WO2011070962A1 - 空気調和機、膨張弁の開度制御方法および膨張弁の開度制御プログラムを記録したコンピュータ読み取り可能な記録媒体 - Google Patents
空気調和機、膨張弁の開度制御方法および膨張弁の開度制御プログラムを記録したコンピュータ読み取り可能な記録媒体 Download PDFInfo
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- WO2011070962A1 WO2011070962A1 PCT/JP2010/071562 JP2010071562W WO2011070962A1 WO 2011070962 A1 WO2011070962 A1 WO 2011070962A1 JP 2010071562 W JP2010071562 W JP 2010071562W WO 2011070962 A1 WO2011070962 A1 WO 2011070962A1
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- Prior art keywords
- expansion valve
- temperature
- discharge temperature
- opening
- air conditioner
- Prior art date
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- 238000000034 method Methods 0.000 title description 17
- 239000003507 refrigerant Substances 0.000 claims abstract description 48
- 238000001816 cooling Methods 0.000 claims description 17
- 238000010438 heat treatment Methods 0.000 claims description 15
- 238000004378 air conditioning Methods 0.000 claims 1
- 230000001105 regulatory effect Effects 0.000 abstract 1
- 238000010586 diagram Methods 0.000 description 12
- 238000004364 calculation method Methods 0.000 description 10
- 238000001704 evaporation Methods 0.000 description 8
- 230000008020 evaporation Effects 0.000 description 8
- 230000006870 function Effects 0.000 description 8
- 230000006835 compression Effects 0.000 description 7
- 238000007906 compression Methods 0.000 description 7
- 230000005494 condensation Effects 0.000 description 6
- 238000009833 condensation Methods 0.000 description 6
- 239000007788 liquid Substances 0.000 description 5
- 239000012071 phase Substances 0.000 description 4
- 229920006395 saturated elastomer Polymers 0.000 description 4
- 238000012545 processing Methods 0.000 description 3
- 239000011555 saturated liquid Substances 0.000 description 3
- 238000012937 correction Methods 0.000 description 2
- 238000002474 experimental method Methods 0.000 description 2
- 239000007791 liquid phase Substances 0.000 description 2
- 230000005284 excitation Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000003287 optical effect Effects 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 239000013526 supercooled liquid Substances 0.000 description 1
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
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
- F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
- F25B41/35—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators by rotary motors, e.g. by stepping motors
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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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2140/00—Control inputs relating to system states
- F24F2140/20—Heat-exchange fluid temperature
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
- F25B2600/21—Refrigerant outlet evaporator temperature
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion valves
-
- 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
-
- 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, an expansion valve opening control method, and a program, and more particularly to an air conditioner that adjusts the flow rate of refrigerant by controlling the expansion valve opening, an expansion valve opening control method, and a program.
- an air conditioner that adjusts the flow rate of refrigerant by controlling the expansion valve opening, an expansion valve opening control method, and a program.
- an air conditioner includes components such as a compressor, a four-way (switching) valve, an outdoor heat exchanger, an expansion valve that adjusts the flow rate of refrigerant when decompressing, and an indoor heat exchanger.
- a compressor a four-way (switching) valve
- an outdoor heat exchanger an expansion valve that adjusts the flow rate of refrigerant when decompressing
- an indoor heat exchanger an indoor heat exchanger.
- Refrigerant flow path (cooling cycle) in which refrigerant circulates in the order of compressor, four-way valve, outdoor heat exchanger (condenser), expansion valve, indoor heat exchanger (evaporator), four-way valve, and compressor during cooling cycle operation
- the pipe is connected so as to be configured. Thereby, the heat absorbed by the indoor heat exchanger is released to the outside by the outdoor heat exchanger.
- a refrigerant flow path in which the refrigerant circulates in the order of the compressor, the four-way valve, the indoor heat exchanger (condenser), the expansion valve, the outdoor heat exchanger (evaporator), the four-way valve, and the compressor. Cycle).
- the outdoor heat absorbed by the outdoor heat exchanger is released indoors by the indoor heat exchanger.
- the degree of superheat is calculated by detecting the temperature of the evaporator and the outlet temperature of the evaporator, and the opening degree of the expansion valve is controlled using the degree of superheat. Is common.
- Patent Document 1 estimates and estimates the evaporation saturation temperature by detecting the inlet temperature of the expansion valve and the outlet temperature of the expansion valve (or the inlet temperature of the evaporator). It describes that the target suction temperature of the compressor is determined from the evaporation saturation temperature and the set superheat degree, and the opening degree of the expansion valve is controlled so that the suction temperature of the compressor matches the target suction temperature.
- Patent Document 2 describes that the opening degree of the expansion valve is controlled according to the temperature difference between the refrigerant discharge refrigerant temperature and the optimum discharge refrigerant temperature calculated based on the evaporation temperature and the condensation temperature. Has been.
- a temperature sensor such as a thermistor is required at each of the inlet and outlet of the evaporator.
- Patent Document 2 describes that the opening degree of the expansion valve is controlled by detecting the discharge refrigerant temperature, the evaporation temperature, and the condensing temperature, and that the opening degree of the expansion valve is controlled by a temperature difference between two locations. Absent.
- the present invention has been made to solve the above-described problems, and an object thereof is an air conditioner that can appropriately control the opening degree of an expansion valve without increasing the number of temperature sensors. It is to provide an expansion valve opening control method and program.
- An air conditioner includes a compressor for compressing a refrigerant, an expansion valve for adjusting the flow rate of the refrigerant, a first temperature sensor for detecting a discharge temperature of the compressor, A second temperature sensor for detecting the temperature of the condenser; and a control means for controlling the opening of the expansion valve.
- the control means includes a discharge temperature and a second temperature detected by the first temperature sensor. The difference between the temperature of the condenser detected by the temperature sensor is calculated as a discharge temperature difference, and based on the calculated discharge temperature difference and the target discharge temperature difference set to achieve the target superheat degree.
- the opening of the expansion valve in normal control is set as the basic opening.
- the control means controls the opening of the expansion valve in a direction that opens more than the basic opening in the normal control.
- the control means controls the opening of the expansion valve in a direction to reduce the basic opening in the normal control.
- the second threshold is smaller than the first threshold.
- the control means calculates the target discharge temperature difference based on the rotation speed of the compressor.
- the outdoor heat exchanger for exchanging heat between the outdoor air and the refrigerant, and the indoor air and the refrigerant
- an indoor heat exchanger for exchanging heat.
- the condenser corresponds to an outdoor heat exchanger
- the condenser corresponds to an indoor heat exchanger.
- An expansion valve opening control method includes an expansion valve for adjusting the flow rate of the refrigerant, a first temperature sensor for detecting the discharge temperature of the compressor, and the temperature of the condenser.
- a method for controlling the opening degree of an expansion valve in an air conditioner including a second temperature sensor for detecting the discharge temperature detected by the first temperature sensor and the second temperature sensor. Based on the step of calculating the difference between the temperature of the condenser detected by the discharge temperature difference as a discharge temperature difference, the calculated discharge temperature difference, and the target discharge temperature difference set to be the target superheat degree, Setting the opening of the expansion valve in normal control as the basic opening.
- the present invention is a computer-readable recording medium recording an expansion valve opening degree control program.
- the expansion valve opening degree control program includes an expansion valve for adjusting the flow rate of the refrigerant, a first temperature sensor for detecting the discharge temperature of the compressor, and a second temperature for detecting the temperature of the condenser.
- the difference between the discharge temperature detected by the first temperature sensor and the temperature of the condenser detected by the second temperature sensor in a computer provided in the air conditioner is provided.
- the opening degree of the expansion valve in the normal control is basically opened. And a step of setting as a degree.
- the opening degree of the expansion valve based on the difference between the discharge temperature of the compressor and the temperature of the condenser (discharge temperature difference) and the target discharge temperature difference set to be the target superheat degree, the opening degree of the expansion valve Therefore, the opening degree of the expansion valve can be appropriately controlled without increasing the number of temperature sensors.
- FIG. 1 is a diagram schematically showing a refrigerant circuit in an air conditioner according to an embodiment of the present invention.
- an air conditioner includes an outdoor unit side heat exchanger (hereinafter referred to as “outdoor heat exchanger”) 1, an expansion valve 2, and an indoor unit side heat exchanger (hereinafter referred to as “indoor heat exchange”). 3), a four-way valve 4, and a compressor 5, which are sequentially connected in a closed loop.
- the compressor 5 compresses the refrigerant.
- the outdoor heat exchanger 1 exchanges heat between outdoor air and refrigerant.
- the expansion valve 2 is controlled to adjust the flow rate of the refrigerant.
- the indoor heat exchanger 3 exchanges heat between indoor air and refrigerant.
- the four-way valve 4 switches the circulation direction of the refrigerant in the cooling cycle operation and the heating cycle operation.
- the air conditioner further measures the temperature sensor 6 for measuring the temperature of the outdoor heat exchanger 1, the temperature sensor 7 for measuring the discharge temperature of the compressor 5, and the temperature of the indoor heat exchanger 3. Temperature sensor 8. These temperature sensors 6, 7, 8 are, for example, thermistors.
- the refrigerant flows in the order of the compressor 5, the four-way valve 4, the outdoor heat exchanger 1, the expansion valve 2, the indoor heat exchanger 3, the four-way valve 4, and the compressor 5. Patrol.
- the outdoor heat exchanger 1 functions as a condenser for condensing and liquefying the compressed high-temperature refrigerant
- the indoor heat exchanger 3 evaporates the liquefied refrigerant so that the refrigerant is cooled to a low temperature. It functions as an evaporator for changing to gas.
- the refrigerant circulates in the order of the compressor 5, the four-way valve 4, the indoor heat exchanger 3, the expansion valve 2, the outdoor heat exchanger 1, the four-way valve 4, and the compressor 5.
- the outdoor heat exchanger 1 functions as an evaporator and the indoor heat exchanger 3 functions as a condenser.
- the heating cycle operation and the cooling cycle operation are described as being switchable, but the air conditioner may be capable of only one of the heating cycle operation and the cooling cycle operation.
- the functions of the outdoor heat exchanger 1 and the indoor heat exchanger 3 are fixed as a condenser or an evaporator.
- FIG. 2 is an external view of the indoor unit 100 of the air conditioner according to the embodiment of the present invention.
- FIG. 3 is a cross-sectional view schematically showing the internal configuration of the indoor unit 100 of FIG.
- FIG. 3 is a cross-sectional view of the indoor unit 100 viewed from the Y-axis direction of FIG.
- indoor unit 100 in addition to indoor heat exchanger 3 and temperature sensor 8 shown in FIG. 1, indoor unit 100 includes a temperature sensor 11 for measuring room temperature, an indoor fan 14, a louver 15, And a louver motor 16.
- Louver 15 is a wind direction guide member provided at the outlet of indoor unit 100.
- the louver motor 16 rotationally drives the louver 15.
- the plurality of louvers 15 are driven to face in the same direction.
- FIG. 4 is an external view of the outdoor unit 200 of the air conditioner in the embodiment of the present invention.
- FIG. 5 is a diagram schematically showing the internal configuration of the outdoor unit 200 of FIG.
- an outdoor unit 200 includes a temperature sensor 21 for measuring an outside air temperature in addition to the outdoor heat exchanger 1, the four-way valve 4, the compressor 5, and the temperature sensor 6 illustrated in FIG. 1, And an outdoor fan 24.
- FIG. 6 is a functional block diagram showing a functional configuration of the air conditioner according to the embodiment of the present invention.
- the air conditioner includes a stepping motor 12 that is driven to adjust the opening degree of the expansion valve 2 in addition to the configurations shown in FIGS. 1, 3, and 5, and the air conditioner. It further includes a control unit 30 for performing overall control and an operation unit 36 for receiving instructions from the user.
- the opening degree of the expansion valve 2 is calculated as the number of phase excitation steps in the stepping motor 12.
- the expansion valve 2 is not limited to the one whose opening degree is adjusted by the stepping motor 12, and may be a temperature type expansion valve, for example. That is, the temperature sensing cylinder enclosing the refrigerant and the expansion valve are connected by the capillary tube.
- the inside of the expansion valve has a structure separated by a diaphragm. The opening degree of the expansion valve may be controlled by applying pressure to the diaphragm in accordance with the temperature of the temperature sensing cylinder.
- the control unit 30 is built in the indoor unit 100 and includes a processor 32 for performing various arithmetic processes and a memory 34 for storing various programs and data.
- the processor 32 is configured by, for example, a CPU (Central Processing Unit).
- the processor 32 controls the opening of the expansion valve 2 as will be described later by executing a program stored in the memory 34.
- the memory 34 may be a non-volatile memory such as a flash memory, for example.
- the operation unit 36 includes, for example, a power switch, a temperature adjustment key, an air volume adjustment key, a timer setting key, and the like.
- the air conditioner may further include an interface unit 38 for reading and writing data and programs from a computer-readable non-transitory recording medium 38a.
- the processor 32 stores the program read from the recording medium 38a by the interface unit 38 in the memory 34 (or updates an existing program), thereby controlling the opening of the expansion valve 2 as described later (opening calculation processing). May be performed.
- the recording medium 38a includes, for example, an optical medium such as a CD-ROM (Compact Disc-ROM), a magnetic recording medium such as a memory card, and the like.
- the opening degree of the expansion valve is often controlled by the degree of superheat converted from the outlet temperature of the evaporator.
- the evaporator temperature and the evaporator outlet temperature are detected, and control is performed so that the temperature difference becomes a target superheat degree.
- “Superheat degree” represents the temperature difference between the superheated steam temperature under a certain pressure and the dry saturated steam temperature.
- the expansion valve 2 is controlled based on the degree of superheat, but the target degree of superheat is estimated by the temperature difference (TMP_diff) between the discharge temperature (TMP_to) and the condenser temperature (TMP_con).
- TMP_diff temperature difference between the discharge temperature (TMP_to) and the condenser temperature (TMP_con).
- the superheat degree is often calculated from the evaporator temperature and the outlet temperature of the evaporator.
- the compression line on the Mollier diagram is determined by the compression pressure (corresponding to the rotational speed) of the compressor 5, the same control as the control using the difference between the evaporator temperature and the evaporator outlet temperature is performed. It is also possible to use a difference between the discharge temperature and the condenser temperature (hereinafter referred to as “discharge temperature difference”). This will be described in more detail with reference to FIG.
- FIG. 7 is a diagram showing an example of a Mollier diagram (Ph diagram).
- the relationship between pressure (kg / dm2) and enthalpy (kcal / kg) is represented.
- closed loops indicated by lines L1 to L4 represent heat pump cycles.
- the line L1 is ideally parallel to the isentropic line 74 and is called a compression line.
- Line L2 is called the condensation line
- line L3 is called the expansion line
- line L4 is called the evaporation line.
- the condensation line L2 and the evaporation line L4 are determined by the temperatures detected by the thermistor provided in the condenser and the thermistor provided in the evaporator, respectively.
- An isotherm 71 in the region on the left side (smaller enthalpy side) than the saturated liquid line 76 indicates an isotherm of the supercooled liquid, and is in a region surrounded by the saturated liquid line 76 and the saturated vapor line 77.
- the isotherm 72 shows the isotherm of wet steam.
- the isotherm 73 in the region on the right side (the side with the larger enthalpy) than the saturated steam line 77 indicates the isotherm of superheated steam.
- the saturated liquid line 76 and the saturated vapor line 77 are separated at a critical point 75.
- the compression line L1 is unique to the compressor 5, the compression line L1 is determined according to the operating state of the compressor 5. Pressure difference between the inlet and outlet of the expansion valve by the condenser thermistor detecting the condenser temperature (corresponding to the condensation pressure) and the evaporator thermistor detecting the evaporator temperature (corresponding to the evaporation pressure) I understand.
- the degree of superheat used for conventional control cannot be obtained unless the evaporator inlet temperature and the evaporator outlet temperature are known.
- the pressure difference between the inlet and outlet of the expansion valve when the expansion valve 2 is stable at a certain opening is determined by the compression pressure (rotation speed) of the compressor 5, conventionally, the evaporator temperature and the evaporator outlet
- the degree of superheat (corresponding to ⁇ h1) detected by the temperature depends on the thermistor for discharge temperature (corresponding to the temperature sensor 7 in the present embodiment) and the condenser thermistor (temperature sensor 6 or 8 in the present embodiment). It can be calculated from the degree of superheat (corresponding to ⁇ h2) obtained by
- the target discharge temperature difference (TMP_aim) that achieves the target superheat degree is calculated from the rotation speed (F) of the compressor 5 corresponding to the compression pressure of the compressor 5.
- the rotation speed of the compressor 5 may be determined based on a known algorithm. For example, it is determined based on the difference between the room temperature set by the operation unit 36 and the current room temperature (temperature sensor 11). That is, the greater the difference between the set temperature and the room temperature, the greater the rotational speed of the compressor 5.
- the degree of superheat can be calculated more reliably by detecting the temperatures at both the evaporator inlet and the evaporator outlet.
- safety control since the main purpose is control for removing from a dangerous state (hereinbelow, referred to as “safety control”) rather than accurate calculation of the superheat degree, the experiment is performed. Control is performed only by the temperature difference (discharge temperature difference) between the discharge temperature and the condenser temperature, using the pressure difference between the inlet and outlet of the expansion valve according to the determined opening of the expansion valve 2.
- the target discharge temperature difference is determined by calculation, but may be determined by using a data table stored in the memory 34 in advance. That is, thermistors (temperature sensors) are installed in advance at the evaporator and the evaporator outlet, and the discharge temperature and condenser temperature when the superheat determined from the detected values of these thermistors becomes the target superheat are measured. To do.
- the difference between the measured discharge temperature and the condenser temperature may be a target discharge temperature difference corresponding to the rotational speed of the compressor at the time of measurement.
- the initial opening degree of the expansion valve 2 is usually set to stabilize the cycle, and a certain amount of time (referred to as mask time) is opened due to the discharge temperature difference. No degree control is performed. It is common to shorten the time to stabilize the initial opening by giving different values depending on the cooling cycle, the heating cycle, the outside air temperature high temperature and the outside air temperature low temperature, etc. .
- the opening of the expansion valve 2 is controlled so that the opening is determined by the rotational speed of the compressor 5. Thereafter, based on the degree of superheat determined for each rotation speed of the compressor 5, the opening degree of the expansion valve 2 is PID controlled (proportional) so that the discharge temperature difference becomes the target discharge temperature difference for each rotation speed of the compressor 5.
- Control Proportional Control
- integral control Integral Control
- differential control Derivative Control
- P PID control is described as the control that brings the actual temperature difference closer to the target temperature difference.
- proportional control or integral control may be used, but it is desirable to reduce the overshoot as much as possible to bring it closer to the target temperature difference.
- the change in the discharge temperature appears very late due to the opening degree of the expansion valve 2. Therefore, the opening degree control may be performed by feedforward control that predicts a stable discharge temperature from the inclination of the temperature change at the time when the discharge temperature change due to the opening degree change of the expansion valve 2 appears.
- a control method may be used in which a mask time is provided after the degree change until the next opening degree change. As a result, a control method that prevents the discharge temperature from overshooting and quickly stabilizes the discharge temperature is desirable.
- the air conditioner in the present embodiment performs the following safety control.
- the air conditioner in the present embodiment performs control for avoiding the evaporator, that is, the indoor heat exchanger 3 from being in a condensed state. Do. If the condenser temperature is too far from the discharge temperature, the opening of the expansion valve 2 becomes too narrow, and the refrigerant flow rate is low (evaporation is easy). Therefore, the refrigerant dries quickly in the indoor heat exchanger 3 (many portions where the refrigerant becomes a gas phase in the indoor heat exchanger 3), and there are portions that are not heat exchanged in the indoor heat exchanger 3. It will be divided. For this reason, cold air and warm air cross each other, and the indoor heat exchanger 3 is likely to condense.
- the indoor heat exchanger 3 is controlled by controlling the opening of the expansion valve 2 to be larger than the opening in the normal control (hereinafter referred to as “basic opening”). Prevent condensation. Specifically, the control is performed so that the opening degree of the expansion valve 2 is opened by “Shigh” step from the basic opening degree in the normal control.
- FIG. 8 is a diagram showing the relationship between the target discharge temperature difference and each threshold value and the compressor rotational speed in the embodiment of the present invention.
- the vertical axis indicates the discharge temperature difference (discharge-condenser). Temperature difference), and the horizontal axis indicates the rotational speed of the compressor 5.
- threshold Hth is set to a temperature that is higher by a certain temperature from, for example, a target discharge temperature difference line (“TMP_aim” in FIG. 8) provided for each rotation speed of compressor 5. .
- TMP_aim target discharge temperature difference line
- a discharge temperature difference in a state where the heat exchanger (indoor heat exchanger 3) used as an evaporator during the cooling cycle is likely to condense is experimentally measured in advance, and the measured discharge temperature difference has a margin. Then, the temperature difference line with the threshold value Hth may be determined.
- the step number Shigh may be determined experimentally or may be calculated by multiplying the opening degree of the expansion valve 2 determined for each frequency (rotation speed) of the compressor 5 by 1 / X. However, even when the opening degree is changed, the temperature change is larger when the rotational speed of the compressor 5 is larger. Therefore, it is desirable that the rotational speed of the compressor 5 is larger and the correction step number Shigh is larger.
- the opening degree of the expansion valve 2 is controlled to be greatly reduced as compared with the normal control.
- the refrigerant easily returns to the compressor 5 in a liquid phase from the heat exchanger used as an evaporator (high wetness).
- liquid back to the compressor 5 is likely to occur.
- control is performed so as to increase the gas phase in the gas-liquid two-phase state after the refrigerant is depressurized by controlling the opening of the expansion valve 2 to be greatly reduced.
- control is performed in such a direction that the opening degree of the expansion valve 2 is reduced by the “Slow” step from the basic opening degree in the normal control.
- Threshold value Lth is set to a temperature that is lower by a certain temperature from, for example, a target discharge temperature difference line (“TMP_aim” in FIG. 8) provided for each rotation speed of compressor 5. .
- TMP_aim target discharge temperature difference line
- the temperature difference line of the threshold value Hth may be determined by experimentally measuring in advance the discharge temperature difference in a state where liquid back is likely to occur, and giving a margin to the measured discharge temperature difference.
- the step number Slow here may be determined experimentally, or may be calculated by multiplying the opening degree of the expansion valve 2 determined for each frequency (rotational speed) of the compressor 5 by 1 / Y. . However, since the temperature change is larger when the rotational speed of the compressor 5 is larger even when the opening degree is changed, it is desirable that the rotational speed of the compressor 5 is larger and the correction step number Slow is larger.
- FIG. 9 is a flowchart showing a target opening calculation process in the embodiment of the present invention. This flowchart shows a function for calculating the target opening degree of the expansion valve 2. The process of the flowchart in FIG. 9 is periodically executed until an end event such as an operation stop instruction occurs. The process shown in the flowchart of FIG. 9 is stored in advance in the memory 34 as a program, and the function of the target opening degree calculation process is realized by the processor 32 reading and executing this program.
- each temperature is detected from the temperature sensor 7 provided at the outlet of the compressor 5 and the temperature sensor 6 provided in the outdoor heat exchanger 1.
- the temperature is detected from the temperature sensor 7 provided at the outlet of the compressor 5 and the temperature sensor 8 provided in the indoor heat exchanger 3.
- the discharge temperature difference “TMP_diff” is calculated from each temperature updated in step S1. Specifically, the discharge temperature difference (TMP_diff) is calculated by subtracting the condenser temperature (TMP_con) from the discharge temperature (TMP_to).
- the opening (basic opening) of the expansion valve 2 during normal control is set to the opening execution value so that the temperature difference (TMP_diff) becomes the target temperature difference “TMP_aim”.
- the target temperature difference (TMP_aim) is set in advance so as to be the target superheat degree for each frequency of the compressor 5.
- the calculation formula for the basic opening during normal control may be determined based on the results of experiments performed in advance. Such a basic opening (number of steps) may also be obtained from a data table stored in the memory 34 without depending on the calculation formula.
- step S4 it is determined whether or not the discharge temperature difference (TMP_diff) is smaller than the set threshold value Hth (step S4).
- the discharge temperature difference (TMP_diff) is greater than or equal to the threshold value Hth (“FALSE” in step S4)
- the basic opening (the opening execution value S in step S3) in normal control is further reduced to “S_high”
- the added value is set as a new opening execution value S (step S5).
- the processor 32 drives the stepping motor 12 with the changed opening execution value.
- the opening degree of the expansion valve 2 is controlled so that the flow rate is increased as compared with the normal control.
- step S4 If the discharge temperature difference (TMP_diff) is smaller than the threshold Hth (“TRUE” in step S4), the process proceeds to step S6.
- step S6 it is determined whether the discharge temperature difference (TMP_diff) is larger than the set threshold value Lth.
- the discharge temperature difference (TMP_diff) is less than or equal to the threshold value Lth (“FALSE” in step S6)
- the basic opening in the normal control opening execution value S in step S3
- S_low Is set as a new opening execution value S (step S7).
- the processor 32 drives the stepping motor 12 with the changed opening execution value.
- the opening degree of the expansion valve 2 is controlled so that the flow rate is smaller than that during normal control.
- the discharge temperature thermistor (temperature sensor 7) that is normally installed in the air conditioner and the thermistor (temperature sensors 6 and 8) for the heat exchanger that becomes the condenser are used. Since the degree of superheat is estimated by using it, the opening degree of the expansion valve can be controlled without increasing the number of temperature sensors for calculating the degree of superheat. As a result, the manufacturing cost of the air conditioner can be suppressed.
Abstract
Description
好ましくは、冷房サイクル運転および暖房サイクル運転において冷媒の巡回方向を切替えるための切替弁と、室外の空気および冷媒の間で熱交換するための室外熱交換器と、室内の空気および冷媒の間で熱交換するための室内熱交換器とをさらに備え、冷房サイクル運転の場合、凝縮器は室外熱交換器に対応し、暖房サイクル運転の場合には、凝縮器は室内熱交換器に対応する。
はじめに、本実施の形態における空気調和機での冷媒回路の例について説明する。
(室内機について)
図2は、本発明の実施の形態における空気調和機の室内機100の外観図である。図3は、図2の室内機100の内部構成を概略的に示す断面図である。図3は、図2のY軸方向から見た室内機100の断面図を示す。
図4は、本発明の実施の形態における空気調和機の室外機200の外観図である。図5は、図4の室外機200の内部構成を概略的に示す図である。
図6は、本発明の実施の形態における空気調和機の機能構成を示す機能ブロック図である。
本実施の形態の制御部30(プロセッサ32)が実行する、膨張弁2の制御(開度の制御)について説明する。
圧縮機5の回転数は、公知のアルゴリズムに基づいて決定されるものであってよい。たとえば、操作部36にて設定された室内温度と、現在の室内温度(温度センサ11)との差に基づいて決定される。つまり、設定温度と室内温度との差が大きい程、圧縮機5の回転数は大きくなる。
本実施の形態における空気調和機は、以下のような安全制御を行なう。
特に冷房サイクル運転の場合、本実施の形態における空気調和機は、蒸発器、つまり室内熱交換器3が結露状態になるのを回避するための制御を行なう。吐出温度から凝縮器温度が大きく離れすぎると、膨張弁2の開度が絞りすぎとなり、冷媒流量が少ない(気化しやすい)状態となる。そのため、室内熱交換器3内で冷媒が早く乾いてしまい(室内熱交換器3で冷媒が気相となる部分が多い)、室内熱交換器3内部で熱交換される部分とされない部分とが分かれてしまう。そのため、冷たい空気と暖かい空気が交わり、室内熱交換器3が結露しやすい状態となる。
(2) 液バックを防止するための安全制御
本実施の形態における空気調和機は、さらに、冷房サイクル、暖房サイクルにかかわらず、圧縮機5に冷媒が液相のまま戻ってくるような状態(液バック)を回避するための制御を行なう。
<膨張弁2の目標開度算出処理>
次に、本実施の形態において、膨張弁2の開度を制御するためにプロセッサ32が実行する目標開度の算出処理について説明する。
Claims (8)
- 冷媒を圧縮するための圧縮機(5)と、
前記冷媒の流量を調整するための膨張弁(2)と、
前記圧縮機(5)の吐出温度を検出するための第1の温度センサ(7)と、
凝縮器(1または3)の温度を検出するための第2の温度センサ(6または8)と、
前記膨張弁(2)の開度を制御するための制御手段(30)とを備え、
前記制御手段(30)は、前記第1の温度センサ(7)により検出された前記吐出温度と前記第2の温度センサ(6または8)により検出された前記凝縮器(1または3)の温度との差を、吐出温度差として算出し、
前記制御手段(30)は、前記算出された吐出温度差と、目標過熱度となるように設定された目標の吐出温度差(TMP_aim)とに基づいて、通常制御における前記膨張弁(2)の開度を基本開度として設定する、空気調和機。 - 前記制御手段(30)は、前記算出された吐出温度差が予め定められた第1の閾値(Hth)以上の場合には、前記通常制御における前記基本開度よりも開く方向に前記膨張弁(2)の開度を制御する、請求の範囲第1項に記載の空気調和機。
- 前記制御手段(30)は、前記算出された吐出温度差が予め定められた第2の閾値(Lth)以下の場合には、前記通常制御における前記基本開度よりも絞る方向に前記膨張弁(2)の開度を制御し、
前記第2の閾値は前記第1の閾値より小さい、請求の範囲第2項に記載の空気調和機。 - 前記制御手段(30)は、前記算出された吐出温度差が予め定められた第2の閾値(Lth)以下の場合には、前記通常制御における前記基本開度よりも絞る方向に前記膨張弁(2)の開度を制御する、請求の範囲第1項に記載の空気調和機。
- 前記制御手段(30)は、前記目標の吐出温度差(TMP_aim)を、前記圧縮機(5)の回転数により算出する、請求の範囲第1~4項のいずれか1項に記載の空気調和機。
- 冷房サイクル運転および暖房サイクル運転において前記冷媒の巡回方向を切替えるための切替弁(4)と、
室外の空気および前記冷媒の間で熱交換するための室外熱交換器(1)と、
室内の空気および前記冷媒の間で熱交換するための室内熱交換器(3)とをさらに備え、
冷房サイクル運転の場合、前記凝縮器は前記室外熱交換器(1)に対応し、暖房サイクル運転の場合には、前記凝縮器は前記室内熱交換器(3)に対応する、請求の範囲第1~4項のいずれか1項に記載の空気調和機。 - 冷媒の流量を調整するための膨張弁(2)と、圧縮機(5)の吐出温度を検出するための第1の温度センサ(7)と、凝縮器(1または3)の温度を検出するための第2の温度センサ(6または8)とを備えた空気調和機において、前記膨張弁(2)の開度を制御するための方法であって、
前記第1の温度センサ(7)により検出された前記吐出温度と前記第2の温度センサ(6または8)により検出された前記凝縮器(1または3)の温度との差を、吐出温度差として算出するステップと、
前記算出された吐出温度差と、目標過熱度となるように設定された目標の吐出温度差(TMP_aim)とに基づいて、通常制御における前記膨張弁(2)の開度を基本開度として設定するステップとを含む、膨張弁の開度制御方法。 - 冷媒の流量を調整するための膨張弁(2)と、圧縮機(5)の吐出温度を検出するための第1の温度センサ(7)と、凝縮器(2)の温度を検出するための第2の温度センサ(6または8)とを備えた空気調和機において、前記空気調和機に備えられたコンピュータ(30)に、
前記第1の温度センサ(7)により検出された前記吐出温度と前記第2の温度センサ(6または8)により検出された前記凝縮器(2)の温度との差を、吐出温度差として算出するステップと、
前記算出された吐出温度差と、目標過熱度となるように設定された目標の吐出温度差とに基づいて、通常制御における前記膨張弁(2)の開度を基本開度として設定するステップとを実行させるための膨張弁の開度制御プログラムを記録したコンピュータ読み取り可能な記録媒体。
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US13/514,617 US20120260678A1 (en) | 2009-12-09 | 2010-12-02 | Air conditioner, method for controlling opening of expansion valve, and computer-readable recording medium with expansion valve opening control program recorded thereon |
EP10835883.9A EP2511626A4 (en) | 2009-12-09 | 2010-12-02 | AIR CONDITIONING SYSTEM, METHOD FOR CONTROLLING THE OPENING OF AN EXPANSION VALVE AND COMPUTER-READABLE STORAGE MEDIUM FOR STORING A PROGRAM FOR CONTROLLING THE OPENING OF AN EXPANSION VALVE |
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JP4854779B2 (ja) | 2012-01-18 |
CN102652245B (zh) | 2015-03-25 |
EP2511626A4 (en) | 2014-06-25 |
EP2511626A1 (en) | 2012-10-17 |
MY153453A (en) | 2015-02-13 |
CN102652245A (zh) | 2012-08-29 |
JP2011122756A (ja) | 2011-06-23 |
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