WO2012111063A1 - 冷凍サイクル装置及び冷凍サイクル制御方法 - Google Patents
冷凍サイクル装置及び冷凍サイクル制御方法 Download PDFInfo
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- WO2012111063A1 WO2012111063A1 PCT/JP2011/052984 JP2011052984W WO2012111063A1 WO 2012111063 A1 WO2012111063 A1 WO 2012111063A1 JP 2011052984 W JP2011052984 W JP 2011052984W WO 2012111063 A1 WO2012111063 A1 WO 2012111063A1
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- hot water
- water supply
- heat
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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
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Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
- 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
- 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
- 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
- F24D2200/12—Heat pump
- F24D2200/123—Compression type heat pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/021—Indoor unit or outdoor unit with auxiliary heat exchanger not forming part of the indoor or outdoor unit
- F25B2313/0214—Indoor unit or outdoor unit with auxiliary heat exchanger not forming part of the indoor or outdoor unit the auxiliary heat exchanger being used parallel to the indoor unit during heating operation
-
- 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
- F25B2600/02—Compressor control
- F25B2600/021—Inverters therefor
-
- 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
- F25B2700/2116—Temperatures of a condenser
- F25B2700/21161—Temperatures of a condenser of the fluid heated by the condenser
-
- 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
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Definitions
- JP 2007-147246 A Japanese Patent No. 3855985 JP 2004-340532 A JP 2003-139391 A JP 2007-218463 A
- boiling is performed in accordance with the usage state of heat to improve energy saving. Specifically, one day is divided into a plurality of time zones, and the heating operation control is performed in accordance with the required heat amount obtained based on the past heat amount use results in each divided time zone. By doing so, it is possible to shorten the time from storing the amount of heat in the hot water storage tank to using it, and to suppress the heat radiation amount, so that energy saving is improved.
- the operation method of the hot water supply apparatus is not controlled based on the past use of heat, and the operation frequency of the compressor becomes high during the hot water supply operation, resulting in an inefficient operation.
- the boiling operation time is estimated from the amount of boiling per unit time, the capacity of the hot water storage tank, and the amount of remaining hot water.
- the operation time for completing the heat storage in the hot water storage tank can be obtained by using this known technology, but the hot water supply operation time and the hot water start time for preventing the hot water shortage with the predetermined hot water supply capacity cannot be obtained.
- the hot water supply operation cannot be performed with high operating efficiency.
- the amount of hot water stored in the night is set by predicting the cooling operation time of the next day from the amount of hot water used on the previous day and the cooling operation time and using the cooling exhaust heat.
- the amount of hot water to be boiled in it is possible to reduce power consumption and prevent the hot water tank from running out.
- heat storage is performed at night, a heat dissipation loss occurs and energy saving performance deteriorates.
- the present invention calculates the minimum hot water supply capacity target required to avoid running out of hot water from the user's past hot water usage record, the amount of heat stored in the hot water storage tank and the hot water supply time, and hot water supply operation so that the hot water supply capacity becomes the target value Like to do. Accordingly, it is an object to realize high operating efficiency by lowering the operating frequency of the compressor according to the hot water supply capacity.
- the refrigeration cycle apparatus of the present invention is In the refrigeration cycle apparatus for circulating the refrigerant, A compressor capable of operating frequency control, a first radiator for supplying heat to the tank water, which is water stored in a hot water storage tank, by the refrigerant, a first decompression mechanism, and a first evaporator A refrigeration cycle mechanism in which the refrigerant circulates in the order of the compressor, the first radiator, the first decompression mechanism, and the first evaporator; A control device, The controller is A storage unit capable of storing control period information indicating a preset control period and storing other information, A supply heat amount indicating the amount of heat supplied to the tank water from the first radiator based on a predetermined time is calculated based on a predetermined supply heat amount calculation rule, and the calculated supply heat amount is stored in the storage unit.
- FIG. 1 is a refrigerant circuit configuration diagram of an air conditioning and hot water supply complex system 100 (refrigeration cycle apparatus) according to Embodiment 1.
- the relationship of the size of each component may be different from the actual one.
- the unit of the symbol is written in []. In the case of dimensionless (no unit), it is expressed as [-].
- FIG. 2 is a schematic diagram illustrating the flow of water from the hot water supply unit 304 to the tank unit 305 of the air conditioning and hot water supply complex system 100.
- FIG. 3 is a schematic diagram showing various sensors and the control device 110 of the air conditioning and hot water supply complex system 100.
- This air conditioning and hot water supply combined system 100 is a three-pipe multi-function system capable of simultaneously processing the cooling operation or heating operation selected in the utilization unit and the hot water supply operation in the hot water supply unit by performing a vapor compression refrigeration cycle operation. It is a system air conditioning hot water supply complex system.
- the combined air conditioning and hot water supply system 100 includes a heat source unit 301, a branch unit 302, use units 303a and 303b, a hot water supply unit 304, and a tank unit 305.
- the heat source unit 301 and the branch unit 302 are connected by a liquid extension pipe 7 that is a refrigerant pipe and a gas extension pipe 13 that is a refrigerant pipe.
- One of the hot water supply units 304 is connected to the heat source unit 301 via a hot water supply gas extension pipe 16 that is a refrigerant pipe, and the other is connected to the branch unit 302 via a hot water supply liquid pipe 19 that is a refrigerant pipe.
- the use units 303a and 303b and the branch unit 302 are connected by indoor gas pipes 12a and 12b that are refrigerant pipes and indoor liquid pipes 9a and 9b that are refrigerant pipes.
- the tank unit 305 and the hot water supply unit 304 are connected by a water upstream pipe 22 that is a water pipe and a water downstream pipe 23 that is a water pipe.
- the water upstream pipe 22 and the water downstream pipe 23 are water flow paths that serve as water flow paths that flow into the plate water heat exchanger 17 from the hot water storage tank 27, pass through the plate water heat exchanger 17, and return to the hot water storage tank 27.
- the air conditioning and hot water supply complex system 100 includes a control device 110 as shown in FIG.
- the control device 110 includes a measurement unit 101, a calculation unit 102, a control unit 103, a storage unit 104, and a clock unit 105. All the control described below is executed by the control device 110.
- the control device 110 is disposed in the heat source unit 301, but is an example. The place where the control device 110 is arranged is not limited.
- the operation mode of the heat source unit 301 is determined according to the hot water supply request of the connected hot water supply unit 304 and the presence or absence of the cooling load or heating load of the use units 303a and 303b. .
- the air conditioning and hot water supply complex system 100 can execute the following five operation modes. That is, they are the cooling operation mode A, the heating operation mode B, the hot water supply operation mode C, the heating / hot water simultaneous operation mode D, and the cooling / hot water simultaneous operation mode E.
- the cooling operation mode A is an operation mode of the heat source unit 301 when there is no hot water supply request signal (also referred to as a hot water supply request) and the use units 303a and 303b perform the cooling operation.
- the heating operation mode B is an operation mode of the heat source unit 301 when there is no hot water supply request and the use units 303a and 303b perform the heating operation.
- Hot water supply operation mode C is an operation mode of the heat source unit 301 when there is no air conditioning load and the hot water supply unit 304 executes the hot water supply operation.
- the heating / hot water simultaneous operation mode D is an operation mode of the heat source unit 301 in the case where the simultaneous operation of the heating operation by the use units 303a and 303b and the hot water supply operation by the hot water supply unit 304 is executed.
- Cooling and hot water simultaneous operation mode E is an operation mode of the heat source unit 301 when simultaneous operation of the cooling operation by the use units 303a and 303b and the hot water supply operation by the hot water supply unit 304 is executed.
- the utilization units 303 a and 303 b are connected to the heat source unit 301 via the branch unit 302.
- the use units 303a and 303b are installed in a place where conditioned air can be blown out to the air-conditioning target area (for example, by embedding or hanging on an indoor ceiling, or hanging on a wall surface).
- the utilization units 303a and 303b are connected to the heat source unit 301 via the branch unit 302, the liquid extension pipe 7 and the gas extension pipe 13, and constitute a part of the refrigerant circuit.
- the utilization units 303a and 303b include an indoor refrigerant circuit that forms part of the refrigerant circuit.
- This indoor refrigerant circuit is composed of indoor heat exchangers 10a and 10b as use side heat exchangers.
- the use units 303a and 303b are provided with indoor fans 11a and 11b for supplying conditioned air after heat exchange with the refrigerant of the indoor heat exchangers 10a and 10b to an air-conditioning target area such as a room.
- the indoor heat exchangers 10a and 10b can be constituted by, for example, a cross fin type fin-and-tube heat exchanger constituted by heat transfer tubes and a large number of fins. Moreover, you may comprise the indoor heat exchangers 10a and 10b with a microchannel heat exchanger, a shell and tube type heat exchanger, a heat pipe type heat exchanger, or a double pipe type heat exchanger.
- the indoor heat exchangers 10a and 10b function as a refrigerant evaporator to cool the air in the air-conditioning target area, and the heating operation mode B In some cases, it functions as a refrigerant condenser (or radiator) to heat the air in the air-conditioned area.
- the indoor blowers 11a and 11b have a function of supplying indoor air to the air-conditioning target area as conditioned air after the indoor air is sucked into the use units 303a and 303b and the indoor air is heat-exchanged with the refrigerant by the indoor heat exchangers 10a and 10b.
- Indoor fan 11a, 11b is comprised by what can change the flow volume of the conditioned air supplied to indoor heat exchanger 10a, 10b, for example, fans, such as a centrifugal fan and a multiblade fan, drive this fan.
- fans such as a centrifugal fan and a multiblade fan
- a motor including a DC fan motor is provided.
- the utilization units 303a and 303b are provided with various sensors described below.
- Indoor liquid temperature sensors 206a and 206b that are provided on the liquid side of the indoor heat exchangers 10a and 10b (the liquid side when operating as a radiator) and detect the temperature of the liquid refrigerant
- Indoor gas temperature sensors 207a and 207b that are provided on the gas side of the indoor heat exchangers 10a and 10b (the gas side when operating as a radiator) and detect the temperature of the gas refrigerant
- Indoor suction temperature sensors 208a, 208b that are provided on the indoor air intake side of the utilization units 303a, 303b and detect the temperature of the indoor air flowing into the units;
- control part 103 which functions as a normal operation control means which performs normal operation including air_conditionaing
- the hot water supply unit 304 is connected to the heat source unit 301 via the branch unit 302. As shown in FIG. 2, the hot water supply unit 304 has a function of supplying hot water to a tank unit 305 installed, for example, outdoors and heating the water in the hot water storage tank 27 to boil hot water.
- the plate water heat exchanger 17 of the hot water supply unit 304 includes a connection part 24 (water inflow pipe connection part) connected to the water upstream pipe 22 (water inflow pipe) and a connection part connected to the water downstream pipe 23 (water outflow pipe). 25 (water outflow pipe connection portion).
- One of the hot water supply units 304 is connected to the heat source unit 301 via the hot water supply gas extension pipe 16, and the other is connected to the branch unit 302 via the hot water supply liquid pipe 19. It constitutes a part of the refrigerant circuit.
- the hot water supply unit 304 includes a hot water supply side refrigerant circuit that constitutes a part of the refrigerant circuit.
- This hot water supply side refrigerant circuit has a plate water heat exchanger 17 as a hot water supply side heat exchanger as an element function.
- the hot water supply unit 304 is provided with a water supply pump 18 for supplying water for supplying hot water after heat exchange with the refrigerant of the plate water heat exchanger 17 to the tank unit 305 and the like.
- the plate water heat exchanger 17 functions as a refrigerant condenser in the hot water supply operation mode C executed by the hot water supply unit 304 and heats water supplied by the water supply pump 18.
- the water supply pump 18 supplies water into the hot water supply unit 304, exchanges heat with the plate water heat exchanger 17 to make hot water, supplies hot water into the tank unit 305, and supplies water in the hot water storage tank 27 (tank water). ) And heat exchange function.
- the hot water supply unit 304 can exchange heat between the water supplied by the water supply pump 18 and the refrigerant flowing through the plate water heat exchanger 17, and the water supplied by the water supply pump 18 and hot water storage. Heat exchange with the water in the tank 27 is possible.
- the flow rate of water supplied to the plate water heat exchanger 17 is variable.
- the hot water supply unit 304 is provided with various sensors described below.
- a hot water supply liquid temperature sensor 209 that is provided on the liquid side of the plate water heat exchanger 17 and detects the temperature of the liquid refrigerant;
- An inlet water temperature sensor 210 inlet temperature sensor
- an outlet water temperature sensor 211 outlet temperature sensor
- An intermediate water flow meter 219 FOG. 2 that is provided at the water inflow portion and detects the volume flow rate of the inflowing water;
- the operation of the water supply pump 18 is controlled by the control unit 103 that functions as normal operation control means for performing normal operation including the hot water supply operation mode of the hot water supply unit 304.
- the tank unit 305 is installed outdoors, for example, and has a function of storing hot water boiled up by the hot water supply unit 304.
- the tank unit 305 has a hot water storage tank 27 for storing hot water as shown in FIG. One is connected to the hot water supply unit 304 via the water upstream pipe 22, and the other is connected to the hot water supply unit 304 via the water downstream pipe 23. It is composed.
- the hot water storage tank 27 is a full-water type. When the user consumes hot water, the hot water is discharged from the upper part of the tank, and city water is supplied from the lower part of the tank according to the amount.
- the water supplied by the hot water supply unit 304 in the hot water supply unit 304 is heated by the refrigerant in the plate water heat exchanger 17 to become hot water, and flows into the hot water storage tank 27 via the water downstream pipe 23.
- the hot water is not mixed with the water in the hot water storage tank 27, and becomes cold water by exchanging heat with water in the hot water storage tank 27 as intermediate water. Thereafter, it flows out of the hot water storage tank 27, flows into the hot water supply unit 304 again via the water upstream pipe 22, is supplied again with the water supply pump 18, and then becomes hot water with the plate water heat exchanger 17. In such a process, hot water is boiled in the tank unit 305.
- the method of heating the water in the tank unit 305 is not limited to the heat exchange method using intermediate water as in the first embodiment, and the water in the hot water storage tank 27 is directly flowed through the pipe and heated by the plate water heat exchanger 17.
- a heating method may be employed in which the hot water is exchanged and returned to the hot water storage tank 27 again.
- the tank unit 305 is provided with various sensors shown below.
- a first hot water tank water temperature sensor 212 that is provided on the side surface of the hot water storage tank 27 and detects the hot water temperature on the upper side surface of the hot water storage tank 27;
- a second hot water tank water temperature sensor 213 that is provided on the side surface of the hot water tank 27 and detects the hot water temperature on the lower side surface of the first hot water tank water temperature sensor 212 of the hot water tank 27;
- a third hot water storage tank water temperature sensor 214 which is provided on the tank side surface of the hot water storage tank 27 and detects the hot water temperature on the lower side surface of the second hot water storage tank water temperature sensor 213 of the hot water storage tank 27;
- (4) a fourth hot water storage tank water temperature sensor 215 which is provided on the side surface of the hot water storage tank 27 and detects the hot water temperature on the lower side surface of the third hot water storage tank water temperature sensor 214 of the hot water storage tank 27;
- a hot water storage tank outlet temperature sensor 216 that is provided in
- the heat source unit 301 is installed outdoors, for example, and is connected to the utilization units 303 a and 303 b via the liquid extension pipe 7, the gas extension pipe 13, and the branch unit 302. Further, it is connected to the hot water supply unit 304 through the hot water supply gas extension pipe 16, the liquid extension pipe 7 and the branch unit 302, and constitutes a part of the refrigerant circuit in the air conditioning and hot water supply complex system 100.
- the heat source unit 301 includes an outdoor refrigerant circuit that constitutes a part of the refrigerant circuit.
- This outdoor refrigerant circuit includes a compressor 1 for compressing refrigerant, a four-way valve 3 for switching the direction of refrigerant flow according to the outdoor operation mode, and three solenoid valves (first discharge solenoid valve 2 and second discharge solenoid).
- the valve 15, the low-pressure equalizing solenoid valve 21), the outdoor heat exchanger 4 as a heat source side heat exchanger, and an accumulator 14 for storing excess refrigerant are included as element devices.
- the heat source unit 301 includes an outdoor fan 5 for supplying air to the outdoor heat exchanger 4 and an outdoor pressure reducing mechanism 6 for controlling the distribution flow rate of the refrigerant as a heat source side pressure reducing mechanism.
- the compressor 1 sucks refrigerant and compresses the refrigerant to a high temperature and high pressure state.
- the compressor 1 mounted in the first embodiment is capable of varying the operating capacity, and is constituted by, for example, a positive displacement compressor driven by a motor (not shown) controlled by an inverter. Yes.
- the case where there is only one compressor 1 is shown as an example.
- the present invention is not limited to this, and two or more units are used depending on the number of connected units 303a and 303b and hot water supply units 304.
- the compressors 1 may be connected in parallel. Further, the discharge side pipe connected to the compressor 1 is branched in the middle, and one side extends to the gas extension pipe 13 via the four-way valve 2 and the other side extends to the hot water supply gas via the second discharge electromagnetic valve 15. Each is connected to the pipe 16.
- the four-way valve 3, the first discharge solenoid valve 2, the second discharge solenoid valve 15, and the low pressure equalizing solenoid valve 21 have a function as a flow path switching device that switches the direction of refrigerant flow according to the operation mode of the heat source unit 301. ing.
- FIG. 4 shows the operation contents of the four-way valve and the solenoid valve with respect to the operation mode. “Solid line” and “broken line” displayed in FIG. 4 mean “solid line” and “broken line” indicating the switching state of the four-way valve 3 shown in FIG.
- the four-way valve 3 is switched to become a “solid line”. That is, in the case of the cooling operation mode A and the cooling hot water supply simultaneous operation mode E, in order for the indoor heat exchangers 10a and 10b to function as an evaporator of the refrigerant compressed in the compressor 1, the suction side of the compressor 1 and the indoor It is switched to connect the gas side of the heat exchangers 10a, 10b. In the case of the heating operation mode B, the hot water supply operation mode C, and the heating and hot water simultaneous operation mode D, the four-way valve 3 is switched so as to be a “broken line”.
- the intake of the compressor 1 is performed in order to cause the outdoor heat exchanger 4 to function as an evaporator of the refrigerant compressed in the compressor 1.
- the side is switched to connect the gas side of the outdoor heat exchanger 4.
- the first discharge solenoid valve 2 is switched to be “open”. That is, in the cooling operation mode A, in order to make the outdoor heat exchanger 4 function as a condenser for the refrigerant compressed in the compressor 1, the discharge side of the compressor 1 and the gas side of the outdoor heat exchanger 4 are connected to perform heating operation.
- the mode B and the heating / hot water simultaneous operation mode D in order for the indoor heat exchangers 10a and 10b to function as a condenser for the refrigerant compressed in the compressor 1, the discharge side of the compressor 1 and the indoor heat exchanger 10a , 10b to be connected to the gas side.
- the hot water supply operation mode C and the heating / hot water simultaneous operation mode D the operation is switched to “closed”.
- the second discharge solenoid valve 15 is switched to “open”. That is, in the case of the hot water supply operation mode C, the heating / hot water simultaneous operation mode D, and the cooling / hot water simultaneous operation mode E, the compressor 1 is used in order to cause the plate water heat exchanger 17 to function as a refrigerant condenser to be compressed in the compressor 1. And the gas side of the plate water heat exchanger 17 are connected. In the case of the cooling operation mode A and the heating operation mode B, the operation is switched to “closed”.
- the low pressure equalizing solenoid valve 21 is switched to be “open”. That is, in the case of the cooling hot water supply simultaneous operation mode E, the suction side of the compressor 1 and the gas side of the outdoor heat exchanger 4 are connected to bring the outdoor heat exchanger 4 into a low pressure state. Further, in the case of the cooling operation mode A, the heating operation mode B, the hot water supply operation mode C, and the heating and hot water simultaneous operation mode D, the low pressure equalizing solenoid valve 21 is switched to be “closed”.
- the outdoor heat exchanger 4 has a gas side connected to the four-way valve 3 and a liquid side connected to the outdoor decompression mechanism 6.
- the outdoor heat exchanger 4 can be composed of, for example, a cross fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins.
- the outdoor heat exchanger 4 functions as a refrigerant condenser and cools the refrigerant in the cooling operation mode A, and includes a heating operation mode B, a hot water supply operation mode C, a heating / hot water simultaneous operation mode D, and a cooling / hot water simultaneous operation mode.
- E it functions as a refrigerant evaporator and heats the refrigerant.
- the outdoor blower 5 has a function of sucking outdoor air into the heat source unit 301 and exchanging the outdoor air with the outdoor heat exchanger 4 and then discharging the outdoor air to the outside. That is, in the heat source unit 301, heat exchange can be performed between the outdoor air taken in by the outdoor fan 5 and the refrigerant flowing through the outdoor heat exchanger 4.
- the outdoor blower 5 is configured to be capable of changing the flow rate of air supplied to the outdoor heat exchanger 4, and includes a fan such as a propeller fan and a motor that drives the fan, for example, a DC fan motor. It has.
- the accumulator 14 is provided on the suction side of the compressor 1 and stores the liquid refrigerant when the abnormality occurs in the air-conditioning and hot water supply complex system 100 or during the transient response of the operation state when the operation control is changed. 1 has a function of preventing liquid back to 1.
- the heat source unit 301 is provided with various sensors shown below.
- a high-pressure sensor 201 provided on the discharge side of the compressor 1 for detecting a high-pressure side pressure
- a discharge temperature sensor 202 provided on the discharge side of the compressor 1 for detecting the discharge temperature
- An outdoor gas temperature sensor 203 that is provided on the gas side of the outdoor heat exchanger 4 and detects the gas refrigerant temperature
- An outdoor liquid temperature sensor 204 that is provided on the liquid side of the outdoor heat exchanger 4 and detects the temperature of the liquid refrigerant
- An outdoor air temperature sensor 205 provided on the outdoor air inlet side of the heat source unit 301 and detecting the temperature of the outdoor air flowing into the unit;
- the operations of the compressor 1, the first discharge solenoid valve 2, the four-way valve 3, the outdoor blower 5, the outdoor pressure reducing mechanism 6, the second discharge solenoid valve 15, and the low pressure equalizing solenoid valve 21 are the cooling operation mode A and the heating operation. It is controlled by the control unit 103 that functions as normal operation control means for performing normal operation including mode B, hot water supply operation mode C, heating / hot water simultaneous operation mode D, and cooling / hot water simultaneous operation mode E.
- the branch unit 302 is installed indoors, for example, is connected to the heat source unit 301 via the liquid extension pipe 7 and the gas extension pipe 13, and is a utilization unit via the indoor liquid pipes 9a and 9b and the indoor gas pipes 12a and 12b.
- the branch unit 302 has a function of controlling the flow of the refrigerant according to the operation required for the use units 303a and 303b and the hot water supply unit 304.
- the branch unit 302 includes a branch refrigerant circuit that constitutes a part of the refrigerant circuit.
- This branch refrigerant circuit has, as element devices, indoor decompression mechanisms 8a and 8b for controlling the distribution flow rate of the refrigerant as a use side decompression mechanism and a hot water supply decompression mechanism 20 for controlling the distribution flow rate of the refrigerant. .
- the indoor decompression mechanisms 8a and 8b are provided in the indoor liquid pipes 9a and 9b.
- the hot water supply pressure reducing mechanism 20 is provided in the hot water supply liquid pipe 19 in the branch unit 302.
- the indoor decompression mechanisms 8a and 8b function as decompression valves and expansion valves, decompress the refrigerant flowing through the liquid extension pipe 7 in the cooling operation mode A, and flow through the hot water supply decompression mechanism 20 in the cooling hot water supply simultaneous operation mode E. Is expanded under reduced pressure.
- the refrigerant flowing through the indoor liquid pipes 9a and 9b is decompressed and expanded.
- the hot water supply depressurization mechanism 20 has a function as a pressure reducing valve or an expansion valve, and decompresses and expands the refrigerant flowing through the hot water supply liquid pipe 19 in the hot water supply operation mode C and the heating hot water supply simultaneous operation mode D.
- the indoor decompression mechanisms 8a and 8b and the hot water supply decompression mechanism 20 may be configured with a controllable flow rate control means such as an electronic expansion valve, or an inexpensive refrigerant flow rate control means such as a capillary tube, which can be variably controlled.
- the operation of the hot water supply pressure reducing mechanism 20 is controlled by the control unit 103 of the control device 110 functioning as normal operation control means for performing normal operation including hot water supply operation of the hot water supply unit 304 as shown in FIG. 3 (FIG. 3). reference).
- the operation of the indoor decompression mechanisms 8a and 8b is controlled by the control unit 103 that functions as normal operation control means for performing normal operation including cooling operation and heating operation of the utilization units 303a and 303b.
- various amounts detected by various temperature sensors and pressure sensors are input to the measurement unit 101 and processed by the calculation unit 102.
- the control part 103 is based on the process result of the calculating part 102, the compressor 1, the 1st discharge electromagnetic valve 2, the four-way valve 3, the outdoor air blower 5, the outdoor pressure reduction mechanism 6, the indoor pressure reduction mechanism 8a, 8b, indoor blowers 11, 11b, second discharge solenoid valve 15, water supply pump 18, and hot water supply pressure reducing mechanism 20 are controlled.
- the operation of the air conditioning and hot water supply complex system 100 is centrally controlled by the control device 110 including the measurement unit 101, the calculation unit 102, and the control unit 103.
- the control apparatus 110 can be comprised with a microcomputer.
- the calculation formula described in the first embodiment is calculated by the calculation unit 102, and the control unit 103 controls each device such as the compressor 1 according to the calculation result.
- the storage unit 104 stores data used by the calculation unit 102, calculation results, and the like.
- the clock unit 105 outputs the current time.
- the operation mode (for example, a cooling request signal for requesting the cooling operation of the utilization units 303a and 303b) via the remote controller, a hot water supply request signal described later, an instruction such as a set temperature, and detection information by various sensors.
- the control unit 103 The operating frequency of the compressor 1, Switching of the first discharge solenoid valve 2; Switching of the four-way valve 3, Number of rotations of outdoor fan 5 (including ON / OFF) Opening degree of the outdoor decompression mechanism 6, Opening degree of the indoor decompression mechanism 8a, 8b, Number of rotations (including ON / OFF) of the indoor fans 11a and 11b, Switching of the second discharge solenoid valve 15; The rotation speed of the water supply pump 18 (including ON / OFF), Opening degree of the hot water supply pressure reducing mechanism 20, Controls the switching of the low pressure equalizing solenoid valve 21, Execute each operation mode.
- the measurement unit 101, the calculation unit 102, the control unit 103, the storage unit 104, and the clock unit 105 may be provided integrally or may be provided separately.
- the measurement unit 101, the calculation unit 102, the control unit 103, the storage unit 104, and the clock unit 105 may be provided in any unit.
- the measurement unit 101, the calculation unit 102, the control unit 103, the storage unit 104, and the clock unit 105 may be provided for each unit.
- the air conditioning and hot water supply complex system 100 includes the heat source unit 301, the branch unit 302, the use units 303a and 303b, and the hot water supply unit 304 in accordance with the air conditioning load required for the use units 303a and 303b and the hot water supply request required for the hot water supply unit 304.
- a cooling operation mode A, a heating operation mode B, a hot water supply operation mode C, a heating / hot water simultaneous operation mode D, and a cooling / hot water simultaneous operation mode E are executed.
- the four-way valve 3 In the cooling operation mode A, the four-way valve 3 is in a state indicated by a solid line, that is, the discharge side of the compressor 1 is connected to the gas side of the outdoor heat exchanger 4.
- the first discharge solenoid valve 2 is open, the second discharge solenoid valve 15 is closed, and the low pressure equalizing solenoid valve 21 is closed. Further, the hot water supply pressure reducing mechanism 20 has a minimum opening (fully closed).
- the outdoor decompression mechanism 6 is controlled to the maximum opening (fully open).
- the refrigerant flowing into the branch unit 302 is decompressed by the indoor decompression mechanisms 8a and 8b, becomes a low-pressure gas-liquid two-phase refrigerant, flows out of the branch unit 302, and is used via the indoor liquid pipes 9a and 9b. It flows into the units 303a and 303b.
- the indoor decompression mechanisms 8a and 8b are configured to eliminate the temperature difference (cooling room temperature difference) obtained by subtracting the set temperature from the indoor suction temperature detected by the indoor suction temperature sensors 208a and 208b in the use units 303a and 303b. Be controlled. Therefore, the refrigerant
- the operating frequency of the compressor 1 is controlled by the control unit 103 so that the evaporation temperature becomes a predetermined value according to the maximum temperature difference in the cooling chamber.
- the evaporation temperature is a temperature detected by the indoor liquid temperature sensors 206a and 206b.
- the cooling unit maximum temperature difference among the usage units 303a and 303b is the usage unit 303a having the largest temperature difference (cooling room temperature difference) obtained by subtracting the set temperature from the indoor suction temperature sensors 208a and 208b detected by the indoor suction temperature sensors 208a and 208b. , 303b.
- the control unit 103 controls the evaporation temperature to be a predetermined value according to the maximum temperature difference in the cooling chamber.
- the air volume of the outdoor blower 5 is controlled by the control unit 103 so that the condensation temperature becomes a predetermined value according to the outside air temperature detected by the outside air temperature sensor 205.
- the condensation temperature is a saturation temperature calculated by the pressure detected from the high pressure sensor 201.
- Heating operation mode B In the heating operation mode B, the four-way valve 3 is indicated by a broken line, that is, the discharge side of the compressor 1 is connected to the gas side of the indoor heat exchangers 10a and 10b, and the suction side of the compressor 1 is the gas of the outdoor heat exchanger 4 Connected to the side.
- the first discharge solenoid valve 2 is open, the second discharge solenoid valve 15 is closed, and the low pressure equalizing solenoid valve 21 is closed. Further, the hot water supply pressure reducing mechanism 20 is fully closed.
- the compressor 1, the outdoor fan 5, the indoor fans 11a and 11b, and the water supply pump 18 are started. Then, the low-pressure gas refrigerant is sucked into the compressor 1 and compressed to become a high-temperature / high-pressure gas refrigerant. Thereafter, the high-temperature and high-pressure gas refrigerant flows through the first discharge electromagnetic valve 2 and the four-way valve 3.
- the refrigerant that has flowed into the four-way valve 3 flows out of the heat source unit 301 and flows to the branch unit 302 via the gas extension pipe 13. Then, it flows into utilization unit 303a, 303b via indoor gas piping 12a, 12b.
- the refrigerant flowing into the utilization units 303a and 303b flows into the indoor heat exchangers 10a and 10b, exchanges heat with the indoor air supplied by the indoor fans 11a and 11b, and condenses to become a high-pressure liquid refrigerant. It flows out of the exchangers 10a and 10b.
- the refrigerant that has heated the indoor air in the indoor heat exchangers 10a and 10b flows out of the use units 303a and 303b, flows into the branch unit 302 via the indoor liquid pipes 9a and 9b, and is discharged by the indoor decompression mechanisms 8a and 8b.
- the pressure is reduced to become a low-pressure gas-liquid two-phase or liquid-phase refrigerant. Thereafter, it flows out from the branch unit 302.
- the indoor decompression mechanisms 8a and 8b are controlled in the use units 303a and 303b so that there is no temperature difference (heating room temperature difference) obtained by subtracting the indoor set temperature from the indoor suction temperature detected by the indoor suction temperature sensors 208a and 208b. The Therefore, the refrigerant
- the operating frequency of the compressor 1 is controlled by the control unit 103 so that the condensation temperature becomes a predetermined value according to the maximum temperature difference in the heating room.
- the method for obtaining the condensation temperature is the same as in the cooling operation.
- the heating room maximum temperature difference is the maximum use of the temperature difference obtained by subtracting the indoor set temperature from the room suction temperature detected by the room suction temperature sensors 208a and 208b among the use units 303a and 303b (heating room temperature difference). This is the temperature difference between the heating units in the units 303a and 303b.
- the air volume of the outdoor fan 5 is controlled by the control unit 103 so that the evaporation temperature becomes a predetermined value according to the outside air temperature detected by the outside air temperature sensor 205.
- the evaporation temperature is obtained from the temperature detected by the outdoor liquid temperature sensor 204.
- Hot water supply operation mode C In the hot water supply operation mode C, the state where the four-way valve 3 is indicated by a broken line, that is, the discharge side of the compressor 1 is connected to the gas side of the plate water heat exchanger 17, and the suction side of the compressor 1 is the gas side of the outdoor heat exchanger 4. Connected to. The first discharge solenoid valve 2 is closed, the second discharge solenoid valve 15 is open, and the low pressure equalizing solenoid valve 21 is closed. Furthermore, the indoor decompression mechanisms 8a and 8b are fully closed.
- the refrigerant that has flowed into the second discharge solenoid valve 15 flows out of the heat source unit 301 and flows into the hot water supply unit 304 via the hot water supply gas extension pipe 16.
- the refrigerant flowing into the hot water supply unit 304 flows into the plate water heat exchanger 17 and is condensed by exchanging heat with the water supplied by the water supply pump 18 to become a high-pressure liquid refrigerant. 1).
- the refrigerant heated by the plate water heat exchanger 17 flows out of the hot water supply unit 304, then flows into the branch unit 302 via the hot water supply liquid pipe 19, and is decompressed by the hot water supply decompression mechanism 20 (first decompression mechanism). It becomes a low-pressure gas-liquid two-phase refrigerant. Then, it flows out from the branch unit 302 and flows into the heat source unit 301 through the liquid extension pipe 7.
- the hot water supply decompression mechanism 20 is controlled by the control unit 103 so that the degree of supercooling on the liquid side of the plate water heat exchanger 17 becomes a predetermined value.
- the degree of supercooling on the liquid side of the plate water heat exchanger 17 is obtained by calculating the saturation temperature (condensation temperature) from the pressure detected by the high pressure sensor 201 and subtracting the temperature detected by the hot water supply liquid temperature sensor 209. It is done.
- the hot water supply decompression mechanism 20 controls the flow rate of the refrigerant flowing through the plate water heat exchanger 17 so that the degree of supercooling of the refrigerant on the liquid side of the plate water heat exchanger 17 becomes a predetermined value.
- the high-pressure liquid refrigerant condensed in the plate water heat exchanger 17 is in a state having a predetermined degree of supercooling.
- the plate water heat exchanger 17 is supplied with a refrigerant having a flow rate corresponding to the hot water supply request required in the hot water use situation of the facility where the hot water supply unit 304 is installed.
- the refrigerant that has flowed out of the branch unit 302 flows into the heat source unit 301 via the liquid extension pipe 7, passes through the outdoor decompression mechanism 6, and then flows into the outdoor heat exchanger 4 (first evaporator).
- the opening degree of the outdoor decompression mechanism 6 is controlled to be fully open.
- the refrigerant flowing into the outdoor heat exchanger 4 is evaporated by exchanging heat with the outdoor air supplied by the outdoor blower 5 and becomes a low-pressure gas refrigerant.
- the air volume of the outdoor blower 5 is controlled by the control unit 103 so that the evaporation temperature becomes a predetermined value according to the outside air temperature detected by the outside temperature sensor 205.
- the evaporation temperature is a temperature detected by the outdoor liquid temperature sensor 204.
- the controller 103 In the conventional hot water supply operation mode, in order to avoid running out of hot water, the controller 103 is controlled to increase the operation frequency of the compressor 1. Thereby, high hot water supply capability can be ensured, and the water temperature in the hot water storage tank 27 can be raised to the set hot water supply temperature in the shortest time. However, the driving efficiency has deteriorated. Therefore, in order to achieve high operating efficiency while avoiding hot water shortages, the operating frequency of the compressor 1 is controlled to be low using past hot water usage records. Control of the operating frequency of the compressor performed based on the following formulas (1) to (7) is referred to as “hot water supply operation control”.
- the hot water supply operation time ⁇ t start [sec] (control period information) is stored in the storage unit 104 in advance (for example, 7200 sec).
- the amount of hot water used on the previous day that is, the maximum heat consumption L m (external supply heat amount) of the tank unit 305 and the time t m at that time are stored in the storage unit 104.
- the calculation unit 102 calculates the heat consumption of the tank unit 305 in one day every hour, and the time t m [h: mm] and the maximum heat consumption L m [kJ] at the time of the maximum heat consumption. Is stored in the storage unit 104 as a learning value (calculation unit as a hot water supply load storage unit).
- “learning” means a process in which the control device 110 (calculation unit 102) stores at least the target heat consumption and the generation time of the heat consumption in the storage unit 104.
- the time is set based on the time measurement of the clock unit 105.
- the calculation unit 102 calculates the amount of heat consumed in the hot water storage tank 27 at each time of the day by the formula (1) (external supply heat amount calculation rule) every hour (as hot water supply load calculation means). The calculation unit) is shown.
- T tankwi is the minimum value of the past detected temperature (for example, the minimum value of the detected temperature for the past three days) among the temperatures detected by the inlet water temperature sensor 210.
- T tankwo is a temperature detected by the outlet water temperature sensor 211, and is a temperature detected when water is discharged from the hot water storage tank 27.
- V wo is a volume flow rate detected by the tank water flow meter 218.
- the largest maximum heat consumption L m next among the amount of heat consumed for calculating from the equation (1), the time at that time is the largest consumer time t m.
- the maximum heat consumption L m and the maximum consumption time t m are information on the hot water supply load.
- the control unit 103 changes the hot water supply operation mode C. Start. That is, the control unit 103 controls the compressor 1 at the following operating frequency. In this case, the operating frequency (target operating frequency F m ) of the compressor 1 is determined by equations (2) to (6).
- T worm T wi + Q wm / ( ⁇ w ⁇ C p, w ⁇ V w ) (4)
- Equation (2) is derived from the definition shown in FIG.
- T wi is the water temperature flowing from the tank unit 305 to the hot water supply unit 304 (detected by the sensor 210)
- T wo is the water temperature flowing out of the hot water supply unit 304 toward the tank unit 305 (detected by the sensor 211)
- T tank1 is a temperature detected by the first hot water tank water temperature sensor 212
- T tank2 is the temperature detected by the second hot water storage tank water temperature sensor 213
- T tank3 is a temperature detected by the third hot water storage tank water temperature sensor 214
- T tank4 is the temperature detected by the fourth hot water tank water temperature sensor 215
- V w is the volume flow rate detected by the intermediate water flow meter 219 (water flow meter), It is.
- the calculation unit 102 calculates the hot water storage amount Li of the hot water storage tank 27 at the start of hot water supply according to the equation (2) (heat storage amount calculation rule) (the calculation unit 102 as a heat storage amount calculation unit).
- the hot water supply capacity target Q wm is calculated using the equation (3) based on the maximum heat consumption L m and the hot water supply operation time ⁇ t start which are the learning results of the previous day. That is, the target value of the hot water supply capability (heat dissipation capability) of the plate water heat exchanger 17 (first radiator) is set.
- the calculation unit 102 calculates the outlet water temperature target T wom in the case of the hot water supply capacity target Q wm according to the equation (4) using the inlet water temperature T wi (the calculation unit 102 as the outlet water temperature target calculation means).
- the outlet water temperature target T worm is the target temperature of the water flow detected by the outlet water temperature temperature sensor 211.
- the operating frequency change amount ⁇ F of the compressor 1 is obtained based on the equation (5).
- the target operating frequency F of the compressor 1 is calculated according to the equation (6). Calculate m .
- control part 103 can perform hot-water supply operation
- the maximum heat consumption L m and the maximum consumption time t m are updated every day.
- learning may be performed from the amount of hot water used for two days or one week. Good.
- the maximum heat consumption L m may be obtained as an average of the plurality of days, or the maximum consumption time t m may be obtained at the time when the largest amount of learning is learned.
- the maximum heat consumption Lm and the maximum consumption time tm may be obtained for each day of the week (Monday to Sunday).
- the time is divided into 1 hour units for learning, but the present invention is not limited to this, and it may be 30 minute units or 2 hour units.
- the inlet water temperature T wi was set as the temperature detected by the inlet water temperature sensor 210.
- the present invention is not limited to this, and the inlet water temperature T wi may be equal to the hot water tank water temperature, and the inlet water temperature may be the hot water tank water temperature.
- the heat exchange pipe part of the intermediate water and the hot water storage water of the hot water storage tank 27 is located at the lower part of the hot water storage tank 27, and the intermediate water outlet is close to the lowermost part of the tank. Therefore, the inlet water temperature may be the detected temperature of the fourth hot water storage tank water temperature sensor 215. By doing so, the inlet water temperature T wi can be acquired without the inlet water temperature sensor 210.
- the outlet water temperature T wo was set as the temperature detected by the outlet water temperature sensor 211.
- the plate water heat exchanger 17 (first radiator) is calculated from the saturation temperature of the pressure detected by the high pressure sensor 201.
- the condensation temperature may be calculated as the outlet water temperature Two . By doing so, the outlet water temperature Two can be acquired without the outlet water temperature sensor 211.
- the hot water supply operation time ⁇ t start is input in advance, and then treated as a constant value without updating the value.
- the hot water supply capacity target Q wm changes depending on the hot water supply operation time ⁇ t start , and the operation frequency of the compressor 1 changes. Therefore, the use state of the user of the hot water, the deviation of the hot heat L i up heat consumption L m and the hot water supply at the start of the hot water storage tank 27 increases. Therefore, the hot water supply capacity target Q wm calculated by the equation (3) becomes large, the operation frequency of the compressor 1 becomes high, and the operation efficiency decreases. Therefore, in order to ensure a certain operating efficiency, it is desirable that the hot water supply operation time ⁇ t start is also changed according to the use state of the user's hot water.
- the standard target hot water supply capacity Q std (standard supply heat amount) is stored in the storage unit 104 in advance, and the hot water supply operation time ⁇ t start is updated with the standard target hot water supply capacity Q std and the hot water supply capacity target Q wm .
- the calculation unit 102 assumes that the inverse number of the hot water supply capacity and the hot water supply time is proportional to the hot water supply capacity target Q wm determined by the expression (3) from the expression (3). Then, the hot water supply operation time ⁇ t start is calculated from the standard hot water supply capacity Q std using equation (7) (calculation unit 102 as hot water supply time calculation means).
- the calculation unit 102 updates the hot water supply operation time ⁇ t start from the previous hot water supply time ⁇ t old (past hot water supply time) to the hot water supply operation time ⁇ t start obtained by the calculation of Expression (7), and applies from the hot water supply operation of the next day. To do. The user's hot water usage may change, so they learn and update again at the end of the day. By determining the hot water supply operation time ⁇ t start by such a method, it becomes possible for any user to control the hot water supply capacity to a predetermined value, and to ensure high operating efficiency.
- the load to be stored in the storage unit 104 was one of the largest amount of heat consumed L m.
- the present invention is not limited to this, and a plurality of (for example, two, three) types of loads (a plurality of heat consumption amounts) are stored in the storage unit 104, and the main control (hot water supply operation control) is applied to each load. May be.
- the target hot-water heat quantity L m varies depending on the magnitude of the amount of heat consumed, regardless of the amount of heat consumed, that is, in order to obtain a predetermined hot-water supply ability target Q wm regardless of the target hot-water heat hot water supply time ⁇ t It is necessary to store the start individually for each type of load.
- the operating frequency of the compressor 1 is determined by the equations (2) to (6).
- C After finishing the hot water supply operation mode C, the maximum hot water supply time applied to the next day is calculated from the equation (7).
- D Moreover, when it becomes the time before the 2nd hot water supply time previously memorize
- the air conditioning and hot water supply combined system 100 is taken as an example.
- the present invention is not limited to this, and the hot water supply system in which the heat source unit 301 and the hot water supply unit 304 are connected by the refrigerant communication pipe, that is, the air conditioning function is provided.
- the developed technology can also be applied to a hot water supply operation of a hot water supply system that can perform only a hot water supply operation.
- Heating and hot water simultaneous operation mode D In the heating and hot water supply simultaneous operation mode D (heat radiation parallel operation), the four-way valve 3 is shown by a broken line in FIG. 4, that is, the discharge side of the compressor 1 is connected to the gas side of the plate water heat exchanger 17. The side is connected to the gas side of the outdoor heat exchanger 4.
- the first discharge solenoid valve 2 is open, the second discharge solenoid valve 15 is open, and the low pressure equalizing solenoid valve 21 is closed.
- the compressor 1, the outdoor fan 5, the indoor fans 11a and 11b, and the water supply pump 18 are started. Then, the low-pressure gas refrigerant is sucked into the compressor 1 and compressed to become a high-temperature / high-pressure gas refrigerant. Thereafter, the high-temperature and high-pressure gas refrigerant is distributed so as to flow through the first discharge electromagnetic valve 2 or the second discharge electromagnetic valve 15.
- the refrigerant that has flowed into the second discharge solenoid valve 15 flows out of the heat source unit 301 and flows into the hot water supply unit 304 via the hot water supply gas extension pipe 16.
- the refrigerant that has flowed into the hot water supply unit 304 flows into the plate water heat exchanger 17, exchanges heat with the water supplied by the water supply pump 18, is condensed, becomes a high-pressure liquid refrigerant, and flows out from the plate water heat exchanger 17. To do.
- the refrigerant heated by the plate water heat exchanger 17 flows out of the hot water supply unit 304 and then flows into the branch unit 302 via the hot water supply liquid pipe 19 and is depressurized by the hot water supply depressurization mechanism 20 to be low pressure gas-liquid two-phase.
- the refrigerant that has flowed through the indoor decompression mechanisms 8 a and 8 b merges at the branch portion 26 and flows out from the branch unit 302.
- the flow path from the discharge side of the compressor 1 to the first discharge solenoid valve 2, the four-way valve 3, the indoor heat exchangers 10a and 10b, and the indoor pressure reducing mechanisms 8a and 8b is compared to the flow path of the hot water supply operation.
- This is a branch channel (heat dissipation branch channel).
- the hot water supply decompression mechanism 20 is controlled by the control unit 103 so that the degree of supercooling on the liquid side of the plate water heat exchanger 17 becomes a predetermined value.
- the degree of supercooling on the liquid side of the plate water heat exchanger 17 is the same as in the hot water supply operation.
- the hot water supply decompression mechanism 20 controls the flow rate of the refrigerant flowing through the plate water heat exchanger 17 so that the degree of supercooling of the refrigerant on the liquid side of the plate water heat exchanger 17 becomes a predetermined value. For this reason, the high-pressure liquid refrigerant condensed in the plate water heat exchanger 17 is in a state having a predetermined degree of supercooling.
- the plate water heat exchanger 17 is supplied with a refrigerant having a flow rate corresponding to the hot water supply request required in the hot water use situation of the facility where the hot water supply unit 304 is installed.
- the refrigerant flowing into the first discharge solenoid valve 2 flows out of the heat source unit 301 after passing through the four-way valve 3, and flows to the branch unit 302 via the gas extension pipe 13. Then, it flows into utilization unit 303a, 303b via indoor gas piping 12a, 12b.
- the refrigerant that has flowed into the utilization units 303a and 303b flows into the indoor heat exchangers 10a and 10b (second radiators), exchanges heat with the indoor air supplied by the indoor fans 11a and 11b, condenses, and condenses. And then flows out of the indoor heat exchangers 10a and 10b.
- the refrigerant that has heated the indoor air in the indoor heat exchangers 10a and 10b flows out from the use units 303a and 303b, flows into the branch unit 302 via the indoor liquid pipes 9a and 9b, and is supplied to the indoor decompression mechanisms 8a and 8b ( The pressure is reduced by the second pressure reducing mechanism) to become a low-pressure gas-liquid two-phase or liquid-phase refrigerant. Thereafter, the refrigerant that has flowed out of the indoor pressure reducing mechanisms 8 a and 8 b merges with the refrigerant that has flowed through the hot water supply pressure reducing mechanism 20 at the branch portion 26, and flows out of the branch unit 302.
- the refrigerant that has flowed out of the branch unit 302 flows into the heat source unit 301 via the liquid extension pipe 7, passes through the outdoor decompression mechanism 6, and then flows into the outdoor heat exchanger 4.
- the opening degree of the outdoor decompression mechanism 6 is controlled to be fully open.
- the refrigerant that has flowed into the outdoor heat exchanger 4 exchanges heat with outdoor air supplied by the outdoor blower 5 and evaporates to become a low-pressure gas refrigerant.
- the refrigerant flows out of the outdoor heat exchanger 4, passes through the accumulator 14 through the four-way valve 3, and is sucked into the compressor 1 again.
- the air volume of the outdoor blower 5 is controlled by the control unit 103 so that the evaporation temperature becomes a predetermined value in accordance with the outside air temperature detected by the outside air temperature sensor 205.
- the evaporation temperature is a temperature detected by the outdoor liquid temperature sensor 204.
- the heating and hot water simultaneous operation mode D it is necessary to supply hot water while outputting the heating capacity corresponding to the heating load.
- Conventionally since there is a hot water supply operation, in order to avoid running out of hot water, it has been necessary to control the compressor frequency high in order to achieve a large hot water supply capacity.
- the hot water supply operation control By applying the hot water supply operation control, the minimum required hot water supply capacity can be grasped, and the operation frequency of the compressor 1 can be controlled accordingly. Therefore, it is possible to realize the operation of simultaneously performing the hot water supply operation with high operation efficiency while outputting the heating capacity according to the heating load.
- the hot water supply capacity target Q wm (minimum required hot water supply capacity) is calculated by the equation (3) using the maximum heat consumption L m and the maximum consumption time t m learned by the hot water supply operation, and the exit is calculated by the equation (4).
- the water temperature target T worm is calculated.
- step S14 the outlet water temperature Two and the outlet water temperature target Twom are compared. Here whether is sufficiently hot water supply capacity to the heat storage up to heat consumption L m in the hot water storage tank 27 to a maximum hot water supply capacity consumption time t m which is determined by the operation frequency of the compressor 1 which is controlled by the step S12 judge. That is, it is determined whether the hot water supply capacity is larger than the hot water supply capacity target Qwm .
- Outlet water temperature T wo is determined that sufficient hot water supply capacity is higher than the outlet temperature target T wom is secured to the directly used as the operating frequency of the compressor 1 proceeds to step S15.
- Outlet water temperature T wo is insufficient hot water supply capability if lower than the outlet temperature target T wom, i.e., determines that the hot water supply capacity is smaller than the hot water supply capacity target, the outlet water temperature T wo outlet temperature target T wom proceeds to step S16 Until the operating frequency of the compressor 1 is increased.
- the operating frequency of the compressor 1 can be set. For this reason, it is possible to control the operation frequency of the compressor 1 to be lower than that in the case where the amount of hot water used by a conventional user is not used, and to perform simultaneous heating and hot water supply operation.
- the hot water supply operation time target ⁇ t m is calculated by the equation (7) and the hot water supply operation time ⁇ t start is updated, so that the hot water supply capacity target Q for any user can be obtained.
- wm can be made constant for the standard hot water supply capacity Q std , and high operating efficiency can be realized.
- the low-pressure gas refrigerant is sucked into the compressor 1 and compressed to be a high-temperature / high-pressure gas. Becomes a refrigerant. Thereafter, the high-temperature and high-pressure gas refrigerant flows into the second discharge electromagnetic valve 15.
- the refrigerant that has flowed into the second discharge solenoid valve 15 flows out of the heat source unit 301 and flows into the hot water supply unit 304 via the hot water supply gas extension pipe 16.
- the refrigerant flowing into the hot water supply unit 304 flows into the plate water heat exchanger 17, exchanges heat with the water supplied by the water supply pump 18, condenses into a high-pressure liquid refrigerant, and flows out from the plate water heat exchanger 17. To do.
- the refrigerant that has heated the water in the plate water heat exchanger 17 flows out of the hot water supply unit 304 and flows into the branch unit 302 via the hot water supply liquid pipe 19.
- the refrigerant that has flowed into the branch unit 302 is decompressed by the hot water supply decompression mechanism 20, and becomes an intermediate-pressure gas-liquid two-phase or liquid-phase refrigerant.
- the hot water supply pressure reducing mechanism 20 is controlled to the maximum opening.
- the refrigerant is distributed into the refrigerant flowing into the liquid extension pipe 7 and the refrigerant flowing into the indoor decompression mechanisms 8a and 8b.
- the refrigerant directed to the indoor unit is branched at the branching portion 26.
- the flow paths of the indoor pressure reducing mechanisms 8a and 8b (second pressure reducing mechanism), the indoor heat exchangers 10a and 10b (second evaporator), and the four-way valve 3 form an endothermic branch flow path.
- the refrigerant that has flowed into the indoor pressure reducing mechanisms 8a and 8b is depressurized to become a low-pressure gas-liquid two-phase state, and flows into the use units 303a and 303b via the indoor liquid pipes 9a and 9b.
- the refrigerant flowing into the utilization units 303a and 303b flows into the indoor heat exchangers 10a and 10b, exchanges heat with the indoor air supplied by the indoor fans 11a and 11b, and evaporates to become a low-pressure gas refrigerant.
- the indoor decompression mechanisms 8a and 8b are configured to eliminate the temperature difference (cooling room temperature difference) obtained by subtracting the set temperature from the indoor suction temperature detected by the indoor suction temperature sensors 208a and 208b in the use units 303a and 303b. Be controlled. Therefore, the refrigerant
- the refrigerant that has flowed through the indoor heat exchangers 10a and 10b then flows out of the use units 303a and 303b, and flows into the heat source unit 301 via the indoor gas pipes 12a and 12b, the branch unit 302, and the gas extension pipe 13.
- the refrigerant flowing into the heat source unit 301 passes through the four-way valve 3 and then merges with the refrigerant that has passed through the outdoor heat exchanger 4.
- the refrigerant that has flowed into the liquid extension pipe 7 then flows into the heat source unit 301, is decompressed to a low-pressure gas-liquid two-phase refrigerant by the outdoor decompression mechanism 6, and then flows into the outdoor heat exchanger 4. It evaporates by exchanging heat with the outdoor air supplied by. Thereafter, the refrigerant merges with the refrigerant that has passed through the indoor heat exchangers 10a and 10b via the low-pressure equalizing solenoid valve 21. Thereafter, it passes through the accumulator 14 and is sucked into the compressor 1 again.
- the outdoor blower 5 controls the minimum air volume necessary for cooling the heat radiating plate, and controls the opening degree of the outdoor decompression mechanism 6 to be slightly opened.
- cooling and hot water simultaneous operation mode E it is necessary to supply hot water while outputting the cooling capacity according to the cooling load.
- Conventionally since there is a hot water supply operation, in order to avoid running out of hot water, it has been necessary to control the compressor frequency high in order to achieve a large hot water supply capacity. Therefore, the cooling capacity becomes excessive, and it becomes necessary to alternately switch between the hot water supply operation mode C and the cooling hot water supply simultaneous operation mode E, and the operation is inefficient.
- this development technology it is possible to grasp the minimum required hot water supply capacity and control the operating frequency of the compressor 1 accordingly. Therefore, by applying this developed technology, it is possible to realize the operation of simultaneously performing the hot water supply operation while outputting the cooling capacity according to the cooling load, and high operating efficiency can be obtained.
- FIG. 9 is a flowchart showing compressor control in the cooling hot water supply simultaneous operation mode E.
- the operation frequency of the compressor 1 is controlled in accordance with the cooling load in the same manner as in the cooling operation mode A in step S22. That is, in Embodiment 1, the operation frequency of the compressor 1 is controlled by the control unit 103 so that the evaporation temperature becomes a predetermined value according to the maximum temperature difference in the cooling chamber.
- the method for obtaining the evaporation temperature is the same as in the cooling operation. In this operation, the cooling capacity according to the cooling load is ensured.
- the outlet water temperature target T worm is calculated in the same manner as in the hot water supply operation mode C.
- the hot water supply capacity target Q wm (minimum required hot water supply capacity) is calculated by the equation (3) using the maximum heat consumption L m and the maximum consumption time t m learned by the hot water supply operation, and the exit is calculated by the equation (4).
- the water temperature target T worm is calculated.
- step S24 the outlet water temperature Two and the outlet water temperature target Twom are compared.
- Outlet water temperature T wo is determined that sufficient hot water supply capacity is higher than the outlet temperature target T wom is secured to the directly used as the operating frequency of the compressor 1 proceeds to step S25.
- Outlet water temperature T wo is insufficient hot water supply capability if lower than the outlet temperature target T wom, i.e., determines that the hot water supply capacity is smaller than the hot water supply capacity target, the outlet water temperature T wo outlet temperature target T wom proceeds to step S26 Until the operating frequency of the compressor 1 is increased.
- the cooling capacity corresponding to the cooling load is output, and the minimum required hot water supply capacity is determined according to the past use of hot water by the user,
- the operating frequency of the compressor 1 can be set accordingly. For this reason, it is possible to control the operation frequency of the compressor 1 to be lower than that in the case where the amount of hot water used by a conventional user is not used, and to perform simultaneous cooling and hot water supply operation.
- the cooling capacity has been increased in order to increase the hot water supply capacity so that the hot water does not run out.
- the hot water supply operation time target ⁇ t m is calculated by the equation (7) and the hot water supply operation time ⁇ t start is updated, so that the hot water supply capacity target Q for any user can be obtained.
- wm can be made constant, and high driving efficiency can be realized.
- the air-conditioning and hot water supply combined system 100 of the first embodiment it is possible to perform hot water supply operation with high operation efficiency and avoid running out of hot water.
- Embodiment 1 the air conditioning and hot water supply combined system 100 (refrigeration cycle apparatus) has been described. However, the operation of the air conditioning and hot water supply combined system 100 can also be grasped as a refrigeration cycle control method.
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Abstract
Description
湯切れの心配がある場合は、ヒートポンプサイクルの加熱能力を引き出す運転を優先して湯切れを防止し、湯切れの心配がない場合には、ヒートポンプサイクルの運転効率を優先した運転を行う。この公知技術では、加熱能力を引き出す運転時は給湯能力を確保するために、圧縮機の運転周波数を高く制御する必要があるため、運転効率の悪化は避けられない。
冷媒を循環させる冷凍サイクル装置において、
運転周波数の制御が可能な圧縮機と、貯湯タンクに蓄えられた水であるタンク水に前記冷媒によって熱量を供給する第1の放熱器と、第1の減圧機構と、第1の蒸発器とを有し、前記冷媒が前記圧縮機、前記第1の放熱器、前記第1の減圧機構、前記第1の蒸発器の順に循環する冷凍サイクル機構と、
制御装置と
を備え、
前記制御装置は、
予め設定された制御期間を示す制御期間情報を記憶する共に、他の情報を記憶可能な記憶部と、
前記第1の放熱器から所定の時刻を基準として前記タンク水に供給された熱量を示す供給熱量を所定の供給熱量計算規則に基づき計算し、計算した前記供給熱量を前記記憶部に記憶すると共に、前記タンク水が有する現在の蓄熱量を所定の蓄熱量計算規則に基づいて算出する演算部と、
前記記憶部に記憶された前記制御期間情報と、前記記憶部に記憶された前記供給熱量と、前記演算部によって計算された前記現在の蓄熱量とに基づいて、前記圧縮機の運転周波数を制御する制御部と
を備えたことを特徴とする。
以下、図面に基づいて実施の形態1について説明する。
図1は、実施の形態1における空調給湯複合システム100(冷凍サイクル装置)の冷媒回路構成図である。なお、図1を含め、以下の図面では各構成部材の大きさの関係が実際のものと異なる場合がある。また、この明細書では、数式に使用する記号で初めて文中にでてくるものには、[ ]の中にその記号の単位を書く。また、無次元(単位なし)の場合は、[-]と表記する。
図3は、空調給湯複合システム100の各種センサ、制御装置110を示す概略図である。以下、図1~図3を参照して空調給湯複合システム100の構成を説明する。この空調給湯複合システム100は、蒸気圧縮式の冷凍サイクル運転を行うことによって、利用ユニットにおいて選択された冷房運転又は暖房運転と給湯ユニットにおける給湯運転とを同時に処理することができる3管式のマルチシステム空調給湯複合システムである。空調給湯複合システム100は、給湯動作時に、圧縮機周波数を低くして高効率に給湯を行い、かつ湯切れを防止することができる。また、この空調給湯複合システム100は、冷房と給湯の同時運転において、冷房負荷に応じて圧縮機周波数を小さく運転しても湯切れを回避することができる。
空調給湯複合システム100は、熱源ユニット301と、分岐ユニット302と、利用ユニット303a,303bと、給湯ユニット304と、タンクユニット305と、を有している。熱源ユニット301と分岐ユニット302とは、冷媒配管である液延長配管7と冷媒配管であるガス延長配管13とで接続されている。給湯ユニット304は一方が冷媒配管である給湯ガス延長配管16を介して熱源ユニット301に接続され、他方が冷媒配管である給湯液配管19を介して分岐ユニット302に接続されている。利用ユニット303a,303bと分岐ユニット302とは、冷媒配管である室内ガス配管12a,12bと冷媒配管である室内液配管9a,9bとで接続されている。また、タンクユニット305と給湯ユニット304とは水配管である水上流配管22と水配管である水下流配管23とで接続されている。水上流配管22と水下流配管23とは、貯湯タンク27からプレート水熱交換器17に流入し、プレート水熱交換器17を通過して貯湯タンク27に戻る水の流路となる水流路を形成する。
空調給湯複合システム100が実行可能な運転モードについて簡単に説明する。空調給湯複合システム100では、接続されている給湯ユニット304の給湯要求、及び、利用ユニット303a,303bの冷房負荷又は暖房負荷の有無によって、熱源ユニット301の運転モードが決定されるようになっている。空調給湯複合システム100は、以下の5つの運転モードを実行することが可能である。
すなわち、冷房運転モードA、暖房運転モードB、給湯運転モードC、暖房給湯同時運転モードD、冷房給湯同時運転モードEである。
(2)暖房運転モードBは、給湯要求がなく、利用ユニット303a,303bが暖房運転を実行する場合の熱源ユニット301の運転モードである。
(3)給湯運転モードCは、空調負荷がなく、給湯ユニット304が給湯運転を実行する場合の熱源ユニット301の運転モードである。
(4)暖房給湯同時運転モードDは、利用ユニット303a,303bによる暖房運転と、給湯ユニット304による給湯運転との同時運転を実行する場合の熱源ユニット301の運転モードである。
(5)冷房給湯同時運転モードEは、利用ユニット303a,303bによる冷房運転と、給湯ユニット304による給湯運転との同時運転を実行する場合の熱源ユニット301の運転モードである。
利用ユニット303a,303bは分岐ユニット302を介して、熱源ユニット301に接続されている。利用ユニット303a,303bは、空調対象域に調和空気を吹き出すことができる場所(たとえば、屋内の天井への埋め込みや吊り下げ等により、又は、壁面への壁掛け等)に設置されている。利用ユニット303a,303bは、分岐ユニット302と液延長配管7及びガス延長配管13とを介して熱源ユニット301に接続されており、冷媒回路の一部を構成している。
また、利用ユニット303a,303bには、以下に示す各種センサが設けられている。
(1)室内熱交換器10a,10bの液側(放熱器として動作の場合の液側)に設けられ、液冷媒の温度を検出する室内液温度センサ206a,206b;
(2)室内熱交換器10a,10bのガス側(放熱器として動作の場合のガス側)に設けられ、ガス冷媒の温度を検出する室内ガス温度センサ207a,207b;
(3)利用ユニット303a,303bの室内空気の吸入口側に設けられ、ユニット内に流入する室内空気の温度を検出する室内吸込温度センサ208a,208b;
給湯ユニット304は分岐ユニット302を介して、熱源ユニット301に接続している。図2に示すように、給湯ユニット304は、たとえば屋外等に設置されたタンクユニット305に温水を供給し、貯湯タンク27内の水を加熱して湯を沸き上げる機能を有している。給湯ユニット304のプレート水熱交換器17は、水上流配管22(水流入配管)が接続する接続部24(水流入配管接続部)と、水下流配管23(水流出配管)が接続する接続部25(水流出配管接続部)とを備えている。また、給湯ユニット304は、一方が給湯ガス延長配管16を介して熱源ユニット301に接続されており、他方が給湯液配管19を介して分岐ユニット302に接続されており、空調給湯複合システム100における冷媒回路の一部を構成している。
また、給湯ユニット304には、以下に示す各種センサが設けられている。
(1)プレート水熱交換器17の液側に設けられ、液冷媒の温度を検出する給湯液温度センサ209;
(2)水の流入部に設けられ、流入する水の入口水温を検出する入口水温温度センサ210(入口温度センサ);
(3)水の流出部に設けられ、流出する水の出口水温を検出する出口水温温度センサ211(出口温度センサ);
(4)水の流入部に設けられ、流入する水の体積流量を検出する中間水流量計219(図2);
タンクユニット305はたとえば屋外に設置されており、給湯ユニット304により沸きあげられた湯を貯留する機能を有している。タンクユニット305は図2に示されるように貯湯をするための貯湯タンク27を有している。また、一方が水上流配管22を介して給湯ユニット304に接続されており、他方が水下流配管23を介して給湯ユニット304に接続されており、空調給湯複合システム100における水回路の一部を構成している。貯湯タンク27は満水式であり、使用者が湯を消費するとタンク上部より湯が出水し、その量に応じてタンク下部より市水が給水される。
また、タンクユニット305には、以下に示す各種センサが設けられている。
(1)貯湯タンク27のタンク側面に設けられ、貯湯タンク27の上部側側面の湯温を検出する第1貯湯タンク水温温度センサ212;
(2)貯湯タンク27のタンク側面に設けられ、貯湯タンク27の第1貯湯タンク水温温度センサ212の下部側面の湯温を検出する第2貯湯タンク水温温度センサ213;
(3)貯湯タンク27のタンク側面に設けられ、貯湯タンク27の第2貯湯タンク水温温度センサ213の下部側面の湯温を検出する第3貯湯タンク水温温度センサ214;
(4)貯湯タンク27のタンク側面に設けられ、貯湯タンク27の第3貯湯タンク水温温度センサ214の下部側面の湯温を検出する第4貯湯タンク水温温度センサ215;
(5)貯湯タンク27のタンク出水部に設けられ、貯湯タンク27からの出水温度を検出する貯湯タンク出水温度センサ216;
(6)貯湯タンク27のタンク給水部に設けられ、貯湯タンク27への入水温度を検出する貯湯タンク入水温度センサ217;
(7)貯湯タンク27のタンク出水部に設けられ、貯湯タンク27からの出水流量を検出するタンク水流量計218;
熱源ユニット301は、たとえば屋外に設置されており、液延長配管7とガス延長配管13と分岐ユニット302を介して利用ユニット303a,303bに接続されている。また、給湯ガス延長配管16、液延長配管7及び分岐ユニット302を介して給湯ユニット304に接続されており、空調給湯複合システム100における冷媒回路の一部を構成している。
図4は、運転モードに対する四方弁及び電磁弁の動作内容を示す。図4に表示されている「実線」及び「破線」は、図1に示している四方弁3の切り換え状態を表している「実線」及び「破線」を意味している。
また、熱源ユニット301には、以下に示す各種センサが設けられている。
(1)圧縮機1の吐出側に設けられ、高圧側圧力を検出する高圧圧力センサ201;
(2)圧縮機1の吐出側に設けられ、吐出温度を検出する吐出温度センサ202;
(3)室外熱交換器4のガス側に設けられ、ガス冷媒温度を検出する室外ガス温度センサ203;
(4)室外熱交換器4の液側に設けられ、液冷媒の温度を検出する室外液温度センサ204;
(5)熱源ユニット301の室外空気の吸入口側に設けられ、ユニット内に流入する室外空気の温度を検出する外気温度センサ205;
分岐ユニット302は、たとえば屋内に設置され、液延長配管7とガス延長配管13を介して熱源ユニット301とに接続され、室内液配管9a,9bと室内ガス配管12a,12bとを介して利用ユニット303a,303bと接続され、給湯液配管19とを介して給湯ユニット304に接続されており、空調給湯複合システム100における冷媒回路の一部を構成している。分岐ユニット302は、利用ユニット303a,303b及び給湯ユニット304に要求されている運転に応じて冷媒の流れを制御する機能を有している。
制御部103は、
圧縮機1の運転周波数、
第1吐出電磁弁2の切換え、
四方弁3の切換え、
室外送風機5の回転数(ON/OFF含む)、
室外減圧機構6の開度、
室内減圧機構8a,8bの開度、
室内送風機11a,11bの回転数(ON/OFF含む)、
第2吐出電磁弁15の切換え、
給水ポンプ18の回転数(ON/OFF含む)、
給湯減圧機構20の開度、
低圧均圧電磁弁21の切換えを制御し、
各運転モードを実行する。
なお、測定部101、演算部102、制御部103、記憶部104及び時計部105は一体的に設けられてもよく、別々に設けられてもよい。また、測定部101、演算部102、制御部103、記憶部104及び時計部105は、いずれのユニットに設けられるようにしてもよい。さらに、測定部101、演算部102、制御部103、記憶部104及び時計部105は、ユニット毎に設けるようにしてもよい。
空調給湯複合システム100は、利用ユニット303a,303bに要求されるそれぞれの空調負荷及び給湯ユニット304に要求される給湯要求に応じて熱源ユニット301、分岐ユニット302及び利用ユニット303a,303b、給湯ユニット304に搭載されている各機器の制御を行い、冷房運転モードA、暖房運転モードB、給湯運転モードC、暖房給湯同時運転モードD、冷房給湯同時運転モードE、を実行する。
空調給湯複合システム100が行う冷房運転モードA、暖房運転モードB、給湯運転モードC、暖房給湯同時運転モードD、冷房給湯同時運転モードEの具体的な冷媒流れ方法及び各機器の通常制御方法を説明する。各運転モードにおける四方弁3の動作は図4に示す通りである。
冷房運転モードAでは四方弁3が実線で示される状態、すなわち、圧縮機1の吐出側が室外熱交換器4のガス側に接続された状態となっている。また、第1吐出電磁弁2は開、第2吐出電磁弁15は閉、低圧均圧電磁弁21は閉状態となっている。さらに、給湯減圧機構20は最低開度(全閉)である。
暖房運転モードBでは、四方弁3が破線で示される状態、すなわち圧縮機1の吐出側が室内熱交換器10a,10bのガス側に接続され、圧縮機1の吸入側が室外熱交換器4のガス側に接続される。また、第1吐出電磁弁2は開、第2吐出電磁弁15は閉、低圧均圧電磁弁21は閉状態となっている。さらに、給湯減圧機構20は全閉である。
給湯運転モードCでは、四方弁3が破線で示される状態、すなわち圧縮機1の吐出側がプレート水熱交換器17のガス側に接続され、圧縮機1の吸入側が室外熱交換器4のガス側に接続される。また、第1吐出電磁弁2は閉、第2吐出電磁弁15は開、低圧均圧電磁弁21は閉状態となっている。さらに、室内減圧機構8a,8bは全閉である。
しかし、運転効率が悪化していた。そこで、湯切れを回避しつつ高い運転効率を実現するため、過去の湯の使用記録を用いて圧縮機1の運転周波数を低く制御する。以下の式(1)~式(7)に基づいて行う圧縮機の運転周波数の制御を「給湯運転制御」と呼ぶこととする。
演算部102は、図5に示すように、1日の各時刻において貯湯タンク27の消費熱量を式(1)(外部供給熱量計算規則)により1時間ごとにそれぞれ算出する(給湯負荷演算手段としての演算部)場合を示す。
Cp,w:水の比熱[kJ/(kgK)]、
Lm:最大消費熱量(目標貯湯熱量)[kJ]、
Ttankwi:給水温度[℃]、
Ttankwo:出水温度[℃]、
Vwo:出水の体積流量[m3/s]、
Δtw:出水時間[s]、
ρw:水の密度[kg/m3]、
である。
Ttankwiは入口水温温度センサ210により検出される温度のうち、過去の検出温度の最小値(例えば過去3日間の検出温度の最小値)である。
Ttankwoは出口水温温度センサ211により検出される温度であり、貯湯タンク27からの出水時に検出された温度である。
Vwoはタンク水流量計218により検出される体積流量である。
式(1)より演算する消費熱量のうち最も大きいものが最大消費熱量Lmとなり、その時の時刻が最大消費時刻tmとなる。最大消費熱量Lmと最大消費時刻tmが給湯負荷に関する情報となる。
そして、1日経過後、図6に示すように前日の最大消費熱量Lmを記録した時刻tmのΔtstart前の時刻(給湯開始時刻)になったら、制御部103は、給湯運転モードCを開始する。つまり、制御部103は、以下に示す運転周波数で、圧縮機1を制御する。この場合の圧縮機1の運転周波数(目標運転周波数Fm)は式(2)~式(6)により決定される。
+(V2-V1)×(Ttank2-Ttankwi)
+(V3-V2)×(Ttank3-Ttankwi)
+(V4-V3)×(Ttank4-Ttankwi)] ・・・(2)
Cp,w:水の比熱[kJ/(kgK)]、
F:圧縮機1の制御前の運転周波数[Hz]、
Fm:圧縮機1の目標運転周波数[Hz]、
ΔF:圧縮機1の運転周波数変更量[Hz]、
Li:給湯開始時の貯湯タンク27の貯湯熱量[kJ]、
Lm:最大消費熱量(目標貯湯熱量)[kJ]、
Qwm:給湯能力目標[kW]、
Ttank1:貯湯タンク27の最上部から第1上部までの貯湯水温[℃]、
Ttank2:貯湯タンク27の第1上部から第2上部までの貯湯水温[℃]、
Ttank3:貯湯タンク27の第2上部から第3上部までの貯湯水温[℃]、
Ttank4:貯湯タンク27の第3上部から最下部までの貯湯水温[℃]、
Ttankwi:給水温度[℃](センサ217により検出)、
Twi:入口水温[℃](センサ210により検出)、
Two:出口水温[℃](センサ211により検出)、
Twom:出口水温目標[℃](Twoの目標温度)、
Δtstart:給湯運転時間[sec]
V1:貯湯タンク27の最上部から第1上部までの内容積[m3]、
V2:貯湯タンク27の最上部から第2上部までの内容積[m3]、
V3:貯湯タンク27の最上部から第3上部までの内容積[m3]、
V4:貯湯タンク27の最上部から最下部までの内容積[m3]、
Vw:中間水の体積流量[m3/s](中間水流量計219)、
ρw:水の密度[kg/m3]、
図7に貯湯タンク27の蓄熱量の演算方法を示す概略図を示す。
なお、「給湯開始時」とは、Δtstartに対応する時刻を意味する。
式(2)は図7に示す定義により導出されている。
また、
Twiは、タンクユニット305から給湯ユニット304への流入する水温(センサ210で検出)、
Twoは、タンクユニット305に向かって給湯ユニット304から流出する水温(センサ211で検出)、
Ttank1は、第1貯湯タンク水温温度センサ212により検出される温度、
Ttank2は、第2貯湯タンク水温温度センサ213により検出される温度、
Ttank3は、第3貯湯タンク水温温度センサ214により検出される温度、
Ttank4は、第4貯湯タンク水温温度センサ215により検出される温度、
Vwは、中間水流量計219(水流量計)により検出される体積流量、
である。
手順としては、演算部102は、式(2)(蓄熱量計算規則)により給湯開始時の貯湯タンク27の貯湯熱量Liを演算する(蓄熱量演算手段としての演算部102)。次に、前日の学習結果である最大消費熱量Lmと給湯運転時間Δtstartによ式(3)を用いて給湯能力目標Qwmを演算する。すなわち、プレート水熱交換器17(第1の放熱器)の給湯能力(放熱能力)の目標値を設定する。次に、演算部102は、入口水温Twiを用いて式(4)により給湯能力目標Qwmの場合の出口水温目標Twomを演算する(出口水温目標演算手段としての演算部102)。出口水温目標Twomとは、出口水温温度センサ211によって検出される水流の目標温度である。そして、出口水温目標Twomと出口水温Twoの偏差から、式(5)に基づき圧縮機1の運転周波数変更量ΔFを求め、最後に、式(6)により圧縮機1の目標運転周波数Fmを演算する。この手順(以下、圧縮機制御手順という場合がある)により圧縮機1の運転周波数を決定することで、圧縮機1の運転周波数を低くしても湯切れを回避することができる。このため、制御部103は、高い運転効率にて給湯動作を行うことができる(加熱制御手段としての制御部)。
また、1日が終わったら、その日の最大消費熱量Lm及び最大消費時刻tmを学習結果として更新し、次の日へ適用する。このようにすることで、ユーザーの湯の使用量の変化を反映することができる。
また、入口水温Twiは、入口水温温度センサ210の検出温度とした。しかし、これに限定されず、入口水温Twiは、貯湯タンク水温と等しいとして入口水温を貯湯タンク水温としても良い。具体的には、図2に示すように、中間水と貯湯タンク27の貯湯水の熱交管部は貯湯タンク27の下部に位置しており、中間水出口はタンク最下部から近い。そのため、入口水温を第4貯湯タンク水温温度センサ215の検出温度としもよい。こうすることで、入口水温温度センサ210がなくても、入口水温Twiを取得可能である。
また、出口水温Twoは、出口水温温度センサ211の検出温度とした。しかし、これに限定されない。例えば、プレート水熱交換器17の凝縮温度と出口水温温度センサ211の検出温度は等しいとして、高圧圧力センサ201より検出される圧力の飽和温度からプレート水熱交換器17(第1の放熱器)の凝縮温度を算出し、出口水温Twoとしても良い。こうすることで、出口水温温度センサ211がなくても出口水温Twoを取得可能である。
また、給水ポンプ18の回転数を低くして中間水(第1放熱器流入水)の流量Vwを少なくすることによって、出口水温目標Twomが高くなり、入口水温と出口水温目標との温度差が大きくなる。そのため、入口水温と出口水温目標との温度差が所定値以上(例えば5℃以上)となるように給水ポンプ18の回転数を制御することによって、センサ誤差による制御性の悪化を防ぐことが可能となる。よって、制御部103は精度よく圧縮機1の運転周波数の制御を行うことができる(水流量制御手段としての制御部)。
また、給湯運転時間Δtstartは前述の説明では、予め入力し、その後は値を更新することなく一定値として扱っていた。しかし、図6から明らかなように、給湯運転時間Δtstartによって給湯能力目標Qwmが変化し、圧縮機1の運転周波数が変化する。このため、ユーザーの湯の使用状況によっては、最大消費熱量Lmと給湯開始時の貯湯タンク27の貯湯熱量Liの偏差が大きくなる。そのため、式(3)で演算する給湯能力目標Qwmが大きくなってしまい、圧縮機1の運転周波数が高くなり、運転効率が低下する。したがって、一定の運転効率を確保するためには、給湯運転時間Δtstartもユーザーの湯の使用状況に応じて変化させるのが望ましい。
Qstd:標準給湯能力[kW]、
Δtold:前回の給湯時間[sec]。
演算部102は、給湯運転時間Δtstartを前回の給湯時間Δtold(過去の給湯時間)から式(7)の演算により求めた給湯運転時間Δtstartに更新し、次の日の給湯動作から適用する。ユーザーの湯の使用状況が変化する可能性あるため、1日の終わりに再度学習し、更新する。このような方法にて、給湯運転時間Δtstartを決定することで、どのユーザーにおいても給湯能力を所定値に制御することが可能となり、高い運転効率を確保することができる。
また、本実施の形態1では、記憶部104に記憶する負荷は最大消費熱量Lmの1つであった。しかし、これに限定されず、複数(例えば2つ、3つ)の種類の負荷(複数の消費熱量)を記憶部104に記憶し、各負荷において本制御(給湯運転制御)を適用するようにしてもよい。このときに、消費熱量の大きさに応じて目標貯湯熱量Lmが異なるため、消費熱量によらず、つまり、目標貯湯熱量によらず所定の給湯能力目標Qwmを得るためには給湯時間Δtstartを負荷の種類ごとに個別に記憶させる必要がある。このようにすることで、1日に複数回本制御を適用することが可能となり、省エネルギー性が向上する。具体的には、最大消費熱量と第2消費熱量(最大消費熱量>第2消費熱量)の2つの負荷に対して本制御を適用するとした場合に次の手順にて行う。
(a)まず、1日のうちで最大消費熱量とその時の時刻である最大消費時刻を記憶部104に記憶し、第2消費熱量とその時の時刻である第2消費時刻を記憶部104に記憶する。
(b)そして1日経過後、最大消費時刻から予め記憶部104に記憶していた最大給湯時間前の時刻になったら給湯運転モードCを開始する。この場合の圧縮機1の運転周波数は式(2)~式(6)により決定する。
(c)給湯運転モードCを終了後、式(7)より次の日に適用する最大給湯時間を演算する。
(d)また、第2消費時刻から予め記憶部104に記憶していた第2給湯時間前の時刻になったら給湯運転モードCを開始する。この場合の圧縮機1の運転周波数は式(2)~式(6)により決定する。給湯運転モードCを終了後、式(7)より次の日に適用する第2給湯時間を演算する。
(e)そして、次の日に前の日と同様に給湯動作を実行する。
暖房給湯同時運転モードD(放熱並行運転)では図4において四方弁3が破線で示される状態、すなわち圧縮機1の吐出側がプレート水熱交換器17のガス側に接続され、圧縮機1の吸入側が室外熱交換器4のガス側に接続される。また、第1吐出電磁弁2は開、第2吐出電磁弁15は開、低圧均圧電磁弁21は閉状態となっている。
冷房給湯同時運転モードE(吸熱凝縮並行運転)では利用ユニット303a,303bは冷房運転、給湯ユニット304は給湯運転となる。冷房給湯同時運転モードEでは四方弁3が破線で示される状態である。すなわち圧縮機1の吐出側が給湯ガス延長配管16を経由してプレート水熱交換器17に接続し、かつ、圧縮機1の吸入側が室外熱交換器4のガス側に接続される。また、第1吐出電磁弁2は閉、第2吐出電磁弁15は開、低圧均圧電磁弁21は開状態となっている。
Claims (10)
- 冷媒を循環させる冷凍サイクル装置において、
運転周波数の制御が可能な圧縮機と、貯湯タンクに蓄えられた水であるタンク水に前記冷媒によって熱量を供給する第1の放熱器と、第1の減圧機構と、第1の蒸発器とを有し、前記冷媒が前記圧縮機、前記第1の放熱器、前記第1の減圧機構、前記第1の蒸発器の順に循環する冷凍サイクル機構と、
制御装置と
を備え、
前記制御装置は、
予め設定された制御期間を示す制御期間情報を記憶する共に、他の情報を記憶可能な記憶部と、
所定の時刻を基準として前記タンク水によって外部に供給された熱量を示す外部供給熱量を所定の外部供給熱量計算規則に基づき計算し、計算した前記外部供給熱量を前記記憶部に記憶すると共に、前記タンク水が有する現在の蓄熱量を所定の蓄熱量計算規則に基づいて算出する演算部と、
前記記憶部に記憶された前記制御期間情報と、前記記憶部に記憶された前記外部供給熱量と、前記演算部によって計算された前記現在の蓄熱量とに基づいて、前記圧縮機の運転周波数を制御する制御部と
を備えたことを特徴とする冷凍サイクル装置。 - 前記冷凍サイクル装置は、さらに、
前記貯湯タンクから前記第1の放熱器に流入し、前記第1の放熱器を通過して前記貯湯タンクに戻る水の流路となる水流路における前記第1の放熱器の出口から流出する流出水の温度を検出する出口温度センサを備え、
前記演算部は、
前記記憶部に記憶された前記制御期間情報と、前記記憶部に記憶された前記外部供給熱量と、前記演算部によって計算された前記現在の蓄熱量とに基づいて、目標とするべき前記流出水の温度を示す目標温度を計算し、
前記制御部は、
前記出口温度センサによって検出される前記流出水の温度が、前記演算部によって計算された前記目標温度になるように、前記圧縮機の運転周波数を制御することを特徴とする請求項1の冷凍サイクル装置。 - 前記記憶部は、
前記タンク水に単位時間当たりに供給するべき熱量の標準値を示す標準供給熱量を記憶し、
前記演算部は、
前記記憶部に記憶された前記制御期間情報とは異なる新たな制御期間情報を、前記記憶部に記憶された前記外部供給熱量と、前記演算部によって計算された前記現在の蓄熱量と、前記記憶部に記憶された前記標準供給熱量とから算出し、算出した前記新たな制御期間情報を前記記憶部に記憶し、
前記制御部は、
前記記憶部に記憶された前記新たな制御期間情報を用いて、前記圧縮機の周波数を制御することを特徴とする請求項1または2のいずれかに記載の冷凍サイクル装置。 - 前記冷凍サイクル装置は、さらに、
前記タンク水の温度を検出するタンク水センサを備え、
前記演算部は、
前記タンク水センサにより検出された前記タンク水の温度をさらに用いて、前記タンク水が有する現在の前記蓄熱量を算出することを特徴とする請求項1~3のいずれかに記載の冷凍サイクル装置。 - 前記冷凍サイクル装置は、さらに、
前記貯湯タンクから前記第1の放熱器に流入し、前記第1の放熱器を通過して前記前記貯湯タンクに戻る水の流路となる水流路における前記第1の放熱器の入り口に流入する流入水の温度を検出する入口温度センサと、
前記圧縮機の吐出側から前記第1の減圧機構の液側までの高圧圧力を検出する高圧圧力センサと
を備え、
前記演算部は、
前記高圧圧力センサによって検出された前記高圧圧力に基づいて前記第1の放熱器の凝縮温度を算出し、
前記制御部は、
前記演算部によって計算された前記凝縮温度と、前記入口温度センサによって検出された前記流入水の温度とをさらに用いて、前記圧縮機の運転周波数を制御することを特徴とする請求項1記載の冷凍サイクル装置 - 前記冷凍サイクル装置は、さらに、
前記水流路に前記水を流通させる給水ポンプと、
前記水流路における前記第1の放熱器の入り口に流入する流入水の温度を検出す入口温度センサと
を備え、
前記制御部は、
前記圧縮機の前記運転周波数を制御している時に、前記給水ポンプの制御を介して前記第1の放熱器に流入する前記流入水の流量を制御することにより、前記入口温度センサによって検出される前記流入水の温度と、目標とすべき前記流出水の温度を示す前記目標温度との温度差を、所定値以上に維持することを特徴とする請求項2記載の冷凍サイクル装置。 - 前記冷凍サイクル装置は、さらに、
前記圧縮機の吐出側から分岐する分岐流路であって、第2の放熱器と第2の減圧機構とを有し、前記圧縮機の前記吐出側から前記第2の放熱器、前記第2の減圧機構の順に接続され、前記第1の減圧機構と前記第1の蒸発器との間に合流する放熱分岐流路を備え、
前記制御部は、
前記圧縮機から吐出された吐出冷媒を前記第1の放熱器と前記第2の放熱器とに流入させて循環させる放熱並行運転を実行すると共に、
前記記憶部に記憶された前記制御期間情報と、前記記憶部に記憶された前記外部供給熱量と、前記演算部によって計算された前記現在の蓄熱量とに加え、さらに、前記第2の放熱器に要求される負荷を示す暖房負荷とに基づいて、前記圧縮機の前記運転周波数を制御することを特徴とする請求項1記載の冷凍サイクル装置。 - 前記冷凍サイクル装置は、さらに、
前記第1の減圧機構と前記第1の蒸発器との間の分岐部から分岐する吸熱分岐流路であって、第2の減圧機構と第2の蒸発器とを有し、前記分岐部から前記第2の減圧機構、前記第2の蒸発器の順に接続され、前記圧縮機の前記吸入側に合流する吸熱分岐流路を備え、
前記制御部は、
前記圧縮機から吐出された吐出冷媒を前記第1の放熱器、前記第1の減圧機構、前記分岐部、前記第1の蒸発器を経て前記吸入側から前記圧縮機に吸入させる前記第1の放熱器の放熱運転と、前記吐出冷媒を前記第1のほう寝つき、前記第1の減圧機構、前記分岐部、前記第2の減圧機構、前記第2の蒸発器を経て前記吸入側から前記圧縮機に吸入させる前記第2の蒸発器の吸熱運転との並行運転である吸熱放熱並行運転を実行すると共に、
前記記憶部に記憶された前記制御期間情報と、前記記憶部に記憶された前記外部供給熱量と、前記演算部によって計算された前記現在の蓄熱量とに加え、さらに、前記第2の蒸発器に要求される負荷を示す冷房負荷とに基づいて、前記圧縮機の前記運転周波数を制御することを特徴とする請求項1記載の冷凍サイクル装置。 - 前記冷凍サイクル装置は、さらに、
前記貯湯タンクから前記第1の放熱器に流入し、前記第1の放熱器を通過して前記貯湯タンクに戻る水の流路となる水流路における前記第1の放熱器の出口から流出する流出水の温度を検出する出口温度センサを備え、
前記演算部は、
前記記憶部に記憶された前記制御期間情報と、前記記憶部に記憶された前記外部供給熱量と、前記演算部によって計算された前記現在の蓄熱量とに基づいて、目標とするべき前記流出水の温度を示す目標温度を計算し、
前記制御部は、
前記出口温度センサによって検出される前記流出水の温度が、前記演算部によって計算された前記目標温度になるように、前記圧縮機の運転周波数を制御することを特徴とする請求項7または8のいずれかに記載の冷凍サイクル装置。 - 冷媒を循環させる冷凍サイクル装置であって、
運転周波数の制御が可能な圧縮機と、貯湯タンクに蓄えられた水であるタンク水に前記冷媒によって熱量を供給する第1の放熱器と、第1の減圧機構と、第1の蒸発器とを有し、前記冷媒が前記圧縮機、前記第1の放熱器、前記第1の減圧機構、前記第1の蒸発器の順に循環する冷凍サイクル機構と、
予め設定された制御期間を示す制御期間情報を記憶する共に、他の情報を記憶可能な記憶部と
を備えた冷凍サイクル装置に対して、
演算部が、
所定の時刻を基準として前記タンク水によって外部に供給された熱量を示す外部供給熱量を所定の供給熱量計算規則に基づき計算し、計算した前記供給熱量を前記記憶部に記憶すると共に、前記タンク水が有する現在の蓄熱量を所定の蓄熱量計算規則に基づいて算出し、
制御部が、
前記記憶部に記憶された前記制御期間情報と、前記記憶部に記憶された前記供給熱量と、前記演算部によって計算された前記現在の蓄熱量とに基づいて、前記圧縮機の運転周波数を制御することを特徴とする冷凍サイクル制御方法。
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CN103370584B (zh) | 2015-11-25 |
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US20130312443A1 (en) | 2013-11-28 |
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