WO2017030068A1 - Refrigeration device - Google Patents
Refrigeration device Download PDFInfo
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- WO2017030068A1 WO2017030068A1 PCT/JP2016/073565 JP2016073565W WO2017030068A1 WO 2017030068 A1 WO2017030068 A1 WO 2017030068A1 JP 2016073565 W JP2016073565 W JP 2016073565W WO 2017030068 A1 WO2017030068 A1 WO 2017030068A1
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- WIPO (PCT)
- Prior art keywords
- heat exchanger
- temperature
- outdoor heat
- outdoor
- indoor
- Prior art date
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- 238000005057 refrigeration Methods 0.000 title claims abstract description 41
- 238000010257 thawing Methods 0.000 claims abstract description 39
- 230000007423 decrease Effects 0.000 claims abstract description 18
- 239000003507 refrigerant Substances 0.000 claims description 46
- 230000006835 compression Effects 0.000 claims description 6
- 238000007906 compression Methods 0.000 claims description 6
- 238000005070 sampling Methods 0.000 claims description 6
- 238000010438 heat treatment Methods 0.000 description 12
- 239000007788 liquid Substances 0.000 description 11
- 230000006870 function Effects 0.000 description 7
- 238000001816 cooling Methods 0.000 description 6
- 238000005259 measurement Methods 0.000 description 6
- 230000015572 biosynthetic process Effects 0.000 description 5
- 230000003247 decreasing effect Effects 0.000 description 5
- ATJFFYVFTNAWJD-UHFFFAOYSA-N Tin Chemical compound [Sn] ATJFFYVFTNAWJD-UHFFFAOYSA-N 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 238000012986 modification Methods 0.000 description 4
- 230000004048 modification Effects 0.000 description 4
- 238000002360 preparation method Methods 0.000 description 3
- 230000036962 time dependent Effects 0.000 description 3
- 238000007664 blowing Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000012546 transfer Methods 0.000 description 2
- 238000004891 communication Methods 0.000 description 1
- 238000012937 correction Methods 0.000 description 1
- 230000001502 supplementing effect Effects 0.000 description 1
Images
Classifications
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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
- F24F11/41—Defrosting; Preventing freezing
- F24F11/42—Defrosting; Preventing freezing of outdoor units
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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
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0043—Indoor units, e.g. fan coil units characterised by mounting arrangements
- F24F1/0057—Indoor units, e.g. fan coil units characterised by mounting arrangements mounted in or on a wall
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
- F24F1/0063—Indoor units, e.g. fan coil units characterised by heat exchangers by the mounting or arrangement of the heat exchangers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0071—Indoor units, e.g. fan coil units with means for purifying supplied air
- F24F1/0073—Indoor units, e.g. fan coil units with means for purifying supplied air characterised by the mounting or arrangement of filters
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
- F24F11/63—Electronic processing
- F24F11/64—Electronic processing using pre-stored data
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
- F24F11/63—Electronic processing
- F24F11/65—Electronic processing for selecting an operating mode
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/70—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
- F24F11/87—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling absorption or discharge of heat in outdoor units
- F24F11/871—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling absorption or discharge of heat in outdoor units by controlling outdoor fans
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/89—Arrangement or mounting of control or safety devices
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- 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
- F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
- F25B47/02—Defrosting cycles
- F25B47/022—Defrosting cycles hot gas defrosting
- F25B47/025—Defrosting cycles hot gas defrosting by reversing the cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
-
- 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
- F24F2110/10—Temperature
-
- 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
- F24F2110/10—Temperature
- F24F2110/12—Temperature of the outside air
-
- 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
- F25B2700/11—Sensor to detect if defrost is necessary
-
- 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
- F25B2700/2106—Temperatures of fresh outdoor air
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2116—Temperatures of a condenser
- F25B2700/21161—Temperatures of a condenser of the fluid heated by the condenser
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2117—Temperatures of an evaporator
- F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
Definitions
- the present invention relates to a refrigeration apparatus including a refrigeration circuit.
- a defrosting operation has been performed in order to remove frost attached to an outdoor heat exchanger.
- Patent Document 1 Japanese Patent Laid-Open No. 9-243210
- Patent Document 2 Japanese Patent Laid-Open No. 10-103818
- a defrost operation for removing frost on the outdoor heat exchanger is started.
- the indoor heat exchanger has entered a state where frost begins to be detected
- the indoor heat exchanger temperature is not more than a predetermined value in addition to the condition that the temperature of the outdoor heat exchanger is not more than a predetermined value as a condition for performing defrosting.
- the compressor operating frequency is lower than the specified value, or setting the outdoor heat exchanger temperature to enter the defrosting operation in consideration of the compressor operating frequency, the outside air temperature and the outside air humidity Has been done.
- the empty defrosting that enters the defrost operation when the outdoor heat exchanger is not frosted. Is not enough to prevent. Air defrosting is, in other words, wrong defrosting.
- the problem of the present invention is to prevent air defrosting that enters defrost operation when the outdoor heat exchanger is not frosted.
- a refrigeration apparatus includes a refrigeration circuit capable of repeating a vapor compression refrigeration cycle by flowing a refrigerant in the order of a compressor, an indoor heat exchanger, an expansion mechanism, and an outdoor heat exchanger, and an indoor heat
- a first sensor capable of detecting the temperature of the indoor heat exchanger of the exchanger and a second sensor capable of detecting the temperature of the outdoor heat exchanger of the outdoor heat exchanger; In addition to the first necessary condition that the state detected by one sensor continues for the first set time, the state in which a continuous decrease in the outdoor heat exchanger temperature is detected by the second sensor continues for the second set time. 2 It is configured to enter a defrost operation for defrosting the outdoor heat exchanger when the necessary conditions are satisfied.
- the state in which the continuous decrease in the indoor heat exchanger temperature is detected by the first sensor is not only the first necessary condition for continuing the first set time, but the continuation of the outdoor heat exchanger temperature by the second sensor. Since the second necessary condition in which the state where the lowering is detected is continued for the second set time is set as the condition for entering the defrost operation, the indoor heat exchanger is not used for reasons other than frost formation on the outdoor heat exchanger. The case where the temperature of the outdoor heat exchanger rises because the temperature is decreasing but the outdoor heat exchanger is not frosted can be excluded from the case of entering the defrost operation.
- the situation in which the average value of the outdoor heat exchanger temperature detected by the second sensor within the predetermined sampling time does not increase continues for a predetermined number of times. In this case, it is determined that the second necessary condition is satisfied.
- a refrigeration apparatus is the refrigeration apparatus according to the first aspect, further comprising a third sensor capable of detecting an outside air temperature at a location where the outdoor heat exchanger is installed, and is detected by the second sensor. It is used as the third necessary condition that the outdoor heat exchanger temperature thus made is lower than the defrost entry temperature set according to the outdoor temperature detected by the third sensor and the operating frequency of the compressor, and the first necessary condition and The defrost operation is started when the second necessary condition and the third necessary condition are satisfied at the same time.
- the outdoor heat exchanger temperature is lower than the defrost entry temperature set in accordance with the outside air temperature and the operating frequency of the compressor, it is used as a third necessary condition, and therefore, an environment in which frost formation occurs It is possible to determine whether or not to enter the defrost operation in consideration.
- the third requirement is that the period during which the outdoor heat exchanger temperature is lower than the defrost entry temperature continues for a third set time. Is what is.
- the defrost operation is not entered even if the first and second necessary conditions are satisfied.
- the operation state of the compressor can be reflected in the determination of whether or not to enter the defrost operation.
- the effect of preventing air defrosting is enhanced.
- the perspective view which shows the external appearance of the air conditioner which concerns on embodiment.
- the timing chart which shows the outline
- the graph which shows an example of the time-dependent change of outdoor heat exchanger temperature.
- operation The flowchart for demonstrating an example of the determination method which rushes into defrost driving
- the graph which shows an example of the relationship of a time-dependent change of the temperature difference of indoor heat exchanger temperature and room temperature, and defrost entry determination.
- the graph which shows the other example of the relationship between the time-dependent change of the temperature difference of indoor heat exchanger temperature and room temperature, and defrost entry determination.
- FIG. 1 An air conditioner 1 shown in FIG. 1 includes an indoor unit 2 attached to an indoor wall surface WL and the like, and an outdoor unit 3 installed outdoors.
- FIG. 2 is a circuit diagram of the air conditioner 1.
- the air conditioner 1 includes a refrigeration circuit 10 and can perform a vapor compression refrigeration cycle by circulating a refrigerant in the refrigeration circuit 10.
- the indoor unit 2 and the outdoor unit 3 are connected by a communication pipe 4.
- Refrigeration circuit 10 The refrigeration circuit 10 includes a compressor 11, a four-way switching valve 12, an outdoor heat exchanger 13, an expansion mechanism 14, an accumulator 15, and an indoor heat exchanger 16.
- the compressor 11 that sucks and compresses the refrigerant sucked from the suction port sends out the refrigerant discharged from the discharge port to the first port of the four-way switching valve 12.
- the four-way switching valve 12 causes the refrigerant to flow between the first port and the fourth port and at the same time the second port and the third port, as indicated by broken lines. Allow refrigerant to flow between ports. Further, when the air conditioner 1 performs the cooling operation and the reverse cycle defrost operation, the four-way switching valve 12 circulates the refrigerant between the first port and the second port, as indicated by the solid line. At the same time, the refrigerant is circulated between the third port and the fourth port.
- the outdoor heat exchanger 13 has a gas side inlet / outlet for mainly allowing the gas refrigerant to flow between the second port of the four-way switching valve 12 and allows the liquid refrigerant to mainly flow between the expansion mechanism 14. For the liquid side.
- the outdoor heat exchanger 13 exchanges heat between the refrigerant flowing through a heat transfer tube (not shown) connected between the liquid side inlet and outlet and the gas side inlet and outlet of the outdoor heat exchanger 13 and the outdoor air.
- the expansion mechanism 14 is disposed between the outdoor heat exchanger 13 and the indoor heat exchanger 16.
- the expansion mechanism 14 has a function of expanding and depressurizing the refrigerant flowing between the outdoor heat exchanger 13 and the indoor heat exchanger 16.
- the indoor heat exchanger 16 has a liquid side inlet / outlet for mainly circulating the liquid refrigerant to and from the expansion mechanism 14, and mainly distributes the gas refrigerant to and from the fourth port of the four-way switching valve 12. It has a gas side entrance and exit.
- the indoor heat exchanger 16 exchanges heat between the refrigerant flowing through the heat transfer pipe 16a (see FIG. 3) connected between the liquid side inlet and outlet and the gas side inlet and outlet of the indoor heat exchanger 16 and the room air. .
- An accumulator 15 is disposed between the third port of the four-way switching valve 12 and the suction port of the compressor 11.
- the refrigerant flowing from the third port of the four-way switching valve 12 to the compressor 11 is separated into gas refrigerant and liquid refrigerant.
- a gas refrigerant is mainly supplied from the accumulator 15 to the suction port of the compressor 11.
- the outdoor unit 3 includes an outdoor fan 21 for generating an air flow of outdoor air that passes through the outdoor heat exchanger 13.
- the outdoor unit 3 includes an outdoor temperature sensor 22 for measuring the temperature of the outdoor air, and an outdoor heat exchanger temperature sensor 23 for measuring the temperature of the outdoor heat exchanger 13.
- the outdoor unit 3 includes an outdoor control device 24 that controls the compressor 11, the four-way switching valve 12, the expansion mechanism 14, and the outdoor fan 21.
- the outdoor control device 24 includes, for example, a CPU (not shown) and a memory (not shown), and can control the outdoor unit 3 according to a stored program or the like.
- the outdoor control device 24 is connected to the outdoor temperature sensor 22 and the outdoor heat exchanger temperature sensor 23 in order to receive signals related to the temperatures measured by the outdoor temperature sensor 22 and the outdoor heat exchanger temperature sensor 23. .
- the indoor unit 2 includes an indoor fan 31 for generating a flow of indoor air that passes through the indoor heat exchanger 16.
- the indoor unit 2 includes an indoor temperature sensor 32 for measuring the temperature of indoor air and an indoor heat exchanger temperature sensor 33 for measuring the temperature of the indoor heat exchanger 16.
- the indoor unit 2 includes an indoor control device 34 that controls the indoor fan 31.
- the indoor side control device 34 includes, for example, a CPU (not shown) and a memory (not shown), and is configured to be able to control the outdoor unit 3 according to a stored program or the like.
- the indoor side control device 34 is connected to the indoor temperature sensor 32 and the indoor heat exchanger temperature sensor 33 in order to receive a signal related to the temperature measured by the indoor temperature sensor 32 and the indoor heat exchanger temperature sensor 33. .
- outdoor side control device 24 and the indoor side control device 34 are connected to each other by a signal line so that signals can be transmitted and received with each other.
- FIG. 3 shows a cross section of the indoor unit cut along the line II in FIG.
- the indoor unit 2 includes a casing 41, an indoor heat exchanger 16, an indoor fan 31, an air filter 42, a horizontal flap 43, and a vertical flap 49.
- An upper surface suction port 44 is provided on the upper surface of the casing 41.
- the indoor air in the vicinity of the upper surface suction port 44 is taken into the casing 41 from the upper surface suction port 44 by the drive of the indoor fan 31 and sent to the indoor heat exchanger 16 having a reverse V-shaped cross section.
- a broken-line arrow A in FIG. 3 represents the flow of indoor air sent from the upper surface inlet 44 to the indoor fan 31 via the indoor heat exchanger 16.
- a lower surface suction port 45 and an air outlet 46 are formed on the lower surface of the casing 41.
- the lower surface suction port 45 is provided on the wall side with respect to the air outlet 46, and is connected to the inside of the casing 41 by the suction channel 47. From the lower surface suction port 45, room air in the vicinity of the lower surface suction port 45 is taken into the casing 41 by driving the indoor fan 31, and is sent to the indoor heat exchanger 16 through the suction channel 47.
- a broken-line arrow B in FIG. 3 represents the flow of indoor air sent from the lower surface suction port 45 to the indoor heat exchanger 16.
- the air outlet 46 is provided on the front side of the indoor unit 2 with respect to the lower surface inlet 45, and is connected to the inside of the casing 41 by the air outlet channel 48.
- the room air sucked from the upper surface suction port 44 and the lower surface suction port 45 is subjected to heat exchange in the indoor heat exchanger 16 and then blown out from the blower outlet 46 into the room through the blowout channel 48.
- a broken-line arrow C in FIG. 3 represents the flow of air sent from the blowout channel 48 to the room through the blowout port 46.
- two horizontal flaps 43 are attached to the casing 41 so as to be rotatable.
- the horizontal flap 43 is rotated by a flap driving motor (not shown), and opens and closes the air outlet 46 according to the operating state of the indoor unit 2.
- the horizontal flap 43 has a function of changing the blowing direction of the room air up and down so that the room air blown out from the blow-out port 46 is guided in the direction desired by the user.
- a vertical flap 49 is attached to the casing 41 so as to be rotatable in the vicinity of the air outlet 46.
- the vertical flap 49 has a function of rotating by a flap driving motor (not shown) and changing the blowing direction of room air to the left and right.
- the low-temperature and high-pressure refrigerant deprived of the temperature by the indoor heat exchanger 16 is decompressed by the expansion mechanism 14 to be changed to a low-temperature and low-pressure refrigerant.
- the refrigerant that has flowed into the outdoor heat exchanger 13 via the expansion mechanism 14 is warmed by heat exchange with the outdoor air, evaporates, and changes from liquid refrigerant to gas refrigerant.
- the outdoor heat exchanger 13 functions as an evaporator.
- refrigerant composed mainly of low-temperature gas refrigerant is sucked into the compressor 11 from the outdoor heat exchanger 13 through the four-way switching valve 12 and the accumulator 15.
- the refrigerant is flowed in the order of the compressor 11, the indoor heat exchanger 16, the expansion mechanism 14, and the outdoor heat exchanger 13, and such a vapor compression refrigeration cycle is repeated.
- the low-temperature and high-pressure refrigerant whose temperature has been deprived by the outdoor heat exchanger 13 is reduced in pressure by the expansion mechanism 14 and changed to a low-temperature and low-pressure refrigerant.
- the refrigerant that has flowed into the indoor heat exchanger 16 through the expansion mechanism 14 cools the indoor air by heat exchange with the indoor air, is warmed, and evaporates to change from a liquid refrigerant to a gas refrigerant.
- the indoor heat exchanger 16 functions as an evaporator.
- the refrigerant mainly composed of low-temperature gas refrigerant is sucked into the compressor 11 from the indoor heat exchanger 16 through the four-way switching valve 12 and the accumulator 15.
- the reverse cycle defrost operation is performed to remove frost attached to the outdoor heat exchanger 13 due to the heating operation. Accordingly, the operation is switched to the reverse cycle defrost operation in the middle of the heating operation, and when the reverse cycle defrost operation is completed, the operation returns to the heating operation again.
- the reverse cycle defrost operation as in the cooling operation, the four-way switching valve 12 is switched to the solid line state shown in FIG. In the reverse cycle defrost operation, the same vapor compression refrigeration cycle as in the cooling operation is repeated.
- the reverse cycle defrost operation is performed in the reverse cycle of the heating operation, and the vapor compression is performed by flowing the refrigerant in the order of the compressor 11, the outdoor heat exchanger 13, the expansion mechanism 14, and the indoor heat exchanger 16. It is the reverse cycle which repeats a formula refrigeration cycle.
- the outdoor unit 3 determines that the outdoor side control device 24 performs defrosting when the heating control is being performed.
- the defrost entry determination will be described later.
- the defrost request signal SG ⁇ b> 1 is transmitted from the outdoor side control device 24 of the outdoor unit 3 to the indoor side control device 34 of the indoor unit 2.
- the indoor side control device 34 receives the defrost request signal SG1
- the indoor unit 2 starts preparation for the defrost operation. For example, in the case where an electric heater (not shown) for supplementing the indoor air is built in, the indoor control device 34 keeps the indoor fan 31 on for a while after the electric heater is turned off. When the is cooled, the preparation for the defrosting operation is completed.
- the indoor side control device 34 transmits a defrost permission signal SG2 to the outdoor side control device 24.
- the outdoor side control apparatus 24 will start defrost control, if the defrost permission signal SG2 is received, and will transmit the signal SG3 which shows being defrosting to the indoor side control apparatus 34.
- the normal notification signal SG4 that notifies the outdoor side control device 24 to return to the normal heating operation to the indoor side control device 34 of the indoor unit 2 Is sent.
- the indoor unit 2 that has received the normal notification signal SG4 returns to the heating control for the heating operation.
- the outdoor side controller 24 monitors the outdoor heat exchanger temperature using the outdoor heat exchanger temperature sensor 23.
- the outdoor control device 24 detects that the outdoor heat exchanger temperature has reached Ta ° C. due to the increase in the outdoor heat exchanger temperature after 90 seconds, the outdoor control device 24 terminates the reverse cycle defrost operation. decide.
- the defrosting time required from the start of defrosting to the end of defrosting varies depending on the outside air temperature and the operating state of the air conditioner 1. In other words, the defrosting time may be longer or shorter.
- the outdoor side control device 24 stores the threshold value tr, and determines whether the defrost time is longer or shorter than tr each time the reverse cycle defrost operation is performed.
- the indoor side control device 34 of the indoor unit 2 measures the indoor heat exchanger temperature Tei of the indoor heat exchanger 16 using the indoor heat exchanger temperature sensor 33 (step ST1), and controls the outdoor side of the outdoor unit 3
- the apparatus 24 measures the outdoor heat exchanger temperature Teo of the outdoor heat exchanger 13 using the outdoor heat exchanger temperature sensor 23 (step ST2).
- FIG. 6 it is described that the measurement of the indoor heat exchanger temperature Tei is measured before the outdoor heat exchanger temperature Teo, but either of these measurements is performed first. Or may be performed simultaneously.
- step ST3 it is determined whether or not the indoor heat exchanger temperature Tei is continuously decreased for the first set time (step ST3), and the outdoor heat exchanger temperature Teo is continuously decreased for the second set time. It is determined whether or not (step ST4).
- the former is the determination of the first necessary condition
- the latter is the determination of the second necessary condition.
- the outdoor heat exchanger temperature Teo and the indoor heat exchanger temperature Tei are collected in one of the indoor side control device 34 and the outdoor side control device 24, and the outdoor heat exchanger temperature Teo and the indoor heat exchanger temperature are collected. It may be determined whether or not both the first necessary condition and the second necessary condition are satisfied by the control device having both data about Tei.
- the measurement of the indoor heat exchanger temperature Tei and the outdoor heat exchanger temperature Teo is repeated until the above first and second necessary conditions are satisfied. If the above-mentioned first necessary condition and second necessary condition are satisfied, the air conditioner 1 determines to enter the defrost operation by the indoor side control device 34 or the outdoor side control device 24 (step ST5).
- step ST4 the outdoor side control device 24 performs sampling n times at a fixed time using a built-in sampling timer, and calculates the average value ( ⁇ Teo / n) of the outdoor heat exchanger temperature Teo.
- n is a predetermined natural number.
- the indoor side control device 34 that has obtained information from the outside control device 24 or the outdoor side control device 24 determines that the outdoor heat exchanger temperature Teo continuously decreases for the second set time (step ST12).
- step ST21 for calculating the defrost entry temperature from the outdoor heat exchanger temperature and the defrost entry temperature are used.
- step ST22 for determining whether or not to enter the defrost operation is provided.
- the outdoor side controller 24 measures the outdoor temperature Tout using the outdoor temperature sensor 22. Then, the outdoor side control device 24 determines whether the outside air temperature Tout is lower than the defrosting determination outside air temperature Tdd or higher than the defrosting determination outside air temperature Tdd. Further, as described in (3-1) above, the outdoor side control device 24 determines whether the previous defrost time tdf is longer or shorter than the threshold value tr. Depending on these situations, the defrost entry temperature Tp is calculated using one of the following four formulas (1) to (4).
- f is the operating frequency of the compressor 11, and ⁇ , ⁇ 1, ⁇ 0, ⁇ 1, ⁇ 0, and ⁇ are positive constants.
- Tp is set within a predetermined range.
- the constants in the equations (1) to (4) are determined from the measurement results for the outdoor air temperature Tout and the operation frequency f for the outdoor heat exchanger temperature (defrost entry temperature Tp) to be entered into the defrost operation. .
- Tp ⁇ ⁇ f + ⁇ 1 ⁇ Tout ⁇ 1 (1)
- Tp ⁇ ⁇ f + ⁇ 0 ⁇ Tout ⁇ 0 (2)
- Tp ⁇ ⁇ f + ⁇ 1 ⁇ Tout ⁇ 1 + ⁇ (3)
- Tp ⁇ ⁇ f + ⁇ 0 ⁇ Tout ⁇ 0 + ⁇ (4)
- the indoor control device 34 calculates an average value of the temperature difference ⁇ Tei sampled for a certain period of time. And the indoor side control apparatus 34 judges that the 1st necessary condition was satisfied when the average value of temperature difference (DELTA) Tei fell continuously k times. By making such a determination, it is possible to determine a continuous decrease in the indoor heat exchanger temperature Tei while considering the influence of the indoor temperature Tin.
- DELTA temperature difference
- the first condition for defrosting may be satisfied at point Q shown in FIG. Therefore, in the modified example C, as the first necessary condition is satisfied, the average value Av ⁇ Tei of the temperature difference ⁇ Tei continuously decreases k times, or the average value Av ⁇ Tei of the temperature difference ⁇ Tei is the first set time Ts1. It is not going to rise. In this case, even if the former condition is not satisfied, as shown in FIG. 10, the average value Av ⁇ Tei of the temperature difference ⁇ Tei does not increase and remains the same between time t31 and time t32. Or has fallen. As described above, the first necessary condition for defrosting is satisfied at a relatively early timing as compared with FIG. 9.
- the first necessary condition for entering the defrost operation is that the indoor heat exchanger 16 has the indoor heat exchanger 16 by the indoor heat exchanger temperature sensor 33.
- the state where the continuous decrease in the temperature Tei is detected is that the first set time continues.
- the second necessary condition is that the state in which the outdoor heat exchanger temperature Teo of the outdoor heat exchanger 13 is continuously detected by the outdoor heat exchanger temperature sensor 23 is continued for the second set time.
- the temperature sensor 33 for indoor heat exchangers is a 1st sensor
- the temperature sensor 23 for outdoor heat exchangers is a 2nd sensor.
- the average value of the outdoor heat exchanger temperature Teo of the outdoor heat exchanger 13 within a predetermined sampling time in other words, the average value of the outdoor heat exchanger temperature sampled a predetermined number n ( ⁇ Teo / n). Is used. As a result, it is possible to suppress an error in the determination that the second necessary condition is satisfied by the measurement noise of the outdoor heat exchanger temperature Teo, and to stably prevent the air defrosting from being performed.
- the outdoor heat exchanger temperature Teo of the outdoor heat exchanger 13 is lower than the defrost entry temperature Tp set according to the outdoor air temperature Tout and the operating frequency f of the compressor 11. 3 Used as a necessary condition. By using such a third necessary condition, it is possible to determine whether or not to enter the defrost operation in consideration of the environment in which frost formation occurs, so that it is easy to prevent the air defrosting from being performed.
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Abstract
Description
以下、本発明の一実施形態に係る冷凍装置として空気調和機を例に挙げて説明する。まず、本発明の一実施形態に係る空気調和機の構成の概要について図1及び図2を用いて説明する。図1に示す空気調和機1は、室内の壁面WLなどに取り付けられる室内機2と、屋外に設置される室外機3とを備えている。図2は、空気調和機1の回路図である。この空気調和機1は、冷凍回路10を備えており、冷凍回路10の中の冷媒を循環させることにより蒸気圧縮式冷凍サイクルを実行することができる。この冷凍回路10に冷媒を循環させるために、連絡配管4によって、室内機2と室外機3が接続されている。 (1) Outline of Configuration of Air Conditioner Hereinafter, an air conditioner will be described as an example of a refrigeration apparatus according to an embodiment of the present invention. First, the outline | summary of a structure of the air conditioner which concerns on one Embodiment of this invention is demonstrated using FIG.1 and FIG.2. An
冷凍回路10は、圧縮機11と、四路切換弁12と、室外熱交換器13と、膨張機構14と、アキュムレータ15と、室内熱交換器16とを備えている。吸入口から冷媒を吸入して圧縮した冷媒を吐出口から吐出する圧縮機11は、吐出口から吐出した冷媒を四路切換弁12の第1ポートに対して送出する。 (1-1)
The
室外機3は、室外熱交換器13を通過する室外空気の気流を発生させるための室外ファン21を備えている。また、室外機3は、室外空気の温度を測定するための室外温度センサ22と、室外熱交換器13の温度を測定するための室外熱交換器用温度センサ23とを備えている。さらに、室外機3は、圧縮機11、四路切換弁12、膨張機構14及び室外ファン21を制御する室外側制御装置24を備えている。この室外側制御装置24は、例えばCPU(図示せず)とメモリー(図示せず)を含んでおり、記憶されているプログラムなどに従って室外機3の制御を行うことができる構成になっている。そして、室外側制御装置24は、室外温度センサ22及び室外熱交換器用温度センサ23が測定した温度に関する信号を受信するために、室外温度センサ22及び室外熱交換器用温度センサ23に接続されている。 (1-2) Configuration Other than Refrigerating
図3には、図1のI-I線に沿って切断した室内機の断面が示されている。室内機2は、ケーシング41と、室内熱交換器16と、室内ファン31と、エアフィルタ42と、水平フラップ43と、垂直フラップ49とを備えている。 (1-3) Detailed Configuration of
(2-1)暖房運転
空気調和機1の暖房運転のときは、四路切換弁12は、図2に示された破線の状態に切り換わる。すなわち、圧縮機11から吐出された高温高圧のガス冷媒は、四路切換弁12を介して室内熱交換器16に流れ込む。このとき、室内熱交換器16は、凝縮器として機能する。そのため、室内熱交換器16の中を流れるに従って、冷媒は、室内空気との熱交換によって室内空気を暖めて自身が冷やされ、凝縮してガス冷媒から液冷媒に変化する。室内熱交換器16で温度を奪われた低温高圧の冷媒は、膨張機構14によって減圧されて低温低圧の冷媒に変化する。膨張機構14を経て室外熱交換器13に流れ込んだ冷媒は、室外空気との熱交換によって暖められ、蒸発して液冷媒からガス冷媒に変化する。このとき、室外熱交換器13は、蒸発器として機能している。そして、室外熱交換器13から四路切換弁12及びアキュムレータ15を介して、主に低温のガス冷媒からなる冷媒が圧縮機11に吸入される。圧縮機11、室内熱交換器16、膨張機構14及び室外熱交換器13の順に冷媒を流して、このような蒸気圧縮式冷凍サイクルを繰り返すのが正サイクルである。 (2) Overview of heating operation, cooling operation and reverse cycle defrost operation (2-1) Heating operation During the heating operation of the
空気調和機1の冷房運転のときは、四路切換弁12は、図2に示された実線の状態に切り換わる。すなわち、圧縮機11から吐出された高温高圧のガス冷媒は、四路切換弁12を介して室外熱交換器13に流れ込む。このとき、室外熱交換器13は、凝縮器として機能する。そのため、室外熱交換器13の中を流れるに従って、冷媒は、室外空気との熱交換によって冷やされ、凝縮してガス冷媒から液冷媒に変化する。室外熱交換器13で温度を奪われた低温高圧の冷媒は、膨張機構14によって減圧されて低温低圧の冷媒に変化する。膨張機構14を経て室内熱交換器16に流れ込んだ冷媒は、室内空気との熱交換によって室内空気を冷やして自身が暖められ、蒸発して液冷媒からガス冷媒に変化する。このとき、室内熱交換器16は、蒸発器として機能している。そして、室内熱交換器16から四路切換弁12及びアキュムレータ15を介して、主に低温のガス冷媒からなる冷媒が圧縮機11に吸入される。 (2-2) Cooling Operation When the
逆サイクルデフロスト運転は、暖房運転が行なわれたことで室外熱交換器13に付着した霜を取るために行われる。従って、暖房運転の途中で逆サイクルデフロスト運転に切り換わり、逆サイクルデフロスト運転が終了すると再び暖房運転に復帰する。逆サイクルデフロスト運転では、冷房運転と同じように、四路切換弁12が、図2に示された実線の状態に切り換わる。そして、逆サイクルデフロスト運転でも、冷房運転と同様の蒸気圧縮式冷凍サイクルが繰り返される。つまり、暖房運転時の正サイクルとは逆に、逆サイクルデフロスト運転で行なわれるのは、圧縮機11、室外熱交換器13、膨張機構14及び室内熱交換器16の順に冷媒を流して蒸気圧縮式冷凍サイクルを繰り返す逆サイクルである。 (2-3) Reverse cycle defrost operation The reverse cycle defrost operation is performed to remove frost attached to the
(3-1)逆サイクルデフロスト運転の終了
逆サイクルデフロスト運転及びその前後の室外熱交換器温度が図5に示されている。なお、図5の時間軸に示されている値は説明をわかり易くするための一例であり、これらの値は外気温度や空気調和機1の運転状態によって変化する。除霜が開始されると、開始から30秒が経過するまでは徐々に室外熱交換器13の温度が上昇する。開始から30秒が経過して室外熱交換器13の温度が0℃に達した後の霜が融解している期間は、室外熱交換器13の温度が0℃を維持する。室外熱交換器13に付着している霜が融けてなくなると、室外熱交換器13の温度が上昇を始める。図5では、90秒が経過した時点で霜が融け終わるので、90秒が経過した後に温度上昇が見られる。室外側制御装置24は、室外熱交換器用温度センサ23を使って室外熱交換器温度を監視している。そして、90秒以降の室外熱交換器温度の上昇によって、室外熱交換器温度がTa℃に達したことを室外側制御装置24が検知すると、室外側制御装置24が逆サイクルデフロスト運転の終了を決定する。 (3) Defrosting entry determination (3-1) End of reverse cycle defrost operation The reverse cycle defrost operation and the outdoor heat exchanger temperatures before and after the reverse cycle defrost operation are shown in FIG. Note that the values shown on the time axis in FIG. 5 are examples for easy understanding of the description, and these values vary depending on the outside air temperature and the operating state of the
(3-2-1)突入判定の概要
逆サイクルデフロスト運転への突入判定の概要について、図6を用いて説明する。まず、室内機2の室内側制御装置34が室内熱交換器用温度センサ33を用いて室内熱交換器16の室内熱交換器温度Teiを測定するとともに(ステップST1)、室外機3の室外側制御装置24が室外熱交換器用温度センサ23を用いて室外熱交換器13の室外熱交換器温度Teoを測定する(ステップST2)。なお、図6では、室内熱交換器温度Teiの測定の方が室外熱交換器温度Teoよりも先に測定しているように記載されているが、これらの測定はどちらが先に行われてもよく、また同時に行われてもよい。 (3-2) Entry Determination for Reverse Cycle Defrost Operation (3-2-1) Outline of Entry Determination An overview of entry determination for reverse cycle defrost operation will be described with reference to FIG. First, the indoor
次に、図7を用いて。室外熱交換器温度の継続的な低下の判断の具体的な例について説明する。図7に示されているフローチャートが図6に示されているフローチャートと異なる点は、室外熱交換器温度Teoが第2設定時間だけ継続的に低下しているか否かを判断するステップ(ステップST4)が、ステップST11とステップST12で実現されている。ステップST11では、室外側制御装置24が、内蔵しているサンプリングタイマを用いて、一定時間にn回サンプリングをして室外熱交換器温度Teoの平均値(ΣTeo/n)を算出する。ここでnは、予め定められた自然数である。このような室外熱交換器温度Teoの平均値を予め定められたm+1個算出した結果、一つ後の平均値がその前の平均値と同じかそれ以下である状況がm回続けば、室外側制御装置24又は室外側制御装置24から情報を得た室内側制御装置34は、室外熱交換器温度Teoが第2設定時間だけ継続的に低下していると判断する(ステップST12)。 (3-2-2) Determination of continuous decrease in outdoor heat exchanger temperature Next, referring to FIG. A specific example of determining the continuous decrease in the outdoor heat exchanger temperature will be described. The flowchart shown in FIG. 7 is different from the flowchart shown in FIG. 6 in that it is determined whether or not the outdoor heat exchanger temperature Teo continuously decreases for the second set time (step ST4). ) Is realized in step ST11 and step ST12. In step ST11, the outdoor
(4-1)変形例A
上記実施形態では、デフロスト運転への突入を判断する際に、第1必要条件と第2必要条件の2つが満たされていることが条件とされたが、デフロスト運転への突入を判断するためにさらに他の必要条件が付加されてもよい。 (4) Modification (4-1) Modification A
In the above embodiment, when the entry to the defrost operation is determined, the first requirement condition and the second requirement condition are satisfied, but in order to determine the entry to the defrost operation. Still other requirements may be added.
Tout≧Tddでかつtdf<trのとき、Tp=-β×f+ε0×Tout-α0 …(2)
Tout<Tddでかつtdf≧trのとき、Tp=-β×f+ε1×Tout-α1+ν …(3)
Tout≧Tddでかつtdf≧trのとき、Tp=-β×f+ε0×Tout-α0+ν …(4)
上述の式(1)~(4)を適宜用いて算出された除霜突入温度Tpと、室外熱交換器用温度センサ23によって検知される室外熱交換器温度Teoとを比較して、Teo≦Tpの状態が第3設定時間継続すれば、室外側制御装置24は、逆サイクルデフロスト運転への突入を決定する(ステップST22)。 When Tout <Tdd and tdf <tr, Tp = −β × f + ε1 × Tout−α1 (1)
When Tout ≧ Tdd and tdf <tr, Tp = −β × f + ε0 × Tout−α0 (2)
When Tout <Tdd and tdf ≧ tr, Tp = −β × f + ε1 × Tout−α1 + ν (3)
When Tout ≧ Tdd and tdf ≧ tr, Tp = −β × f + ε0 × Tout−α0 + ν (4)
By comparing the defrost entry temperature Tp calculated using the above-described equations (1) to (4) as appropriate with the outdoor heat exchanger temperature Teo detected by the outdoor heat
上記実施形態では、デフロスト運転への突入を判断する際に、第1必要条件として、室内熱交換器温度Teiが第1設定時間だけ継続的に低下している場合を例に挙げて説明した。しかし、室内熱交換器温度Teiの継続的な低下を判断する際に、室内熱交換器温度Teiが室内温度Tinの影響を受けることから、室内温度Tinを用いて修正を加えてもよい。つまり、室内熱交換器温度Teiが第1設定時間だけ継続的に低下しているという態様には、例えば、室内熱交換器温度Teiと室内温度Tinの差(=Tei-Tin)で定義される温度差ΔTeiが第1設定時間だけ継続的に低下しているという態様が含まれるということである。 (4-2) Modification B
In the above-described embodiment, the case where the indoor heat exchanger temperature Tei continuously decreases for the first set time has been described as an example of the first necessary condition when determining the entry into the defrost operation. However, when determining the continuous decrease in the indoor heat exchanger temperature Tei, the indoor heat exchanger temperature Tei is affected by the indoor temperature Tin, so that the indoor temperature Tin may be used for correction. That is, the aspect in which the indoor heat exchanger temperature Tei continuously decreases for the first set time is defined by, for example, the difference between the indoor heat exchanger temperature Tei and the indoor temperature Tin (= Tei−Tin). That is, a mode in which the temperature difference ΔTei continuously decreases for the first set time is included.
上記変形例Bでは、温度差ΔTeiの平均値AvΔTeiが連続してk回低下することが、第1必要条件である場合について説明した。しかし、このような判定では、例えばk=5の場合について考えると、図9に示されているように、時刻t21から5回連続して温度差ΔTeiの平均値AvΔTeiが低下した時刻t22の時点で除霜突入のための第1必要条件が満たされる。 (4-3) Modification C
In the modified example B, the case where the first necessary condition is that the average value AvΔTei of the temperature difference ΔTei continuously decreases k times has been described. However, in such a determination, for example, in the case of k = 5, as shown in FIG. 9, as shown in FIG. 9, at the time t22 when the average value AvΔTei of the temperature difference ΔTei has decreased five times continuously from the time t21. The first requirement for defrosting is satisfied.
(5-1)
以上説明したように、実施形態に係る冷凍装置の例としての空気調和機1では、デフロスト運転に入る第1必要条件は、室内熱交換器用温度センサ33により室内熱交換器16の室内熱交換器温度Teiの継続的な低下が検出される状態が第1設定時間継続することである。また、第2必要条件は、室外熱交換器用温度センサ23により室外熱交換器13の室外熱交換器温度Teoの継続的な低下が検出されている状態が第2設定時間継続されることである。ここでは、室内熱交換器用温度センサ33が第1センサであり、室外熱交換器用温度センサ23が第2センサである。そして、第1必要条件だけではなく、第2必要条件をデフロスト運転に入る条件にしている。このことから、室外熱交換器13への着霜以外の理由で室内熱交換器16の温度が低下しているが、室外熱交換器13に着霜していないために室外熱交換器13の温度が上昇する場合をデフロスト運転に突入する場合から除くことができる。 (5) Features (5-1)
As described above, in the
上述の空気調和機1では、室外熱交換器13の室外熱交換器温度Teoの所定サンプリング時間内の平均値言い換えると所定回数nだけサンプリングされた室外熱交換器温の平均値(ΣTeo/n)を用いている。その結果、室外熱交換器温度Teoの測定ノイズによって第2必要条件が満たされたとする判断の誤りを抑制することができ、空除霜が行われるのを安定して防止することができる。 (5-2)
In the
上述の空気調和機1では、室外熱交換器13の室外熱交換器温度Teoが外気温度Tout及び圧縮機11の運転周波数fに応じて設定される除霜突入温度Tpよりも低くなることを第3必要条件として用いる。このような第3必要条件を用いることから、着霜が生じる環境も考慮に入れてデフロスト運転に入るか否かの判断ができるから、空除霜が行われるのを防止し易くなる。 (5-3)
In the
上述の空気調和機1では、室外熱交換器温度Teoが除霜突入温度Tpよりも低い期間が第3設定時間継続しないと第1必要条件及び第2必要条件が満たされてもデフロスト運転に入らないように構成されている。その結果、外気温度Tout及び圧縮機11の運転状況をデフロスト運転に入るか否かの判断に反映させることができ、空除霜が行われるのを防止する効果が高くなる。 (5-4)
In the
2 室内機
3 室外機
10 冷凍回路
11 圧縮機
12 四路切換弁
13 室外熱交換器
14 膨張機構
16 室内熱交換器
21 室外ファン
22 室外温度センサ
23 室外熱交換器用温度センサ
24 室外側制御装置
31 室内ファン
32 室内温度センサ
33 室内熱交換器用温度センサ
34 室内側制御装置 DESCRIPTION OF
Claims (4)
- 圧縮機(11)、室内熱交換器(16)、膨張機構(14)及び室外熱交換器(13)の順に冷媒を流して蒸気圧縮式冷凍サイクルを繰り返すことが可能な冷凍回路(10)と、
前記室内熱交換器の室内熱交換器温度を検出可能な第1センサ(33)と、
前記室外熱交換器の室外熱交換器温度を検出可能な第2センサ(23)と
を備え、
前記室内熱交換器温度の継続的な低下が前記第1センサにより検出される状態が第1設定時間継続する第1必要条件に加えて、前記室外熱交換器温度の継続的な低下が前記第2センサにより検出されている状態が第2設定時間継続する第2必要条件が満たされたときに前記室外熱交換器の除霜のためのデフロスト運転に入るように構成されている、冷凍装置。 A refrigeration circuit (10) capable of repeating a vapor compression refrigeration cycle by flowing refrigerant in the order of the compressor (11), the indoor heat exchanger (16), the expansion mechanism (14), and the outdoor heat exchanger (13). ,
A first sensor (33) capable of detecting an indoor heat exchanger temperature of the indoor heat exchanger;
A second sensor (23) capable of detecting an outdoor heat exchanger temperature of the outdoor heat exchanger,
In addition to the first requirement that the state in which the continuous decrease in the indoor heat exchanger temperature is detected by the first sensor continues for a first set time, the continuous decrease in the outdoor heat exchanger temperature is the first condition. A refrigeration apparatus configured to enter a defrost operation for defrosting the outdoor heat exchanger when a second necessary condition in which a state detected by two sensors continues for a second set time is satisfied. - 前記第2センサにより検出された前記室外熱交換器温度の所定サンプリング時間内の平均値が上昇しない状況が所定回数以上継続する場合に前記第2必要条件が満たされたと判断する、
請求項1に記載の冷凍装置。 Determining that the second necessary condition is satisfied when a state in which an average value within a predetermined sampling time of the outdoor heat exchanger temperature detected by the second sensor does not increase more than a predetermined number of times continues;
The refrigeration apparatus according to claim 1. - 前記室外熱交換器が設置されている箇所の外気温度を検出可能な第3センサ(22)をさらに備え、
前記第2センサにより検出された前記室外熱交換器温度が前記第3センサの検出した前記外気温度及び前記圧縮機の運転周波数に応じて設定される除霜突入温度よりも低くなることを第3必要条件として用い、前記第1必要条件及び前記第2必要条件と前記第3必要条件とが同時に満たされたときに前記デフロスト運転に入るように構成されている、
請求項1に記載の冷凍装置。 A third sensor (22) further capable of detecting an outside air temperature at a location where the outdoor heat exchanger is installed;
Third, the outdoor heat exchanger temperature detected by the second sensor is lower than the defrost entry temperature set according to the outdoor temperature detected by the third sensor and the operating frequency of the compressor. Used as a necessary condition, configured to enter the defrost operation when the first necessary condition and the second necessary condition and the third necessary condition are simultaneously satisfied,
The refrigeration apparatus according to claim 1. - 前記第3必要条件は、前記室外熱交換器温度が前記除霜突入温度よりも低い期間が第3設定時間継続するという条件である、
請求項3に記載の冷凍装置。 The third necessary condition is a condition that a period in which the outdoor heat exchanger temperature is lower than the defrost entry temperature continues for a third set time.
The refrigeration apparatus according to claim 3.
Priority Applications (5)
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BR112018001930-5A BR112018001930A2 (en) | 2015-08-18 | 2016-08-10 | Refrigerating device |
AU2016309268A AU2016309268A1 (en) | 2015-08-18 | 2016-08-10 | Refrigeration device |
EP16837058.3A EP3339761A4 (en) | 2015-08-18 | 2016-08-10 | Refrigeration device |
CN201680047774.7A CN107923646B (en) | 2015-08-18 | 2016-08-10 | Refrigerating plant |
US15/753,310 US20180238578A1 (en) | 2015-08-18 | 2016-08-10 | Refrigeration apparatus |
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JP2015161207A JP6119811B2 (en) | 2015-08-18 | 2015-08-18 | Refrigeration equipment |
JP2015-161207 | 2015-08-18 |
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WO2017030068A1 true WO2017030068A1 (en) | 2017-02-23 |
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PCT/JP2016/073565 WO2017030068A1 (en) | 2015-08-18 | 2016-08-10 | Refrigeration device |
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US (1) | US20180238578A1 (en) |
EP (1) | EP3339761A4 (en) |
JP (1) | JP6119811B2 (en) |
CN (1) | CN107923646B (en) |
AU (1) | AU2016309268A1 (en) |
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WO (1) | WO2017030068A1 (en) |
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CN112050371A (en) * | 2019-06-07 | 2020-12-08 | 青岛海尔空调器有限总公司 | Control method and control device for defrosting of air conditioner and air conditioner |
CN112050356A (en) * | 2019-06-06 | 2020-12-08 | 青岛海尔空调器有限总公司 | Control method and control device for defrosting of air conditioner and air conditioner |
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CN112050373A (en) * | 2019-06-07 | 2020-12-08 | 青岛海尔空调器有限总公司 | Control method and control device for defrosting of air conditioner and air conditioner |
CN112050367A (en) * | 2019-06-07 | 2020-12-08 | 青岛海尔空调器有限总公司 | Control method and control device for defrosting of air conditioner and air conditioner |
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JP6611829B2 (en) * | 2016-02-05 | 2019-11-27 | 三菱電機株式会社 | Air conditioner |
CN108644971B (en) * | 2018-03-21 | 2020-11-10 | 珠海格力电器股份有限公司 | Control method and device for defrosting of air conditioner, storage medium and processor |
CN110631198B (en) * | 2018-06-25 | 2021-06-01 | 青岛海尔空调器有限总公司 | Defrosting control method and device for air conditioner |
CN109916000B (en) * | 2019-03-20 | 2020-04-28 | 珠海格力电器股份有限公司 | Defrosting control method and device for air conditioner, air conditioner and storage medium |
CN112050369B (en) * | 2019-06-07 | 2022-11-18 | 青岛海尔空调器有限总公司 | Control method and control device for defrosting of air conditioner and air conditioner |
CN110454916B (en) * | 2019-08-19 | 2022-03-25 | 广东美的制冷设备有限公司 | Defrosting method of air conditioner and air conditioner |
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CN112050356B (en) * | 2019-06-06 | 2022-08-19 | 青岛海尔空调器有限总公司 | Control method and control device for defrosting of air conditioner and air conditioner |
CN112050371A (en) * | 2019-06-07 | 2020-12-08 | 青岛海尔空调器有限总公司 | Control method and control device for defrosting of air conditioner and air conditioner |
CN112050372A (en) * | 2019-06-07 | 2020-12-08 | 青岛海尔空调器有限总公司 | Control method and control device for defrosting of air conditioner and air conditioner |
CN112050373A (en) * | 2019-06-07 | 2020-12-08 | 青岛海尔空调器有限总公司 | Control method and control device for defrosting of air conditioner and air conditioner |
CN112050367A (en) * | 2019-06-07 | 2020-12-08 | 青岛海尔空调器有限总公司 | Control method and control device for defrosting of air conditioner and air conditioner |
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AU2016309268A1 (en) | 2018-04-19 |
BR112018001930A2 (en) | 2018-09-25 |
EP3339761A1 (en) | 2018-06-27 |
US20180238578A1 (en) | 2018-08-23 |
JP2017040402A (en) | 2017-02-23 |
CN107923646A (en) | 2018-04-17 |
CN107923646B (en) | 2019-02-01 |
EP3339761A4 (en) | 2018-08-08 |
JP6119811B2 (en) | 2017-04-26 |
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