention relates to an air conditioning and hot water supply combined system capable of air conditioning operation and hot water supply operation using a heat medium cooled or heated using a heat pump cycle.
- the air conditioning and hot water supply combined system described in Patent Document 1 includes at least one heat source unit on which a compressor and a heat source side heat exchanger are mounted, and at least one on which an indoor side heat exchanger and an indoor side expansion device are mounted.
- the indoor unit is connected to at least one hot water supply unit on which the refrigerant-heat medium heat exchanger and the hot water supply side expansion device are mounted.
- this air-conditioning hot-water supply complex system performs heat exchange with a refrigerant circuit that performs at least a heating operation in which an indoor heat exchanger functions as a condenser or a radiator, and a refrigerant in the refrigerant circuit and a refrigerant-heat medium heat exchanger.
- a heat medium circuit that performs at least a heating operation for heating the heat medium, and is a system that enables an air conditioning operation (heating operation) and a hot water supply operation (heating operation) to be performed simultaneously in one refrigerant system.
- Patent Document 1 is not a system in which different refrigerant systems are connected in a complicated manner, an air conditioning and hot water supply complex system can be constructed at a very low cost.
- the indoor side expansion device and the hot water supply side expansion device are set so that the respective subcooling degrees of the indoor unit and the hot water supply unit become the corresponding target supercooling degrees.
- the degree of supercooling is controlled individually.
- the heat medium outlet temperature which is the outlet temperature of the heat medium side outlet of the hot water supply unit
- this supercooling control is the heat medium outlet temperature, so the heat medium outlet temperature is set to the target temperature.
- the heat medium outlet temperature cannot be controlled directly by controlling the rotation speed of the compressor, and by performing supercooling control, the heat medium outlet temperature is controlled to approach the target temperature as a result. It ’s just that. Further, the hot water supply unit cannot independently control the heat medium outlet temperature according to the required hot water supply capability required by itself, and improvement has been demanded.
- the present invention has been made to solve the above-described problems, and an object of the present invention is to obtain an air-conditioning and hot-water supply complex system in which a hot-water supply unit is independent and can perform fine outlet temperature control.
- An air conditioning and hot water supply combined system includes a heat source unit on which a compressor and a heat source side heat exchanger are mounted, and a hot water supply unit on which a refrigerant-heat medium heat exchanger, a hot water supply side expansion device, and a pump are mounted,
- a heat source unit on which a compressor and a heat source side heat exchanger are mounted
- a hot water supply unit on which a refrigerant-heat medium heat exchanger, a hot water supply side expansion device, and a pump are mounted
- the hot water supply unit it is possible for the hot water supply unit to be self-supporting and to perform fine outlet temperature control.
- FIG. 1 is a refrigerant circuit diagram illustrating an example of a refrigerant circuit configuration of an air conditioning and hot water supply complex system according to an embodiment of the present invention. Based on FIG. 1, the structure and operation
- the combined air conditioning and hot water supply system 100 is installed in a building, condominium, hotel, or the like, and can simultaneously supply an air conditioning load (cooling load, heating load) and a hot water supply load by using a refrigeration cycle that circulates refrigerant. Is.
- the combined air conditioning and hot water supply system 100 includes at least a heat source unit (outdoor unit) 110, a load side unit (indoor unit) 210, and a hot water supply unit 310. Among these, 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 that is a refrigerant pipe, a liquid branch pipe 3b that is a refrigerant pipe, a gas branch pipe 3a that is a refrigerant pipe, and a gas main pipe 2 that is a refrigerant pipe.
- the heat source unit 110 and the hot water supply unit 310 are connected by a liquid main pipe 1 that is a refrigerant pipe, a liquid branch pipe 4b that is a refrigerant pipe, a gas branch pipe 4a that is a refrigerant pipe, and a gas main pipe 2 that is a refrigerant pipe.
- 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.
- the heat source unit 110 includes a compressor (heat source side compressor) 111, a flow path switching valve 112 as a flow path switching means, a heat source side heat exchanger 113, and an accumulator 115 connected in series.
- the heat source unit 110 is provided with a blower 114 such as a fan for supplying air to the heat source side heat exchanger 113 in the vicinity of the heat source side heat exchanger 113.
- the compressor 111 sucks the refrigerant flowing through the gas main pipe 2 and compresses the refrigerant to bring it into a high temperature and high pressure state.
- the compressor 111 is not particularly limited as long as it can compress the sucked air-conditioning refrigerant to a high pressure state.
- the compressor 111 can be configured using various types such as reciprocating, rotary, scroll, or screw.
- the compressor 111 may be of a type that can be variably controlled by an inverter.
- the flow path switching valve 112 switches the flow of the air conditioning refrigerant according to the required operation mode (cooling or heating).
- 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 accumulator 115 is disposed on the suction side of the compressor 111 and stores excess refrigerant.
- 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.
- an indoor expansion device 212 and an indoor heat exchanger 211 are mounted connected in series.
- FIG. 1 although the state in which the one indoor unit 210 is mounted is shown as an example, the number is not particularly limited.
- the indoor unit 210 may be provided with a blower such as a fan for supplying air to the indoor heat exchanger 211 in the vicinity of the indoor heat exchanger 211.
- 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 throttle device 212 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.
- a gas pipe temperature detection sensor 213G and a liquid pipe temperature detection sensor 213L are installed in the front and rear pipes of the indoor heat exchanger 211. Based on the temperature data information obtained from these sensors, 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 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 a blower (not shown) and the refrigerant to condense the refrigerant. It is liquefied or vaporized.
- the hot water supply unit 310 has a function of receiving a supply of hot or cold heat from the heat source unit 110 and taking charge of a hot water supply load or a cooling load.
- the hot water supply unit 310 includes a hot water supply side expansion device 312 and a refrigerant-heat medium heat exchanger 311 connected in series.
- FIG. 1 although the state in which one hot water supply unit 310 is mounted is shown as an example, the number is not particularly limited.
- 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 decompressing it.
- the hot water supply side throttling device 312 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 refrigerant-heat medium heat exchanger 311 is a heat exchanger that has a refrigerant pipe through which the refrigerant flows and a heat medium pipe through which the heat medium flows, and performs heat exchange between the refrigerant and the heat medium.
- the refrigerant-heat medium heat exchanger 311 functions as a radiator (condenser) during the heating cycle and as an evaporator during the cooling cycle, and condenses the refrigerant flowing through the refrigerant pipe by heat exchange with the heat medium flowing through the heat medium circuit 10. It is liquefied or vaporized.
- a gas pipe temperature detection sensor 313G and a liquid pipe temperature detection sensor 313L are installed in the front and rear pipes on the refrigerant pipe side of the refrigerant-heat medium heat exchanger 311.
- the front and rear pipes on the heat medium pipe side of the refrigerant-heat medium heat exchanger 311 are provided with an inlet temperature sensor 316R that detects the heat medium inlet temperature Twi and an outlet temperature sensor 316F that detects the heat medium outlet temperature Two. ing.
- the control device 320 determines the control amount of the hot water supply side expansion device 312 and performs refrigerant flow control of the hot water supply side expansion device 312.
- the heat medium pipe of the refrigerant-heat medium heat exchanger 311 constitutes a part of the heat medium circuit 10, and the heat medium circuit 10 includes a pump 315, a heat medium pipe 5, and a heat medium pipe 6. These are connected, and the heat medium heated or cooled by the refrigerant-heat medium heat exchanger 311 is circulated by the pump 315.
- the heat medium pipe 5 and the heat medium pipe 6 may be constituted by a copper pipe, a stainless pipe, a steel pipe, a vinyl chloride pipe, or the like.
- the pump 315 has a function of circulating the heat medium in the heat medium circuit 10.
- pump types there are an inexpensive constant speed type and a type in which the flow rate is varied using an inverter.
- a plurality of pumps 315 may be connected in parallel, and the flow rate may be varied by changing the number of operating units.
- An appropriate pump 315 may be selected in accordance with the head and flow rate of the heat medium circuit 10 to be connected.
- a variable flow rate type is selected as the pump 315, and the flow rate is controlled to increase as the hot water supply load increases.
- the heat source unit 110, the indoor unit 210, and the hot water supply unit 310 have a control device 120, a control device 220, and a control device 320, respectively, and have a function of controlling an actuator included in each unit.
- the control device 120, the control device 220, and the control device 320 are each configured by, for example, a microcomputer or a DSP.
- the heat source unit 110, the indoor unit 210, and the hot water supply unit 310 have a communication device 130, a communication device 230, and a communication device 330, respectively, and transmit information that each has.
- the control device 120 of the heat source unit 110 has a function of controlling the refrigerant pressure state and the refrigerant temperature state in the air conditioning and hot water supply complex system 100. Specifically, the control device 120 of the heat source unit 110 has functions of controlling the operating frequency of the compressor 111, controlling the fan rotation speed of the blower 114, and switching the flow path switching valve 112. Yes. In addition, for example, if the heat source side heat exchanger 113 is divided into a plurality of heat exchangers and an on-off valve (not shown) is installed on the primary side of the heat source side heat exchanger 113 for each heat exchanger, the control The device 120 has a function of changing the area of the heat source side heat exchanger 113 for heat exchange by controlling the on-off valve.
- the control device 220 of the indoor unit 210 determines the degree of superheat during the cooling operation of the indoor unit 210 and the heating operation of the indoor unit 210.
- the control device 320 has a function of controlling the fan rotation speed of a blower (not shown) and controlling the opening degree of the indoor expansion device 212.
- the indoor heat exchanger 211 is divided into a plurality of heat exchangers and an open / close valve (not shown) is installed on the primary side of the indoor heat exchanger 211 for each heat exchanger, It has a function of changing the heat exchange area of the indoor heat exchanger 211 by controlling the valve.
- the control device 320 of the hot water supply unit 310 determines the degree of superheat during the cooling operation of the hot water supply unit 310 and the hot water supply operation of the hot water supply unit 310. It has a function of controlling the degree of supercooling or the heat medium outlet temperature Two. Specifically, in the control device 320, the refrigerant-heat medium heat exchanger 311 is divided into a plurality of heat exchangers, and an open / close valve (not shown) is provided on the primary side of the refrigerant-heat medium heat exchanger 311 for each heat exchanger.
- the on-off valve is controlled to change the heat exchange area of the refrigerant-heat medium heat exchanger 311.
- the control device 320 has a function of controlling the opening degree of the hot water supply side expansion device 312.
- the heat medium circuit 10 has a function of controlling the target temperature based on information obtained from the inlet temperature sensor 316R and the outlet temperature sensor 316F, or operates the pump 315 connected to the heat medium circuit 10. It also has the function of outputting ON / OFF and controlling the flow rate of the pump 315.
- the air conditioning and hot water supply complex system 100 includes a sensor that detects the refrigerant discharge pressure, a sensor that detects the refrigerant suction pressure, a sensor that detects the refrigerant discharge temperature, and a refrigerant suction temperature.
- Sensor sensor for detecting the temperature of refrigerant flowing into and out of the heat source side heat exchanger 113, sensor for detecting the outside air temperature taken into the heat source unit 110, sensor for detecting the temperature of the air sucked into or blown into the indoor heat exchanger 211
- a sensor or the like for detecting the temperature of the heat medium stored in the hot water storage tank may be provided.
- Information (measurement information such as temperature information and pressure information) detected by these various sensors is sent to the control device 120, the control device 220, and the control device 320 via the communication device 130, the communication device 230, and the communication device 330. , It will be used to control each actuator.
- the refrigerant that can be used in the air-conditioning and hot water supply complex system 100 will be described.
- Examples of the refrigerant that can be used in the refrigeration cycle of the air conditioning and hot water supply complex system 100 include a non-azeotropic refrigerant mixture, a pseudo-azeotropic refrigerant mixture, and a single refrigerant.
- Non-azeotropic refrigerant mixture includes R407C (R32 / R125 / R134a) which is an HFC (hydrofluorocarbon) refrigerant.
- 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) and R404A (R125 / R143a / R134a) which are HFC refrigerants.
- 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.
- natural refrigerants such as carbon dioxide, propane, isobutane, and ammonia can be used.
- R22 represents chlorodifluoromethane
- R32 represents difluoromethane
- R125 represents pentafluoromethane
- R134a represents 1,1,1,2-tetrafluoromethane
- R143a represents 1,1,1-trifluoroethane. Yes. Therefore, it is good to use the refrigerant
- the heat medium circulating in the heat medium circuit 10 of the hot water supply unit 310 may be water or another fluid.
- an antifreeze may be added to the water.
- the type of antifreeze is not particularly limited, and may be selected according to availability and use, such as ethylene glycol and propylene glycol.
- the operation performed by the air conditioning and hot water supply complex system 100 includes a heating (heating) operation and a cooling (cooling) operation. Both operations will be described below.
- the heating (heating) operation the flow path switching valve 112 is switched to the dotted line side in FIG. 1, and in the cooling (cooling) operation, the flow path switching valve 112 is switched to the solid line side in FIG.
- the high-pressure gas refrigerant heated and compressed by the compressor 111 is conveyed to the indoor unit 210 (or the hot water supply unit 310) via the flow path switching valve 112, the gas main pipe 2, and the gas branch pipe 3a (or the gas branch pipe 4a).
- the refrigerant conveyed to the indoor unit 210 (or hot water supply unit 310) releases heat to the indoor air (or the heat medium of the heat medium circuit 10) in the indoor heat exchanger 211 or the refrigerant-heat medium heat exchanger 311. Therefore, it changes into a high-pressure liquid refrigerant by the condensation action.
- the high-pressure liquid refrigerant is changed into a low-pressure two-phase refrigerant (a refrigerant mixed with gas and liquid) by an expansion action in the indoor side expansion device 212 (or the hot water supply side expansion device 312) on the secondary side of the heat exchanger. .
- the low-pressure two-phase refrigerant is changed into a low-pressure gas refrigerant by transferring heat from the air in the heat source side heat exchanger 113 in the heat source unit 110 via the liquid branch pipe 4b and the liquid main pipe 1.
- the low-pressure gas refrigerant passes through the flow path switching valve 112 and the accumulator 115, is sucked in by the compressor 111, and changes to a high-pressure gas refrigerant.
- the air conditioning and hot water supply combined system 100 can perform a heating (hot water supply) operation.
- the high-pressure gas refrigerant heated and compressed by the compressor 111 passes through the flow path switching valve 112 and is conveyed to the heat source side heat exchanger 113 in the heat source unit.
- the heat source side heat exchanger 113 by releasing heat to the air, 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 (or the hot water supply unit 310) through the liquid main pipe 1 and the liquid branch pipe 3b (or the liquid branch pipe 4b).
- the high-pressure liquid refrigerant is a low-pressure two-phase refrigerant (refrigerant mixed with gas and liquid) due to the expansion action in the indoor-side expansion device 212 (or hot-water supply side expansion device 312).
- the indoor heat exchanger 211 or refrigerant-heat medium heat exchanger 311
- the heat is transferred from the load to the low-pressure gas refrigerant (the load side is deprived of heat). Cooled by).
- the low-pressure gas refrigerant exiting the indoor unit 210 (or the hot water supply unit 310) returns to the heat source unit 110 via the gas branch pipe 3a (or the gas branch pipe 4a) and the gas main pipe 2.
- the low-pressure gas refrigerant that has flowed into the heat source unit 110 passes through the flow path switching valve 112 and the accumulator 115, is sucked in by the compressor 111, and changes to a high-pressure gas refrigerant.
- the air conditioning and hot water supply combined system 100 can perform a cooling (cooling) operation.
- the refrigerant is stored in the accumulator 115 because the refrigerant is left in the heating operation.
- the supercooling degree control for controlling the hot water supply side expansion device 312 so that the supercooling degree of the hot water supply unit 310 becomes the target supercooling degree, and the hot water supply so that the heat medium outlet temperature Two becomes the target temperature Twom.
- outlet temperature control for controlling the side expansion device 312.
- the supercooling control is the refrigerant control itself in the conventional building multi-air conditioner.
- the conventional control method can be selected when fine outlet temperature control is not required.
- the hot water supply unit 310 has two setting modes of “normal setting” and “heat medium outlet temperature thermo setting” in which priority is given to setting the heat medium outlet temperature Two to the target temperature Twom. Can be switched by user operation.
- “Only normal cooling” is performed in the “normal setting”, and control for switching between the supercooling degree control and the outlet temperature control is performed in the “heat medium outlet temperature thermo setting”.
- the “heat medium outlet temperature thermo setting” specifically, when the temperature difference between the heat medium outlet temperature Two and the target temperature Two is equal to or larger than a preset value ⁇ , that is, the heat medium outlet temperature Two is the target temperature Twom. Until it approaches, supercooling control is performed.
- the temperature difference between the heat medium outlet temperature Two and the target temperature Twom is smaller than the set value ⁇ , that is, when the heat medium outlet temperature Two approaches the target temperature Twom, the outlet temperature control is performed. This is due to the following reason.
- the supercooling control In the supercooling control, the heat medium outlet temperature Two becomes a consequence, so the heat medium outlet temperature Two may not be the target temperature Twom. Therefore, the supercooling control is performed until the heat medium outlet temperature Two approaches the target temperature Twom, and when the heat medium outlet temperature Two approaches the target temperature Twom, the outlet temperature control is performed in order to achieve the target temperature Twom.
- the hot water supply unit 310 is independent and controls the hot water supply side expansion device 312. In order for each hot water supply unit 310 to be independent and perform outlet temperature control, it is necessary to know the required hot water supply capacity Qd required for each hot water supply unit 310 to handle the load of the heat medium circuit 10.
- the pump 315 is controlled such that the heat medium flow rate increases as the hot water supply load increases. Therefore, if the hot water supply unit 310 can grasp the heat medium flow rate Vw flowing through the hot water supply unit 310 itself, the required hot water supply capacity Qd required for the hot water supply unit 310 can be obtained.
- the hot water supply unit 310 uses the required hot water supply capacity Qd and the refrigerant information to calculate the necessary refrigerant circulation amount Grm necessary for the refrigerant-heat medium heat exchanger 311 to set the heat medium outlet temperature Two to the target temperature Twom.
- the Cv value of the hot water supply side expansion device 312 is determined from the required refrigerant circulation amount Grm, and the hot water supply side expansion device 312 is controlled.
- the present invention performs the outlet temperature control for controlling the hot water supply side expansion device 312 so that the heat medium outlet temperature Two becomes the target temperature Twom based on the required hot water supply capacity Qd and the refrigerant information.
- the current hot water supply capacity Qn in the hot water supply unit 310 is obtained from the heat medium flow rate Vw that is the heat medium flow rate information of the hot water supply unit 310, the heat medium inlet temperature Twi obtained from the inlet temperature sensor 316R, and the outlet temperature sensor 316F.
- Vw the heat medium flow rate information of the hot water supply unit 310
- Twi the heat medium inlet temperature Twi obtained from the inlet temperature sensor 316R
- the outlet temperature sensor 316F the outlet temperature sensor 316F.
- the first method is a method in which a flow rate sensor 11 (shown by a dotted line in FIG. 1) is installed in the heat medium circuit 10 and the heat medium flow rate Vw detected by the flow rate sensor 11 is taken into the control device 320 to know. It is done. There is no particular specification of the flow sensor type, and it can be freely selected based on the purpose and specifications. If the pressure difference with respect to the flow rate of the hot water supply unit 310 is known in advance, a differential pressure sensor may be used instead of the flow rate sensor.
- the second method of knowing the heat medium flow rate Vw is a method of knowing the heat medium flow rate Vw based on the power and rotation speed of the pump 315. This will be described with reference to FIG.
- FIG. 2 is a diagram showing a power curve of a pump in the combined air-conditioning and hot-water supply system according to the embodiment of the present invention.
- the power curve shows the relationship between the power and the flow rate.
- (a) shows the power curve when the rotational speed is n1
- (b) shows the power curve when the rotational speed is n2.
- the horizontal axis in FIG. 2 indicates the heat medium flow rate Vw
- the vertical axis indicates the power W.
- the power W of the pump 315 and the heat medium flow rate Vw are uniquely determined based on the power curve.
- the power is calculated from the information, and the heat medium is calculated from the calculated power, the rotational speed of the pump 315, and the power curve.
- the flow rate Vw can be calculated.
- FIG. 2 shows an example in which the heat medium flow rate Vw2 is obtained from the power W2 and the power curve (a) of the rotation speed n2.
- the voltage and current information can be calculated from a voltage sensor and a current sensor not described in FIG. In some cases, voltage and power factor are uniquely determined from product specifications.
- the pump 315 may be appropriately selected according to the specifications of the hot water supply unit 310.
- FIG. 3 is an explanatory diagram of a method of knowing heat medium flow rate information in the air conditioning and hot water supply complex system according to the embodiment of the present invention.
- the horizontal axis represents time
- the vertical axis represents the heat medium temperature difference at the inlet / outlet on the heat medium side of the refrigerant-heat medium heat exchanger 311.
- the heat medium flow rate Vw flowing through the hot water supply unit 310 itself is calculated based on the heat medium temperature difference at the inlet / outlet of the refrigerant-heat medium heat exchanger 311 detected at each control interval.
- a prediction method is mentioned. In the following description, it is assumed that “current time” in FIG. 3 is “current time” and “time immediately before the current time” is “previous time”.
- a ratio R obtained by dividing the current heat medium temperature difference (hereinafter referred to as a predicted temperature difference) ⁇ Tp (n) is the current heat medium flow rate Vw, that is, the heat medium flow rate Vw to be obtained here is determined as the previous heat Equal to the ratio obtained by dividing by the medium flow rate.
- the ratio R corresponds to a heat medium flow rate correction ratio R described later.
- the “previous heat medium flow rate” may be an initial value set in advance when calculating the first heat medium flow rate Vw. Considering that the control amount becomes excessive when the initial value is large, the lowest heat medium flow rate possible on the apparatus may be used as the initial value. However, since the stability of the control varies depending on the situation on the heat medium circuit 10 side, an optimal initial value may be set according to the situation.
- Qr is the refrigerant capacity.
- the refrigerant side capacity Qr can be calculated using the following formula (4).
- the previous required refrigerant circulation amount Grm may be used as Grm in the equation (4).
- A is a constant considering the density and specific heat of the heat medium flowing in the refrigerant-heat medium heat exchanger 311.
- Vw is the heat medium flow rate, and when calculating the first heat medium flow rate Vw, for example, the lowest heat medium flow rate possible on the apparatus is used as described above. What is necessary is just to use the obtained heat-medium flow rate.
- the required hot water supply capacity Qd can be obtained from the above equation (2).
- the refrigerant side capacity Qr is used to calculate the necessary refrigerant circulation amount Grm.
- the refrigerant side capacity Qr is the amount of heat given from the refrigerant circuit side to the load on the heat medium circuit 10 side, the necessary refrigerant circulation amount Grm, the enthalpy H1 on the primary side of the refrigerant-heat medium heat exchanger 311, and the secondary side And enthalpy H2 of the following formula (4).
- the primary side is the gas side for hot water use and the liquid side for cooling
- the secondary side is the liquid side for hot water and the gas side for cooling.
- the required refrigerant circulation amount Grm can be expressed by the following equation (5).
- enthalpy H1 and enthalpy H2 can be calculated as follows.
- enthalpy H1 can be calculated from the refrigerant pressure and refrigerant temperature on the gas pipe side
- enthalpy H2 can be calculated from the liquid pipe temperature.
- the enthalpy H1 can be calculated from the refrigerant temperature passing through the liquid branch pipe 4b from the indoor expansion device 212, and the enthalpy H2 is detected by the liquid pipe temperature detection sensor 313L. It is possible to calculate from the detection temperature and the detection temperature of the gas pipe temperature detection sensor 313G.
- the temperature sensor described in FIG. 1 or the pressure sensor information not described may be used.
- B is an arbitrary constant
- the Cv value is a Cv value determined for each opening of the expansion device.
- the Cv value of the hot water supply side expansion device 312 can be calculated by substituting the necessary refrigerant circulation amount Grm obtained by the above equation (5) into Gr of the equation (6).
- the “refrigerant density on the primary side of the expansion device” can be calculated from the pressure information on the primary side of the hot water supply side expansion device and the refrigerant temperature detected by the liquid pipe temperature detection sensor 313L in the case of heating operation. It is.
- the hot water supply side expansion device primary side in the heating operation corresponds to the hot water supply side expansion device 312 side from the refrigerant-heat medium heat exchanger 311.
- the "throttle device primary side refrigerant density” can be calculated from the pressure information on the hot water supply side throttle device primary side and the refrigerant temperature on the liquid branch pipe 4b side from the indoor side throttle device 212. Is possible.
- the hot water supply side expansion device primary side in the cooling operation corresponds to the liquid branch pipe 4b side.
- the “front-rear differential pressure of the expansion device” can be calculated from the liquid pipe temperature detection sensor 313L depending on the state of the refrigerant by providing pressure sensors before and after the hot water supply-side expansion device.
- the information obtained by the control device 120 on the heat source unit side is acquired and used by the control device 320 on the hot water supply unit 310 side via the communication device 130 and the communication device 330. Also good.
- any of the above-described refrigerant pressure information and refrigerant temperature information may use values determined in advance through tests or experiments. What method should be used to determine the value is appropriately determined as necessary.
- the refrigerant pressure information and the refrigerant temperature information used in Expression (6) correspond to “refrigerant information” of the present invention.
- the required opening of the hot water supply side expansion device 312 can be obtained from the required refrigerant circulation amount Grm calculated based on the required hot water supply capacity Qd and the refrigerant information, and the control amount can be determined. is there.
- the control amount a control amount that achieves the target value opening degree may be given to the hot water supply side expansion device 312 at once, or the control amount obtained by dividing the determined control amount in consideration of the stability of the refrigerant control is set to the control interval. You may give to the hot water supply side expansion device 312 every time.
- FIG. 4 is a diagram showing a control flowchart in the combined air-conditioning and hot-water supply system according to the embodiment of the present invention.
- the setting mode is set to “heat medium outlet temperature thermosetting” capable of fine outlet temperature control (S1). If it is determined in step S1 that “heat medium outlet temperature thermo setting” is set, the control device 320 calculates a temperature difference between the heat medium outlet temperature Two and the target temperature Twom, and optionally the temperature difference. Comparison with the set value ⁇ is performed (S2). If the temperature difference is smaller than the set value ⁇ , the process proceeds to the heat medium flow rate information acquisition process (S3).
- the control device 320 of the hot water supply unit 310 acquires the heat medium flow rate Vw of the heat medium circuit 10 (S3).
- the method using the flow sensor 11, the method using pump power, and the method for predicting based on the heat medium temperature difference detected at each control interval A total of three methods are used. Of these three methods, the latter two methods will be described later with reference to FIGS. 5 and 6.
- the control device 320 After the heat medium flow rate information acquisition process, the control device 320 performs the required hot water supply capacity Qd calculation process (S4) as described above, and subsequently calculates the opening degree control amount of the hot water supply side expansion device 312 as described above. Processing (S5) is performed sequentially. With the above processing, the opening degree control amount output from the control device 320 to the hot water supply side expansion device 312 is determined.
- step S1 when the setting mode is not set to “heat medium outlet temperature thermo setting”, that is, set to “normal setting” or set to “heat medium outlet temperature thermo setting”.
- the temperature difference between the heat medium outlet temperature Two and the target temperature Twom is equal to or greater than the set value ⁇
- supercooling control is performed.
- a process (S6) of acquiring the current supercooling degree is performed, and then the hot water supply side throttle is set so that the supercooling degree acquired in step S6 becomes a preset target supercooling degree.
- the process (S7) which calculates the opening degree control amount of the apparatus 312 is implemented.
- the control device 320 When the opening degree control amount of the hot water supply side throttle device 312 is obtained as described above, the control device 320 performs a process of outputting the opening degree control amount to the hot water supply side throttle device 312 (S8). By this output, the opening degree information is output to the hot water supply side expansion device 312 and controlled. After the control process is performed, the processes in steps S1 to S8 are repeated at each control interval until hot water supply unit 310 is stopped (S9).
- the control interval may be set arbitrarily, and may be set while looking at the stability of the refrigeration cycle.
- FIG. 5 is a diagram showing a flowchart of heat medium flow rate detection by pump power in the combined air-conditioning and hot water supply system according to the embodiment of the present invention.
- the control device 320 of the hot water supply unit 310 acquires voltage information, current information, and pump rotation speed information on the voltage applied to the pump 315 (S11). Thereafter, the control device 320 performs a power value calculation process (S12). That is, the control device 320 calculates a power value that is power of the pump 315 based on the information acquired in step S11.
- the power value is a product of voltage and current, but may be calculated in consideration of single phase / 3 phase, power factor COS ⁇ and the like according to the pump specifications.
- the control device 320 calculates the heat medium flow rate value based on the power, the pump rotational speed, and the power curve as shown in FIG. 2 (S13).
- a power curve for each rotation speed is stored in the control device 320 in advance.
- FIG. 6 is a diagram showing a flow chart of heat medium flow rate detection by heat medium flow rate prediction in the air conditioning and hot water supply complex system according to the embodiment of the present invention.
- the control device 320 of the hot water supply unit 310 first detects the refrigerant pressure, the refrigerant temperature, the heat medium inlet temperature Twi, and the heat medium outlet temperature Two (S21). Thereafter, an initial value of the heat medium flow rate is set (S22). As the initial value, the lowest heat medium flow rate possible on the apparatus is used as described above.
- the control device 320 performs a capacity calculation process (S23) for calculating the refrigerant side capacity Qr as described above.
- the control device 320 calculates the predicted temperature difference ⁇ Tp by the above equation (3) based on the refrigerant side capability Qr calculated by the capability calculation process (S24).
- ⁇ Tm the heat medium temperature difference at the inlet / outlet on the heat medium side of the current refrigerant / heat medium heat exchanger 311.
- the hot water supply unit 310 when the difference between the heat medium outlet temperature Two and the target temperature Twom is smaller than the set value, the hot water supply unit 310 generates heat based on the required hot water supply capacity and the refrigerant information.
- the hot water supply side expansion device 312 is controlled so that the medium outlet temperature Two becomes the target temperature Twom. For this reason, finer outlet temperature control is possible as compared with the supercooling control in which the heat medium outlet temperature Two becomes a consequence.
- each hot water supply unit 310 can realize individual distributed control that can perform fine outlet temperature control independently and individually. The same control is possible in the cooling operation.
- the hot water supply unit 310 calculates the required refrigerant circulation amount Grm based on the required hot water supply capacity and the refrigerant information, and determines the opening degree of the hot water supply side expansion device 312 based on the required refrigerant circulation amount Grm. Fine outlet temperature control can be realized.
- the same supercooling control as in the prior art is performed, and the temperature difference between the heat medium outlet temperature Two and the target temperature Twom becomes smaller than the set value.
- the supercooling control is preferable to the outlet temperature control in terms of operating efficiency, and the supercooling control is performed when the heat medium outlet temperature Two approaches the target temperature Twom. By switching from to the outlet temperature control, the operation efficiency is not lowered when performing the fine outlet temperature control.
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Abstract
Description
以下、図面に基づいて本発明の実施の形態について説明する。
図1は、本発明の実施の形態に係る空調給湯複合システムの冷媒回路構成の一例を示す冷媒回路図である。図1に基づいて、空気調和機の構成および動作について説明する。
空調給湯複合システム100は、熱源ユニット(室外機)110と、負荷側ユニット(室内ユニット)210と、給湯ユニット310と、を少なくとも有している。このうち、室内ユニット210および給湯ユニット310は、熱源ユニット110に対して並列となるように接続されている。
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。この熱源ユニット110には、圧縮機(熱源側圧縮機)111と、流路切替手段である流路切替弁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ファン等の送風機114が熱源側熱交換器113の近傍位置に設置されている。
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。なお、図1では、1台の室内ユニット210が搭載されている状態を例に示しているが、台数を特に限定するものではない。また、室内ユニット210には、室内側熱交換器211に空気を供給するためのファン等の送風機を室内側熱交換器211の近傍に設けるとよい。
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の供給を受けて給湯負荷または冷却負荷を担当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、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。なお、図1では、1台の給湯ユニット310が搭載されている状態を例に示しているが、台数を特に限定するものではない。
空調給湯複合システム100で行う運転には、暖房(加熱)運転および冷房(冷却)運転が存在する。以下に両運転について説明する。なお、暖房(加熱)運転では流路切替弁112は図1の点線側に切り替えられ、冷房(冷却)運転では流路切替弁112は図1の実線側に切り替えられる。
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弁112、ガス主管2、ガス枝管3a(またはガス枝管4a)を経て、室内ユニット210(または給湯ユニット310)へ搬送される。室内ユニット210(または給湯ユニット310)に搬送された冷媒は、室内側熱交換器211または冷媒-熱媒体熱交換器311において室内空気(または熱媒体回路10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。高圧の液冷媒は熱交換器二次側にある室内側絞り装置212(または給湯側絞り装置312)にて膨張作用により低圧の二相冷媒(ガスと液が入り混じった冷媒)へと変化する。
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弁112を経て、熱源ユニット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3b(または液枝管4b)を経て、室内ユニット210(または給湯ユニット310)へ搬送される。
本実施の形態では、給湯ユニット310の過冷却度が目標過冷却度となるように給湯側絞り装置312を制御する過冷却度制御と、熱媒体出口温度Twoが目標温度Twomになるように給湯側絞り装置312を制御する出口温度制御とを有している。過冷却制御は、従来のビル用マルチエアコンでの冷媒制御そのものであるが、本実施の形態では、きめ細かい出口温度制御を求めない場合には従来通りの制御手法を選択可能としている。そして、給湯ユニット310では、「通常設定」と、熱媒体出口温度Twoを目標温度Twomとすることを優先した「熱媒体出口温度サーモ設定」との2つの設定モードを有しており、設定モードをユーザー操作により切替可能としている。
給湯ユニット310における現在の給湯能力Qnは、給湯ユニット310の熱媒体流量情報である熱媒体流量Vwと、入口温度センサー316Rから得られた熱媒体入口温度Twiと、出口温度センサー316Fから得られた熱媒体出口温度Twoと、冷媒-熱媒体熱交換器311に流れる熱媒体の密度および比熱を考慮した定数Aとを用いて、次式(1)で表せる。
図2に示すように、ポンプ315の動力Wと熱媒体流量Vwとは動力曲線に基づいて一意的に決まっている。よって、ポンプ315に印加される電圧、電流および力率等の情報がわかれば、それらの情報から動力を算出し、算出して得た動力とポンプ315の回転数と動力曲線とから、熱媒体流量Vwを算出することができる。図2では、動力W2と回転数n2の動力曲線(a)とから、熱媒体流量Vw2を求める例を示している。電圧、電流情報は、図1に未記載の電圧センサーおよび電流センサーから算出することが可能である。また電圧および力率等は製品仕様から一意的に決定しているものもある。ポンプ315は、給湯ユニット310の仕様に併せて適宜選定すればよい。
図3は、本発明の実施の形態に係る空調給湯複合システムにおいて熱媒体流量情報を知る方法の説明図である。図3において横軸は時間、縦軸は冷媒-熱媒体熱交換器311の熱媒体側の出入口の熱媒体温度差である。
必要冷媒循環量Grmの算出には冷媒側能力Qrが用いられる。冷媒側能力Qrは、冷媒回路側から熱媒体回路10側の負荷に与えられる熱量であり、必要冷媒循環量Grmと、冷媒-熱媒体熱交換器311の一次側のエンタルピH1と、二次側のエンタルピH2とを用いて、次式(4)で表せる。一次側とは、給湯用途であればガス側、冷却用途であれば液側であり、二次側とは、給湯用途であれば液側、冷却用途であればガス側である。
一般的に、絞り装置と冷媒循環量Grとの間には以下の式(6)が成り立っている。
本実施の形態に係る制御を図4に示すフローチャートにて述べる。
図4は、本発明の実施の形態に係る空調給湯複合システムにおける制御フローチャートを示す図である。
空調給湯複合システム100では、制御開始処理終了後、設定モードが、きめ細かな出口温度制御が可能な「熱媒体出口温度サーモ設定」に設定されているかどうかの判断を行う(S1)。ステップS1の判定にて、もし「熱媒体出口温度サーモ設定」に設定されていれば、制御装置320は、熱媒体出口温度Twoと目標温度Twomとの温度差を算出し、温度差と任意で設定した設定値αとの比較を実施(S2)する。ここで、温度差が設定値αよりも小さい場合、熱媒体流量情報取得処理(S3)へ移行する。
図5は、本発明の実施の形態に係る空調給湯複合システムにおける、ポンプ動力による熱媒体流量検知のフローチャートを示す図である。
まず、給湯ユニット310の制御装置320は、ポンプ315に印加される電圧の電圧情報、電流情報、ポンプ回転数情報とを取得する(S11)。その後、制御装置320は電力値算出処理(S12)を行う。すなわち、制御装置320は、ステップS11で取得した情報に基づいてポンプ315の動力である電力値を算出する。電力値は電圧と電流の積であるが、ポンプ仕様に応じて単相/3相および力率COSφ等を考慮して算出すればよい。そして、制御装置320は、動力と、ポンプ回転数と、上記図2に示したような動力曲線とに基づき熱媒体流量値を算出する(S13)。なお、回転数ごとの動力曲線は予め制御装置320に記憶されている。
図6は、本発明の実施の形態に係る空調給湯複合システムにおける、熱媒体流量予測による熱媒体流量検知のフローチャートを示す図である。
まず、給湯ユニット310の制御装置320は、まず冷媒圧力、冷媒温度、熱媒体入口温度Twiおよび熱媒体出口温度Twoを検知する(S21)。その後、熱媒体流量の初期値を設定する(S22)。この初期値には、上述したように装置上可能な最低熱媒体流量を用いる。続いて制御装置320は上述したようにして冷媒側能力Qrを算出する能力算出処理(S23)を行う。そして、制御装置320は、能力算出処理で算出した冷媒側能力Qrに基づいて予測温度差ΔTpを上記(3)式で算出する(S24)。
Claims (8)
- 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、
冷媒-熱媒体熱交換器、給湯側絞り装置およびポンプが搭載された給湯ユニットとを備え、
前記給湯ユニットは、
前記給湯ユニットの熱媒体側出口の出口温度と目標温度との温度差が予め設定された設定値より小さい場合、前記出口温度を前記目標温度にするために必要な要求給湯能力と、前記熱源ユニットおよび前記給湯ユニットを循環する冷媒の温度および圧力を示す冷媒情報とに基づいて、前記出口温度が前記目標温度となるように前記給湯側絞り装置の開度を制御する制御装置
を備えた空調給湯複合システム。 - 前記制御装置は、前記要求給湯能力と前記冷媒情報とに基づいて必要冷媒循環量を算出し、前記必要冷媒循環量に基づいて前記給湯側絞り装置の開度を制御する請求項1記載の空調給湯複合システム。
- 前記制御装置は、前記出口温度が前記目標温度となるように前記給湯側絞り装置の開度を制御する前記制御である出口温度制御と、前記冷媒-熱媒体熱交換器の冷媒側出口の過冷却度が目標過冷却度となるように前記給湯側絞り装置を制御する過冷却制御とを、前記温度差に基づいて切り替えるようにしており、前記温度差が前記設定値以上の場合、前記過冷却制御を行う
請求項1または請求項2記載の空調給湯複合システム。 - 室内側熱交換器および室内側絞り装置とが搭載された室内ユニットをさらに有する
請求項1~請求項3のいずれか一項に記載の空調給湯複合システム。 - 前記給湯ユニットは、前記冷媒-熱媒体熱交換器の熱媒体流量を検知する流量センサーを備え、
前記制御装置は、前記流量センサーで得た前記熱媒体流量に基づいて前記要求給湯能力を算出する
請求項1~請求項4のいずれか一項に記載の空調給湯複合システム。 - 前記制御装置は、前記ポンプの動力と回転数とに基づいて前記冷媒-熱媒体熱交換器の熱媒体流量を算出し、算出した前記熱媒体流量に基づいて前記要求給湯能力を算出する
請求項1~請求項4のいずれか一項に記載の空調給湯複合システム。 - 前記制御装置は、前記冷媒-熱媒体熱交換器の熱媒体側の出入口温度差である熱媒体温度差を制御間隔ごとに取得しており、取得した各熱媒体温度差に基づいて前記冷媒-熱媒体熱交換器の熱媒体流量を算出し、算出した前記熱媒体流量に基づいて前記要求給湯能力を算出する
請求項1~請求項4のいずれか一項に記載の空調給湯複合システム。 - 前記給湯ユニットは、前記冷媒-熱媒体熱交換器を放熱器として機能させる加熱運転と、前記冷媒-熱媒体熱交換器を蒸発器として機能させる冷却運転とを行う
請求項1~請求項7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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---|---|---|---|---|
CN108800563A (zh) * | 2018-06-25 | 2018-11-13 | 佛山光腾新能源股份有限公司 | 一种超低温热泵热水器及其电子膨胀阀控制方法 |
CN114738824A (zh) * | 2022-03-07 | 2022-07-12 | 华电湖北发电有限公司武昌热电分公司 | 集中供热系统能耗调节方法、设备、存储介质及装置 |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS58120054A (ja) * | 1982-01-09 | 1983-07-16 | 三菱電機株式会社 | 空気調和装置 |
JPS59109748A (ja) * | 1982-12-14 | 1984-06-25 | 三菱電機株式会社 | 空気調和機 |
JPH0833242B2 (ja) * | 1987-04-13 | 1996-03-29 | 三菱重工業株式会社 | 冷凍装置 |
JP2004003827A (ja) * | 2002-04-04 | 2004-01-08 | Matsushita Electric Ind Co Ltd | 冷凍サイクル装置 |
JP2007526436A (ja) * | 2004-03-04 | 2007-09-13 | キャリア コーポレイション | 冷媒システムの多変量制御 |
JP2009052880A (ja) * | 2004-03-29 | 2009-03-12 | Mitsubishi Electric Corp | ヒートポンプ給湯機 |
WO2012164608A1 (ja) * | 2011-05-31 | 2012-12-06 | 三菱電機株式会社 | 空調給湯複合システム |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0833242A (ja) * | 1994-07-18 | 1996-02-02 | Nissan Motor Co Ltd | マイクロ波送受電装置およびその艤装方法 |
-
2015
- 2015-12-24 GB GB1806389.1A patent/GB2561095B/en active Active
- 2015-12-24 WO PCT/JP2015/086090 patent/WO2017109905A1/ja active Application Filing
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS58120054A (ja) * | 1982-01-09 | 1983-07-16 | 三菱電機株式会社 | 空気調和装置 |
JPS59109748A (ja) * | 1982-12-14 | 1984-06-25 | 三菱電機株式会社 | 空気調和機 |
JPH0833242B2 (ja) * | 1987-04-13 | 1996-03-29 | 三菱重工業株式会社 | 冷凍装置 |
JP2004003827A (ja) * | 2002-04-04 | 2004-01-08 | Matsushita Electric Ind Co Ltd | 冷凍サイクル装置 |
JP2007526436A (ja) * | 2004-03-04 | 2007-09-13 | キャリア コーポレイション | 冷媒システムの多変量制御 |
JP2009052880A (ja) * | 2004-03-29 | 2009-03-12 | Mitsubishi Electric Corp | ヒートポンプ給湯機 |
WO2012164608A1 (ja) * | 2011-05-31 | 2012-12-06 | 三菱電機株式会社 | 空調給湯複合システム |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN108800563A (zh) * | 2018-06-25 | 2018-11-13 | 佛山光腾新能源股份有限公司 | 一种超低温热泵热水器及其电子膨胀阀控制方法 |
CN114738824A (zh) * | 2022-03-07 | 2022-07-12 | 华电湖北发电有限公司武昌热电分公司 | 集中供热系统能耗调节方法、设备、存储介质及装置 |
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