WO2014192052A1 - 空気調和装置 - Google Patents
空気調和装置 Download PDFInfo
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- WO2014192052A1 WO2014192052A1 PCT/JP2013/064595 JP2013064595W WO2014192052A1 WO 2014192052 A1 WO2014192052 A1 WO 2014192052A1 JP 2013064595 W JP2013064595 W JP 2013064595W WO 2014192052 A1 WO2014192052 A1 WO 2014192052A1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
- F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
- F24F11/81—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the air supply to heat-exchangers or bypass channels
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
- F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
- F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
- F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
- F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
- F24F11/86—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling compressors within refrigeration or heat pump circuits
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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
- F25B49/027—Condenser control arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
- F24F11/63—Electronic processing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2110/00—Control inputs relating to air properties
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/006—Compression machines, plants or systems with reversible cycle not otherwise provided for two pipes connecting the outdoor side to the indoor side with multiple indoor units
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/029—Control issues
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/029—Control issues
- F25B2313/0293—Control issues related to the indoor fan, e.g. controlling speed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/029—Control issues
- F25B2313/0294—Control issues related to the outdoor fan, e.g. controlling speed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/031—Sensor arrangements
- F25B2313/0314—Temperature sensors near the indoor heat exchanger
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/02—Compressor control
- F25B2600/021—Inverters therefor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/11—Fan speed control
- F25B2600/111—Fan speed control of condenser fans
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/15—Power, e.g. by voltage or current
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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
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
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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
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
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- 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
- the present invention relates to an air conditioner.
- control gain of PID control is determined in accordance with the difference between the opening value of the expansion valve, the compressor operating capacity, and the current value of the control target (for example, compressor discharge temperature) and the target value.
- a method of controlling the flow rate of refrigerant by driving the opening of an expansion valve has been proposed (see, for example, Patent Document 1).
- the following method has been proposed as a control method for changing the opening degree of the expansion valve in accordance with the deviation between the current value to be controlled and the target value.
- the target value of the control target increases, the target value of the control target is temporarily set to a temporary target value that is larger than the new target value, and the deviation between the current value and the new target value of the control target falls below a predetermined value
- a method has been proposed in which the temporary target value is changed to a new target value to be controlled to improve the responsiveness of the current value to the target value to be controlled (see, for example, Patent Document 2).
- the conventional air conditioner has the following problems.
- the control gain of PID control is a value unique to the system of the air conditioner.
- the values are constant (fixed values), and the effects of changes in operating conditions such as high and low pressures in the refrigeration cycle are taken into account.
- the amount of change in opening which is the operation amount of the expansion valve, is small, it takes a long time to reach the target value of the control target, and it takes time to realize a comfortable space. There was a problem.
- the operation target operated to reach the target value of the state quantity of the refrigeration cycle such as the temperature and pressure of the refrigerant to be controlled is not limited to the expansion valve, but includes a compressor, a condenser fan, The evaporator fan is also an operation target, and there is a similar problem in controlling the operation amount.
- the present invention has been made in view of such a point, and the object thereof is to suppress the overshoot in consideration of the operating state of the air conditioner, while the current value of the controlled object is quickly changed to the target value of the controlled object.
- an air conditioner for controlling the operation amount of the operation target is provided.
- the air conditioner according to the present invention includes a compressor, a condenser, an expansion valve, and an evaporator, and measures the refrigerant circuit in which the refrigerant circulates, the condenser fan, the evaporator fan, and the operating state quantity of the refrigerant circuit.
- the frequency of the compressor so that the current value of the control object that is one of the measurement values measured by the measurement part becomes the target value of the control object determined based on the other measurement values,
- a control unit that controls an operation amount of an operation target that is at least one of the opening degree of the expansion valve, the rotation speed of the condenser fan, and the rotation speed of the evaporator fan.
- the manipulated variable is determined with the upper limit as the target value, and when the current value is higher than the upper limit, the lower limit is targeted.
- the operation amount is determined as a value, and is set in advance after the current value falls within the settling range. The based on the reference allowable overshoot rate is overshooting ratio is what determines the operation amount.
- the present invention it is possible to control the operation amount of the operation target so that the current value of the control target quickly becomes the target value of the control target while suppressing the overshoot in consideration of the operating state of the air conditioner. it can.
- the air conditioner includes an outdoor unit 1 and an indoor unit 2.
- a compressor 3, a four-way valve 4 that switches between cooling and heating operation, an outdoor heat exchanger 5, an outdoor fan (evaporator fan or condenser fan) 6, and an expansion valve 7 are mounted in the outdoor unit 1.
- An indoor heat exchanger 9 and an indoor fan (condenser fan or evaporator fan) 10 are mounted in the indoor unit 2.
- a refrigerant is used as a heat transport medium in the refrigerant circuit of the air conditioner.
- the cooling / heating can be switched by switching the four-way valve 4, but the four-way valve 4 is not necessarily an essential configuration and can be omitted.
- the compressor 3 is a type in which the rotation speed is controlled by an inverter and the capacity is controlled. Some types of compressors have a constant rotational speed, but the present invention has the same effect as a type in which the rotational speed is capacity-controlled.
- the opening degree of the expansion valve 7 can be variably controlled.
- the outdoor heat exchanger 5 exchanges heat between the outdoor air blown by the outdoor fan 6 and the refrigerant.
- the indoor heat exchanger 9 exchanges heat between the indoor air blown by the indoor fan 10 and the refrigerant.
- the liquid pipe 8 and the gas pipe 11 are connection pipes that connect the outdoor unit 1 and the indoor unit 2.
- a plurality of temperature sensors and a control device 41 are installed in the outdoor unit 1.
- the temperature sensor 21 measures the piping temperature at the installation location on the discharge side of the compressor 3, the temperature sensor 22 is between the outdoor heat exchanger 5 and the expansion valve 7, and the temperature sensor 25 is on the suction side of the compressor 3. Guess the temperature.
- Temperature sensors 23 and 24 are installed in the indoor unit 2.
- the temperature sensor 23 is installed on the liquid pipe 8 side of the indoor heat exchanger 9, and the temperature sensor 24 is installed on the gas pipe 11 side of the indoor heat exchanger 9. Measure the piping temperature at the location and estimate the refrigerant temperature.
- pressure sensors 31 and 32 are installed in the outdoor unit 1, and the pressure sensor 31 measures the pressure of the refrigerant discharged from the compressor 3, and the pressure sensor 32 measures the pressure of the refrigerant sucked by the compressor 3.
- the control device 41 in the outdoor unit 1 includes a measurement unit 41a that measures operation information instructed by a user of each sensor or air conditioner, and the frequency of the compressor 3 and the outdoor fan based on the measured information source. 6 for controlling the frequency of the compressor 3, the flow of the four-way valve 4, the flow of the four-way valve 4, the rotational speed of the outdoor fan 6, the opening of the expansion valve 7, etc. 41b.
- FIG. 1 illustrates the case where the operation target is the expansion valve 7, and the dotted line is also connected to the compressor 3, the outdoor fan 6, and the indoor fan 10.
- the flow path of the four-way valve 4 is set in the direction of the solid line in FIG.
- the high-temperature and high-pressure gas refrigerant discharged from the compressor 3 condenses and liquefies through the four-way valve 4 while dissipating heat in the outdoor heat exchanger 5 serving as a condenser, and becomes high-pressure liquid refrigerant.
- the high-pressure refrigerant exiting the outdoor heat exchanger 5 is depressurized by the expansion valve 7, then flows into the indoor unit 2 via the liquid pipe 8, and flows into the indoor heat exchanger 9 serving as an evaporator, There it absorbs heat and evaporates. Cooling is performed by absorbing the heat of the load side medium such as air or water on the indoor unit 2 side. Thereafter, the gas flows into the outdoor unit 1 through the gas pipe 11. Then, it is sucked into the compressor 3 through the four-way valve 4.
- the flow path of the four-way valve 4 is set in the direction of the broken line in FIG.
- the high-temperature and high-pressure gas refrigerant discharged from the compressor 3 flows out of the outdoor unit 1 through the four-way valve 4 and flows into the indoor unit 2 through the gas pipe 11.
- the refrigerant flowing into the indoor unit 2 condenses and liquefies while dissipating heat in the indoor heat exchanger 9 serving as a condenser, and becomes a high-pressure liquid refrigerant. Heating is performed by dissipating heat from the load-side medium such as air or water on the indoor unit 2 side.
- the high-pressure refrigerant that has exited the indoor heat exchanger 9 flows into the outdoor unit 1 via the liquid pipe 8.
- the refrigerant flowing into the outdoor unit 1 is depressurized by the expansion valve 7 and then flows into the outdoor heat exchanger 5 serving as an evaporator, where it absorbs heat and is evaporated and gasified. Then, it is sucked into the compressor 3 through the four-way valve 4.
- FIG. 2 is a diagram showing an operation flow when the user operates the remote control in the air-conditioning apparatus according to Embodiment 1 of the present invention.
- FIG. 2 is an operation flow when the control target is the compressor discharge temperature and the operation target is the expansion valve 7.
- the control device 41 receives the indoor temperature and indoor air volume signals set by the user from the remote controller.
- the control device 41 sets the expansion valve 7 to a predetermined initial opening degree, and starts the compressor 3, the indoor fan 10, and the outdoor fan 6.
- the control device 41 determines the compressor frequency according to the deviation between the indoor set temperature and the indoor current temperature. The compressor frequency determined here is used when calculating the control gain K described later.
- the control device 41 determines the compressor discharge temperature based on the compressor discharge refrigerant pressure measured by the pressure sensor 31, the compressor suction refrigerant pressure measured by the pressure sensor 32, and a preset relational expression or table. Determine the target value. And the control apparatus 41 determines an expansion valve opening degree as mentioned later according to the deviation of the compressor discharge temperature (current value) detected by the temperature sensor 21 and the target value. Thereafter, the operations of S3 to S4 are repeated at each control interval. When the operation stop signal is received from the remote controller from the user, the operation flow of FIG.
- control target here, the expansion valve 7
- the control target here, the compressor discharge temperature
- FIG. 3 is an explanatory diagram of the control principle of the operation target.
- FIG. 3 shows the response characteristics of the control value (here, the compressor discharge temperature) when the operation amount of the operation target is changed for a plurality of patterns (1) to (3).
- the maximum value at which the control value exceeds the target value Tm is generally referred to as an overshoot amount or overshoot.
- the time until the control value falls within the settling range (here, ⁇ ⁇ T of the target value Tm) centered on the target value is referred to as the settling time.
- the deviation between the target value and the current value T is
- the line (1) passing through the point A has the smallest allowable overrun rate, and the control value has converged to the target value without reaching the upper limit value of the settling range.
- the line (2) passing through the point B has a larger allowable overrun rate than the line (1), and after the control value has just reached the upper limit value of the settling range, it has converged to the target value.
- the line (3) passing through the point C since the allowable overrun rate is too large, the control value converges to the target value after exceeding the upper limit value of the settling range.
- the settling time indicates the last time when the control value is within the settling range of the target value
- the points A, B, and C are the positions of the settling times in the respective conditions
- the line (2) It can be seen that the settling time is the shortest. Therefore, in the first embodiment, as shown by the line (2), the allowable overshoot rate at which the control value reaches the upper limit value of the settling range is set, and the control gain K is calculated based on the allowable overshoot rate. Then, the operation amount to be operated is determined based on the control gain K.
- FIG. 4 is a diagram showing the relationship between the control gain K and the allowable overshoot rate.
- the horizontal axis in FIG. 4 indicates the control gain K, and the vertical axis indicates the allowable overshoot rate.
- the allowable overshoot rate represents the ratio at which the compressor discharge temperature overshoots the target value.
- FIG. 4 is a diagram obtained from a result of simulation of the control gain K and the allowable overshoot rate using the control interval, the expansion valve opening degree, and the compressor frequency as fixed values.
- the control gain K When the control gain K is reduced, the change in the compressor discharge temperature becomes gradual and converges to the target value without overshooting the target value, so that the allowable overshoot rate is a minute value of 1% or less. .
- the allowable overshoot rate In less than the control gain K is a predetermined value K A, the allowable overshoot rate remains very small value.
- the control gain K In the control gain K is equal to or greater than the predetermined value K A, the allowable overshoot rate control gain K has a proportional relationship, the change of the compressor discharge temperature as the control gain K is increased becomes steeper, over the target value After shooting, it converges to the target value.
- control gain K is calculated based on the relational expression between the control gain K and the allowable overshoot rate acquired in advance. Can be determined.
- This relational expression is a relational expression having the control interval, the expansion valve opening degree, the compressor frequency, and the allowable overshoot rate as variables.
- the control gain K from relation is K B. Further, if the allowable overshoot rate is less than the ratio of the point A in FIG. 4, the control gain K is set to K A.
- control gain K for determining the operation amount of the operation target at which the control value just reaches the upper limit value of the settling range varies depending on the operation state.
- the control gain K is changed according to the operating state, and the control amount reaches the upper limit value of the settling range by determining the operation amount of the operation target using the changed control gain K.
- the “overshoot amount a” of the numerator of the above equation (1) for calculating the allowable overshoot rate is set to “settling range ⁇ T”.
- variable allowable overshoot rate Xa [%] and a preset reference allowable overshoot rate Xb [%] are introduced, and either one is selected according to the operating state, and the selected allowable overrun rate is selected.
- the control gain K is calculated using the rate to obtain the operation amount.
- the selected allowable overshoot rate is referred to as a set allowable overrun rate Y.
- variable allowable overshoot rate Xa is calculated as in the following equation (1).
- the reference allowable overshoot rate Xb is a preset fixed value, and is an overshoot ratio in which the current value of the control target is allowed with respect to the target value.
- the reference allowable overshoot rate Xb is set to, for example, 50% or 30% according to the use of the air conditioner, and is arbitrarily set, but a value less than 100% is set.
- the control value does not converge but diverges and does not reach the target value, and is set to a value less than 100%.
- FIG. 5 is an explanatory diagram of the difference in settling time when the set allowable overshoot rate Y is set to the variable allowable overshoot rate Xa and when the set allowable overshoot rate Xa is set to a value smaller than the variable allowable overrun rate Xa.
- (a) shows a case where the set allowable overshoot rate Y is a variable allowable overshoot rate Xa
- (b) shows a case where the set allowable overshoot rate Y is a value smaller than the variable allowable overshoot rate Xa.
- the control of the air conditioner is controlled at a certain control interval.
- the target value for each control interval is hereinafter referred to as an allowable value.
- the allowable value differs between the case where the variable allowable overshoot rate Xa is set as the set allowable overshoot rate Y and the case where the reference allowable overshoot rate Xb is set.
- the allowable value is calculated by the following equation (2) using the set allowable overshoot rate Y.
- the allowable value Ta is as follows.
- the allowable value is lower than the upper limit value 55 ° C. of the settling range.
- variable allowable overshoot rate Xa is set as the set allowable overshoot rate Y, and the reference allowable overshoot rate Xb is set for each control interval. A change in the allowable value will be described.
- FIG. 6 shows the change in the allowable value (target value) Ta for each control interval when the variable allowable overshoot rate Xa is set to the set allowable overshoot rate Y when the current value is lower than the lower limit value of the settling range. It is a figure.
- the interval between plot points is the control interval.
- the operation amount of the operation target calculated based on the variable allowable overshoot rate Xa is specifically determined as an operation amount for setting the control value to the allowable value Ta.
- allowable overshoot rate Y variable allowable overshoot rate Xa
- the allowable value Ta is the upper limit value of the settling range.
- the set allowable overshoot rate Y variable permissible overrun rate Xa
- the allowable value is the lower limit value of the settling range.
- the upper limit value or the lower limit value of the settling range is set as the next allowable value according to the magnitude relationship between the current value and the target value.
- the set allowable overshoot rate Y at time t2 is the variable allowable overshoot rate Xa or the reference allowable overshoot rate Xb. Since the control value is within the settling range at time t2, when the variable allowable overshoot rate Xa is set to the set allowable overrun rate Y, the current value exceeds the target value, so the lower limit value of the settling range is The next manipulated variable is determined such that the allowable value Ta is set and the compressor discharge temperature becomes the allowable value Ta.
- variable allowable overshoot rate Xa is set to the set allowable overshoot rate Y after t2 when the current value falls within the settling range
- the upper limit value and the lower limit value of the settling range are controlled alternately to allow values, and compression is performed.
- the machine discharge temperature diverges without converging on the target value.
- the reference allowable overshoot rate Xb is set to the set allowable overshoot rate Y.
- the allowable value Ta gradually increases and closes to the target value Tm while passing up and down the target value Tm at each control interval, and the compressor discharge temperature also goes up and down similarly through the target value Tm. However, it gradually converges to the target value Tm.
- FIG. 7 shows a change in the allowable value (target value) Ta for each control interval when the reference allowable overshoot rate Xb is set to the set allowable overshoot rate Y when the current value is lower than the lower limit value of the settling range. It is a figure.
- the plot points are the control intervals.
- FIG. 8 is a control flowchart of the expansion valve of the air-conditioning apparatus according to Embodiment 1 of the present invention.
- FIG. 8 corresponds to the details of the operation of the expansion valve 7 in S4 shown in FIG.
- the control device 41 reads a preset compressor discharge temperature limit value Tb.
- the limit value Tb is determined as an upper limit value that allows safe operation of the device to be continued without entering protection control for avoiding damage to the device to be controlled (here, the compressor 3).
- a settling range ⁇ T set in advance as an index indicating the stability of the current value is read in the same manner.
- the preset reference allowable overshoot rate Xb is read in the same manner.
- the control device 41 calculates the upper limit value Tmmax of the target value of the compressor discharge temperature.
- the upper limit value Tmmax of the target value is expressed by the following equation (3) by the limit value Tb and the settling range ⁇ T. For this reason, even if the value calculated as the target value in the next S4-3 is equal to the upper limit value Tmmax, the upper limit value of the settling range set with the target value as the center will not be greater than the limit value Tb. Absent.
- a target value Tm of the compressor discharge temperature is calculated. To do.
- the upper limit value Tmmax of the target value is set as the target value Tm.
- the measurement unit 41a measures the current value (compressor discharge temperature T) from the temperature sensor 21.
- control device 41 calculates the variable allowable overshoot rate Xa from the above equation (1) from the settling range ⁇ T, the target value Tm of the compressor discharge temperature, and the current value T of the compressor discharge temperature.
- the control device 41 sets the setting allowable overshoot rate Y.
- the control device 41 sets the variable calculation allowable overshoot rate Xa to the set allowable overshoot rate Y when the current value is smaller than the lower limit value of the settling range, and the reference allowable when the current value is greater than or equal to the lower limit value of the settling range.
- the overshoot rate Xb is set to the set allowable overshoot rate Y.
- the controller 41 sets the allowable allowable overrun rate Y, each value obtained from the operating state of the refrigeration cycle, and a relational expression obtained in advance (the relational expression in FIG.
- the control gain K is calculated based on the opening degree, the compressor frequency, and the allowable overshoot rate (a function having the set allowable overshoot rate Y) as variables.
- the control device 41 calculates the expansion valve operation amount ⁇ LP based on the deviation between the target value Tm of the compressor discharge temperature and the current value T and the control gain K.
- the control device 41 calculates the expansion valve opening LP by adding the operation amount ⁇ LP calculated in S4-8 to the current expansion valve opening LPnow. And the control apparatus 41 sets the opening degree of the expansion valve 7 to the calculated expansion valve opening degree LP in the control part 41b.
- the discharge temperature of the compressor tends to be lower as the outdoor temperature is lower, the difference between the current value T and the target value Tm becomes larger as the outdoor temperature is lower.
- the excess rate Xa tends to be small.
- the variable allowable overshoot rate Xa is set to the set allowable overshoot rate Y. Therefore, when the variable allowable overshoot rate Xa is small, the set allowable overshoot rate Y Similarly, the control gain K proportional to is also reduced.
- the variable overrun rate Xa increases from the equation (1) as the current value approaches the lower limit value of the settling range. Therefore, while the current value is smaller than the lower limit value of the settling range, the control gain K that is proportional to the set allowable overshoot rate Y is similarly increased. For this reason, the operation amount ⁇ LP of the operation target is increased as compared with the conventional case where the control gain is a fixed value, and the current value can be quickly reached the target value.
- control gain K is calculated by the function having the control interval, the opening degree of the expansion valve, the compressor frequency, and the allowable overrun rate Y as variables. can do. That is, since the operation amount of the expansion valve does not become too small in the low load operation where the set temperature is close to the room temperature, the problem that it takes time to reach the target value of the control target can be solved.
- the control device 41 determines the expansion valve operation amount according to the deviation between the current value of the compressor discharge temperature and the target value, so that the operation amount is ensured as compared with Patent Document 1. It is possible to realize energy-saving operation at an early stage. Further, the control device 41 increases the operation amount within a range not exceeding the allowable value even if the deviation between the current value of the compressor discharge temperature and the target value is a predetermined value or less. Can be realized early. In addition, since the expansion valve 7 is controlled so as to quickly reach the desired refrigeration cycle, the device reliability of the expansion valve 7 is improved by shortening the number of operations of the expansion valve 7.
- the case where the initial value of the compressor discharge temperature is lower than the target value Tm and the upper limit value is set as the limit value in the time change of the compressor discharge temperature has been described.
- the same can be applied to the case where the initial value is higher than the target value Tm and the lower limit value is provided as the limit value. That is, while the current value is higher than the upper limit value of the settling range, the variable allowable overshoot rate Xa is calculated using the lower limit value of the settling range as the target value, and the control gain K is calculated based on the variable allowable overshoot rate Xa.
- the operation amount may be determined.
- Embodiment 2 when the target value Tm calculated in S4-3 of FIG. 8 is larger than the upper limit value Tmmax of the target value Tm, the target value Tm is restricted to the upper limit value Tmmax of the target value. This is because the fixed value set in advance is used as the settling range, and the upper limit value Tmmax is obtained by the above equation (3). Therefore, in the second embodiment, when the current value T approaches the target value Tm, the settling range is reduced, thereby increasing the upper limit value Tmmax of the target value and quickly bringing the current value T close to the original target value. In this way, further energy-saving operation is achieved.
- the configuration of the air conditioner of the second embodiment is the same as that of the first embodiment shown in FIG. In the following, the second embodiment will be described focusing on the differences from the first embodiment.
- FIG. 9 is a control flowchart of the operation amount of the operation target in the air-conditioning apparatus according to Embodiment 2 of the present invention.
- S4-1 to S4-4 are the same as those in the flowchart of FIG.
- S4-a if the controller 41 determines that the compressor discharge temperature is lower than the value obtained by subtracting the settling range ⁇ T from the upper limit value Tmmax of the target value, the process proceeds to S4-5, and the subsequent steps are the same as in the flowchart of FIG. is there.
- the compressor discharge temperature target value Tm2 is newly calculated.
- the variable allowable overshoot rate Xa2 is calculated from the settling range ⁇ T2 and target value Tm2 after the change, and the current value T (compressor discharge temperature) measured in S4-4. Thereafter, the process proceeds to S4-6, and the subsequent steps are the same as those in the flowchart of FIG.
- FIG. 10 is a diagram illustrating a change over time in the control value when the settling range ⁇ T is changed in the middle of the air-conditioning apparatus according to Embodiment 2 of the present invention.
- FIG. 10 shows the time variation of the control value when the compressor frequency is relatively high and the target value Tm is equal to the upper limit value Tmmax of the target value.
- the current value T of the control value compressor discharge temperature
- the settling range ⁇ T is the same as S4-1 in the flowchart of FIG. 9 in order to satisfy the relationship of S4-a in the flowchart of FIG.
- the target value Tm is the same as the upper limit value Tmmax of the target value obtained from the setting range ⁇ T in S4-1.
- the process proceeds to S4-b and the settling range ⁇ T is changed to ⁇ T2.
- the case where the upper limit value of the target value of the control target is increased when the current value of the control target approaches the target value from the side lower than the target value has been described.
- the lower limit value of the target value to be controlled may be lowered.
- the compressor discharge temperature is taken as an example as the allowable value Ta, the target value Tm, and the current value T.
- Compressor discharge superheat degree, high pressure, low pressure, compression ratio, compressor current value can be similarly implemented by giving a limit value and a settling range ⁇ T to the control device 41, and does not depart from the scope of the present invention. Absent.
- the next value predicted from the past value of the control target and the current value of the control target may be used instead of the current value of the control target within the settling range. In this case, convergence can be further improved.
- the next value prediction method for example, a case where three-point prediction is used will be described below.
- FIG. 11 is a diagram illustrating a next value prediction method for predicting the next value from the current value, the previous value, and the last time value to be controlled.
- the three-point prediction is based on a deviation between the previous value Told2 and the previous value Told1 based on the deviation between the previous value Told2 and the previous value Told1 using the three points of the previous value Told2, the previous value Told1, and the current value Tnow collected at regular control intervals.
- the next value Tnew is predicted according to the deviation ratio as shown in the following equation (5).
- Tnew Tnow + (Tnow ⁇ Told1) 2 / (Told1 ⁇ Told2) (5)
- the control device 41 decreases the control gain K when the next value Tnew exceeds the allowable overshoot amount.
- FIG. 12 is a chart showing the specific heat ratio of the refrigerant used in the refrigeration cycle of the air-conditioning apparatus according to each embodiment of the present invention.
- the refrigerant used in the refrigeration cycle of the air conditioner has a larger specific heat ratio and higher compressor discharge temperature than the R22 refrigerant currently used in overseas models, for example, R32 refrigerant.
- An easy refrigerant has the following advantages.
Abstract
Description
以下、本発明の実施形態を図面に基づいて詳細に説明する。
空気調和装置は、室外機1と室内機2とを備えている。室外機1内には圧縮機3、冷房と暖房の運転切換を行う四方弁4、室外熱交換器5、室外ファン(蒸発器ファン又は凝縮器ファン)6、膨張弁7が搭載されている。また、室内機2内には室内熱交換器9、室内ファン(凝縮器ファン又は蒸発器ファン)10が搭載されている。また、本空気調和装置の冷媒回路内には熱輸送媒体として冷媒を使用している。なお、図1では四方弁4の切換えにより冷暖房を切換え可能な構成としたが、四方弁4は必ずしも必須の構成ではなく、省略可能である。
冷房運転時には、四方弁4の流路は図1の実線方向に設定される。そして圧縮機3から吐出された高温高圧のガス冷媒は、四方弁4を経て凝縮器となる室外熱交換器5で放熱しながら凝縮液化し高圧の液冷媒となる。室外熱交換器5を出た高圧の冷媒は、膨張弁7で減圧された後、液配管8を経由して、室内機2に流入し、蒸発器となる室内熱交換器9に流入し、そこで吸熱し、蒸発ガス化される。室内機2側の空気や水などの負荷側媒体の熱を吸熱することで冷房を行う。その後、ガス配管11を経て室外機1に流入する。そして、四方弁4を経て、圧縮機3に吸入される。
S1では、制御装置41がリモコンから使用者により設定された室内温度、室内風量の信号を受け取る。S2では、制御装置41は膨張弁7を決められた初期開度にして、圧縮機3、室内ファン10、室外ファン6を起動する。S3では、制御装置41は室内設定温度と室内現在温度との偏差に応じて圧縮機周波数を決定する。ここで決定された圧縮機周波数は、後述の制御ゲインKの算出時に使用される。
制御値が目標値Tmを超えた最大値は、行過ぎ量あるいはオーバーシュートと一般的に言われている。また、制御値が目標値を中心として、所望の許容範囲である整定範囲(ここでは目標値Tmの±ΔT)内に収まるまでの時間は、整定時間と言われている。目標値と現在値Tとの偏差を|T-Tm|、オーバーシュート量a(図3では、線(3)のオーバーシュート量のみを図示)とし、a/|T-Tm|を許容行過ぎ率として定義する。
可変許容行過ぎ率Xa[%]=|(整定範囲ΔT)/(現在値T-目標値Tm)|×100
・・・(1)
但し、T=TmのときはXa=0%とする。
空気調和装置の制御は、ある制御間隔で制御される。その制御間隔毎の目標値を以下では許容値という。許容値は、設定許容行過ぎ率Yとして可変許容行過ぎ率Xaが設定される場合と、基準許容行過ぎ率Xbが設定される場合とで値が異なる。許容値は、設定許容行過ぎ率Yを用いて以下の(2)式で算出される。
Ta=Tm - Y(T-Tm) ・・・(2)
許容値=Tm-Y(T-Tm)
=Tm-|ΔT/(T-Tm))|×(T-Tm)
=Tm-(-ΔT)=Tm+ΔT=整定範囲の上限値
許容値=50-0.1(30-50)=52℃
この場合、許容値が整定範囲の上限値55℃よりも低くなってしまう。
許容値=50-0.5(30-50)=60℃
この場合、許容値が整定範囲の上限値を超えてしまう。
Xa=|5/(30-50)|×100=25%
許容値=55℃=整定範囲の上限値
図6に示すように、現在値Tが時間t1のとき、現在値Tは整定範囲の下限値より低いため、可変許容行過ぎ率Xaが設定許容行過ぎ率Yに設定され、許容値Taは(2)式より整定範囲の上限値となる。よって、可変許容行過ぎ率Xaに基づいて算出される操作対象の操作量は、具体的には制御値を許容値Taとするための操作量が決定されることになる。
現在値Tが時間t1で、例えば基準許容行過ぎ率Xb(<可変許容行過ぎ率Xa)を設定許容行過ぎ率Yに設定した場合、許容値Taは目標値より高く、整定範囲の上限値より低い値となる。そして、制御値が許容値Taとなるように次の操作量を決定する。t2以降においては図6と同様である。
まずS4-1では、制御装置41が、あらかじめ設定した圧縮機吐出温度の限界値Tbを読み込む。限界値Tbは制御対象の機器(ここでは圧縮機3)の損傷を回避するための保護制御に入らず、機器の安全運転継続可能な上限値として定める。また、現在値の安定を示す指標としてあらかじめ設定した整定範囲ΔTも同様に読み込む。また、あらかじめ設定した基準許容行過ぎ率Xbも同様に読み込む。
Tmmax=Tb-ΔT ・・・(3)
実施の形態1では、図8のS4-3で算出した目標値Tmが目標値Tmの上限値Tmmaxより大きくなるときは、目標値Tmを目標値の上限値Tmmaxに規制している。これは、予め設定した固定値を整定範囲としており、上限値Tmmaxを前記(3)式で求めているためである。そこで、本実施の形態2は、現在値Tが目標値Tmに近づいたときに整定範囲を小さくすることで、目標値の上限値Tmmaxを上げて現在値Tを迅速に本来の目標値に近づけるようにし、更なる省エネ運転を図ったものである。
図9においてS4-1~S4-4は図8のフローチャートと同一である。S4-aでは制御装置41は、圧縮機吐出温度が目標値の上限値Tmmaxから整定範囲ΔTを減算した値より低いと判定した場合はS4-5へ進み、以降は図8のフローチャートと同一である。
ΔT2=ΔT×Xb(Xb<100%) ・・・ (4)
制御値(圧縮機吐出温度)の現在値Tが点Aの場合、前記図9のフローチャートのS4-aの関係を満たすため、整定範囲ΔTは前記図9のフローチャートのS4-1と同一である。また、目標値Tmは前記S4-1の整定範囲ΔTより得られる目標値の上限値Tmmaxと同一である。
上記実施の形態1、2では、整定範囲内において、制御対象の現在値の代わりに、制御対象の過去の値と制御対象の現在値より予測した次回値を用いてもよい。この場合、より収束性を高めることができる。次回値の予測方法として、例えば、3点予測を用いた場合について以下に説明する。
3点予測とは、一定の制御間隔ごとに収集される現在値の前々回値Told2、前回値Told1、現在値Tnowの3点を用いて、前々回値Told2と前回値Told1の偏差より、前回値Told1と現在値Tnowの偏差が小さい場合に、偏差の比に応じて下記の(5)式のように次回値Tnewを予測する方法である。
Tnew = Tnow + (Tnow -Told1)2/(Told1 -Told2)
・・・ (5)
図12は、本発明の各実施の形態の空気調和装置の冷凍サイクルに使用する冷媒の比熱比を示す図表である。
空気調和装置の冷凍サイクルに使用する冷媒として、図12に示すように、例えばR32冷媒のように、現在海外機種で使用されているR22冷媒よりも比熱比が大きく、圧縮機吐出温度が高くなりやすい冷媒において以下の利点がある。それは、圧縮機吐出温度を制御対象とする場合、許容行過ぎ率の設定により、圧縮機吐出温度の異常な過昇を防ぐことができる点と、圧縮機吐出温度が高くならない運転状態において、圧縮機吐出温度を迅速に圧縮機吐出温度の目標値Tmに到達させることで快適性を向上させることができる点の2点である。
Claims (5)
- 圧縮機、凝縮器、膨張弁、蒸発器を有し、冷媒が循環する冷媒回路と、
凝縮器ファンと、
蒸発器ファンと、
前記冷媒回路の運転状態量を計測する計測部と、
前記計測部で計測された計測値の一つである制御対象の現在値が、それ以外の計測値に基づいて決定した前記制御対象の目標値となるように、前記圧縮機の周波数、前記膨張弁の開度、前記凝縮器ファンの回転数、前記蒸発器ファンの回転数の少なくとも一つである操作対象の操作量を制御する制御部とを備え、
前記制御部は、
前記現在値が前記目標値を中心として設定された整定範囲の上限値と下限値のうちの前記下限値より低い間は、前記上限値を目標値として前記操作量を決定し、
前記現在値が、前記上限値より高い間は、前記下限値を目標値として前記操作量を決定し、
前記現在値が前記整定範囲内に入って以降は、予め設定されたオーバーシュート比率である基準許容行過ぎ率に基づいて前記操作量を決定する
ことを特徴とする空気調和装置。 - 前記制御部は、
前記現在値が前記整定範囲から外れている間の前記操作量の決定に際しては、前記整定範囲を前記現在値と前記目標値との差分で除算した可変許容行過ぎ率を演算し、前記可変許容行過ぎ率に基づいて、前記操作量を決定するための制御ゲインを演算し、前記制御ゲインに基づいて前記操作量を決定し、
前記現在値が、前記整定範囲内に入って以降の前記操作量の決定に際しては、前記基準許容行き過ぎ率に基づいて、前記操作量を決定するための制御ゲインを演算し、前記制御ゲインに基づいて前記操作量を決定する
ことを特徴とする請求項1記載の空気調和装置。 - 前記制御部は、
前記制御対象の現在値が前記目標値に近づいたときに、前記制御対象の目標値の上限値を現在よりも高く、又は前記制御対象の目標値の下限値を現在よりも低くする
ことを特徴とする請求項1又は請求項2記載の空気調和装置。 - 前記制御部は、
制御間隔毎に、現在値の過去の値と現在値とより次回値を予測して、前記次回値が許容オーバーシュート量を超える場合、前記制御ゲインを小さくすることを特徴とする請求項2、請求項2に従属する請求項3記載の空気調和装置。 - 前記制御部は、前記制御ゲインを演算する際に、更に、制御間隔と、膨張弁開度と、圧縮機周波数とを用いる
ことを特徴とする請求項2又は請求項4記載の空気調和装置。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2013/064595 WO2014192052A1 (ja) | 2013-05-27 | 2013-05-27 | 空気調和装置 |
JP2015519507A JP6109307B2 (ja) | 2013-05-27 | 2013-05-27 | 空気調和装置 |
US14/787,291 US20160153686A1 (en) | 2013-05-27 | 2013-05-27 | Air-conditioning apparatus |
CN201380076928.1A CN105378392B (zh) | 2013-05-27 | 2013-05-27 | 空调装置 |
EP13885584.6A EP3006847B1 (en) | 2013-05-27 | 2013-05-27 | Air-conditioning device |
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PCT/JP2013/064595 WO2014192052A1 (ja) | 2013-05-27 | 2013-05-27 | 空気調和装置 |
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WO2014192052A1 true WO2014192052A1 (ja) | 2014-12-04 |
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US (1) | US20160153686A1 (ja) |
EP (1) | EP3006847B1 (ja) |
JP (1) | JP6109307B2 (ja) |
CN (1) | CN105378392B (ja) |
WO (1) | WO2014192052A1 (ja) |
Cited By (1)
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WO2022196813A1 (ja) * | 2021-03-18 | 2022-09-22 | ダイキン工業株式会社 | 補正装置、予測装置、方法、プログラム、および補正モデル |
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KR20160084149A (ko) * | 2015-01-05 | 2016-07-13 | 엘지전자 주식회사 | 냉장고의 제어방법 |
WO2018230281A1 (ja) * | 2017-06-12 | 2018-12-20 | 日立ジョンソンコントロールズ空調株式会社 | 空調システム、空調方法、及び制御装置 |
CN111356885B (zh) * | 2017-11-22 | 2022-02-01 | 三菱电机株式会社 | 空调机 |
CN110906515B (zh) * | 2019-11-29 | 2021-07-23 | 四川长虹空调有限公司 | 空调的制冷除湿切换方法及系统 |
CN113686066B (zh) * | 2021-08-27 | 2023-04-07 | 经纬恒润(天津)研究开发有限公司 | 一种热泵系统控制方法及装置 |
CN114659229A (zh) * | 2022-04-19 | 2022-06-24 | 重庆美的通用制冷设备有限公司 | 中央空调、中央空调的控制方法和装置、可读存储介质 |
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- 2013-05-27 WO PCT/JP2013/064595 patent/WO2014192052A1/ja active Application Filing
- 2013-05-27 CN CN201380076928.1A patent/CN105378392B/zh active Active
- 2013-05-27 EP EP13885584.6A patent/EP3006847B1/en active Active
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WO2022196813A1 (ja) * | 2021-03-18 | 2022-09-22 | ダイキン工業株式会社 | 補正装置、予測装置、方法、プログラム、および補正モデル |
JP2022145655A (ja) * | 2021-03-18 | 2022-10-04 | ダイキン工業株式会社 | 補正装置、予測装置、方法、プログラム、および補正モデル |
JP7284435B2 (ja) | 2021-03-18 | 2023-05-31 | ダイキン工業株式会社 | 補正装置、予測装置、方法、プログラム、および補正モデル |
Also Published As
Publication number | Publication date |
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JPWO2014192052A1 (ja) | 2017-02-23 |
EP3006847B1 (en) | 2021-03-31 |
EP3006847A1 (en) | 2016-04-13 |
US20160153686A1 (en) | 2016-06-02 |
EP3006847A4 (en) | 2017-01-18 |
CN105378392B (zh) | 2018-10-26 |
CN105378392A (zh) | 2016-03-02 |
JP6109307B2 (ja) | 2017-04-05 |
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