WO2017149664A1 - Réfrigérateur - Google Patents

Réfrigérateur Download PDF

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Publication number
WO2017149664A1
WO2017149664A1 PCT/JP2016/056277 JP2016056277W WO2017149664A1 WO 2017149664 A1 WO2017149664 A1 WO 2017149664A1 JP 2016056277 W JP2016056277 W JP 2016056277W WO 2017149664 A1 WO2017149664 A1 WO 2017149664A1
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WO
WIPO (PCT)
Prior art keywords
operation period
cooling operation
refrigerator
sensor
evaporator
Prior art date
Application number
PCT/JP2016/056277
Other languages
English (en)
Japanese (ja)
Inventor
孔明 仲島
雄亮 田代
前田　剛
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2016/056277 priority Critical patent/WO2017149664A1/fr
Priority to JP2018502913A priority patent/JP6611905B2/ja
Priority to CN201680082180.XA priority patent/CN108885050B/zh
Priority to TW106104049A priority patent/TWI683080B/zh
Publication of WO2017149664A1 publication Critical patent/WO2017149664A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • 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
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/04—Compression machines, plants or systems, with several condenser circuits arranged in series
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
    • F25D21/06—Removing frost
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
    • F25D21/06—Removing frost
    • F25D21/08—Removing frost by electric heating
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
    • F25D21/14—Collecting or removing condensed and defrost water; Drip trays

Definitions

  • the present invention relates to a refrigerator.
  • Some conventional refrigerators include a refrigerant circulation circuit in which a storage room, a compressor, a plurality of condensers, a decompression device, and an evaporator are connected by piping.
  • a refrigeration cycle is constructed with the above configuration, and the storage chamber is cooled by driving the compressor.
  • a conventional refrigerator air is cooled by an evaporator to cool food stored in a storage room.
  • the temperature inside the refrigerator is 2-5 ° C for refrigeration and -20 ° C to -15 ° C for refrigeration, so the evaporator temperature needs to be 0 ° C or less.
  • water vapor in the air in the refrigerator adheres to the evaporator as a condensate, and is then cooled to freeze (frost).
  • frost formation proceeds and frost accumulates on the evaporator surface.
  • a defrosting operation in which frost attached to the evaporator is melted with a heater or the like is periodically performed.
  • Drain water generated by the defrosting operation is discharged through a pipe provided at the lower part of the evaporator into a machine room provided at the lower part of the refrigerator.
  • a compressor, a blower, a drain water tray for receiving drain water, a first condenser immersed in a drain water solution and dissipating heat by the drain water, and the outside air sucked by the blower are radiated by heat.
  • a second condenser is installed (see Patent Document 1).
  • drain water accumulates in the drain water tray. Since drain water is low temperature, the heat dissipation of the first condenser increases. If the number of revolutions per unit time of the blower does not change, the heat dissipation amount of the second condenser also does not change. Therefore, when the two condensers are viewed as a whole, the heat dissipation amount increases by the increase in the heat dissipation amount of the first condenser. When the amount of heat release increases, the condensation temperature decreases, so the power of the compressor can be reduced, thus saving energy.
  • This invention was made in order to solve the above problems, and provides a refrigerator capable of cooling operation that realizes energy saving without deteriorating the performance of the refrigeration cycle after completion of the defrosting operation. With the goal.
  • the refrigerant is configured to circulate in the order of the compressor, the first condenser, the second condenser, the decompression device, and the evaporator, and the evaporation And a drain pan for storing drain water generated in the vessel.
  • the first condenser is accommodated in the drain pan.
  • the refrigerator further includes a fan for sending air to the second condenser.
  • the cooling operation period includes a first cooling operation period following the evaporator defrosting operation period and a second cooling operation period following the first cooling operation period. The rotational speed of the fan in at least a part of the first cooling operation period is smaller than the rotational speed of the fan in the second cooling operation period.
  • the number of rotations of the fan is reduced during the first cooling operation period in which there is drain water after the defrosting operation, so that the heat radiation amount can be adjusted appropriately. As a result, high-performance operation is possible and energy saving can be realized.
  • FIG. 3 is a structural diagram of a cross section of the refrigerator according to Embodiment 1.
  • FIG. It is a figure showing the machine room installed in the back lower part of a refrigerator. It is the figure which looked at the whole refrigerator from the back side.
  • 3 is a timing chart illustrating a control procedure according to the first embodiment.
  • 3 is a flowchart illustrating a control procedure according to the first embodiment.
  • FIG. 4 is a structural diagram of a cross section of a refrigerator according to a second embodiment.
  • 6 is a flowchart showing a procedure for obtaining a low rotational speed time of a machine room fan in a second embodiment. It is a flowchart showing the procedure of the process of step S204 of FIG.
  • FIG. 6 is a structural diagram of a cross-sectional view of a refrigerator according to a third embodiment.
  • 10 is a flowchart showing a procedure for obtaining a low rotational speed time of a machine room fan in a third embodiment.
  • FIG. 6 is a structural diagram of a cross-sectional view of a refrigerator according to a fourth embodiment.
  • 10 is a flowchart showing a procedure for obtaining a low rotational speed time of a machine room fan in a fourth embodiment.
  • FIG. 10 is a structural diagram of a cross-sectional view of a refrigerator according to a fifth embodiment. It is a figure showing the relationship between the amount of frost formation and the speed of the temperature rise of the evaporator 4 during a defrost operation.
  • 10 is a flowchart showing a procedure for obtaining a low rotational speed time of a machine room fan in a fifth embodiment.
  • FIG. 1 is a structural diagram of a cross section of the refrigerator 51 of the first embodiment.
  • the refrigerator 51 includes a refrigeration cycle device 81.
  • the refrigeration cycle apparatus 81 includes a compressor 1, a condenser 2, a decompressor (capillary 3), and an evaporator 4 that are communicated with each other.
  • the refrigerant circulates in the order of the compressor 1, the condenser 2, the decompressor 3, and the evaporator 4.
  • the evaporator 4 is disposed in the cooling chamber 10.
  • the compressor 1, the condenser 2, and the decompressor 3 are disposed in the machine room 11. Although the machine room 11 may be arranged in addition to these, the description is omitted in FIG. 1 and described in FIG.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 is a drain water evaporation condenser (water-cooled condenser: first condenser), machine room condenser (air-cooled condenser: second condenser), side face
  • the high-pressure liquid refrigerant is obtained by passing through the condenser 2 composed of pipes in this order and exchanging heat with the outside air.
  • the condenser 2 is simplified, and only the air-cooled condenser is shown.
  • the condensed high-pressure liquid refrigerant is decompressed by a decompressor 3 constituted by a decompression valve, and becomes a low-pressure low-temperature two-phase refrigerant.
  • the refrigerant flows into the evaporator 4 installed in the refrigerator 51.
  • the air in the refrigerator 51 and the refrigerant exchange heat.
  • the air in the refrigerator 51 is cooled by the refrigerant, and the refrigerant becomes a low-pressure gas refrigerant.
  • the refrigerant that has become low-pressure gas flows into the compressor 1 and is pressurized again and discharged.
  • the solid line arrows represent the flow of air cooled in the cooling chamber 10 from the storage chambers 7a, 7b, and 7c.
  • a dotted arrow represents a flow in which the air that has cooled the storage chambers 7a, 7b, and 7c returns to the cooling chamber.
  • the air cooled by heat exchange with the refrigerant in the cooling chamber 10 is transported by the refrigerator fan 5a and flows into the storage chambers 7a, 7b, 7c through the air passages connected to the storage chambers 7a, 7b, 7c. Then, the storage chambers 7a, 7b, and 7c are cooled.
  • the storage chambers 7a, 7b, and 7c are adjusted by adjusting the air volume of the cooling air by changing the number of rotations (that is, the rotation speed) of the fan 5a for the refrigerator or operating the air volume regulator 6 (damper). Adjust the temperature.
  • the cooling air that has cooled the storage chambers 7a, 7b, and 7c passes through the return air passage, flows into the cooling chamber again, and is cooled again by the evaporator 4.
  • the refrigerator 51 further includes a controller 30.
  • the controller 30 controls each component in the refrigerator 51.
  • FIG. 2 is a diagram illustrating the machine room 11 installed at the lower back of the refrigerator 51.
  • a compressor 1 In the machine room 11, a compressor 1, a drain water evaporation tray (drain pan) 8, a drain water evaporation condenser 2a, a machine room condenser 2b, and a machine room fan 5b are installed.
  • the radiant heater 38 is disposed between the evaporator 4 and the drain water evaporating dish 8.
  • the radiant heater 38 includes a heating wire for warming air.
  • the knuckle heater 37 is installed in direct contact with the evaporator 4. During the defrosting operation of the evaporator 4, the radiant heater 38 and the click heater 37 are operated.
  • a hole 12 for discharging drain water generated in the evaporator 4 by a defrosting operation is provided in the upper part of the drain water evaporation dish 8. Drain water falls through the hole 12 to the drain water evaporating dish 8 by gravity.
  • the drain water evaporation condenser 2a which is a water-cooled condenser, is accommodated in the drain water evaporation dish 8, and can be cooled by the drain water when there is drain water in the drain water evaporation dish 8.
  • FIG. 3 is a view of the entire refrigerator 51 as seen from the back side.
  • a side pipe 2C through which the high-pressure refrigerant flows is provided in the sheet metal on the side surface of the refrigerator 51. Through this side surface, the refrigerant flowing through the side pipe 2C and the outside air exchange heat.
  • the pipe through which such a high-pressure refrigerant flows is not only installed on the side surface, but may be installed so as to pass through the ceiling of the refrigerator 51. Thereby, the heat radiation area can be increased.
  • FIG. 4 is a timing chart showing the control procedure of the first embodiment.
  • FIG. 5 is a flowchart showing the control procedure of the first embodiment.
  • step S101 when the temperature of evaporator 4 detected by a temperature sensor (not shown) or the like is smaller than a predetermined threshold value TH1 in step S101, the process proceeds to step S102.
  • a predetermined threshold value TH1 is set to a temperature at which a predetermined amount of frost is stacked on the surface of the evaporator 4 and the cooling performance is expected to decrease by a certain amount.
  • This threshold value TH1 can be obtained from experiments or simulations.
  • step S102 the controller 30 stops the cooling operation and starts the defrosting operation. That is, the controller 30 stops the cooling operation by stopping the compressor 1, energizes the knuckle heater 37, radians, and the heater 38 to defrost the evaporator 4. Furthermore, the controller 30 stops the machine room fan 5b.
  • step S103 when the temperature of the evaporator 4 becomes higher than the predetermined threshold value TH2, the process proceeds to step S104.
  • the threshold TH2 is set to a temperature at which defrosting of the evaporator 4 is expected to be completed. This threshold value TH2 can be obtained from experiments or simulations.
  • step S104 the controller 30 stops the defrosting operation and starts the cooling operation. That is, the controller 30 starts the cooling operation by operating the compressor 1, stops the cavitation heater 37 and the radiant heater 38, and ends the defrosting of the evaporator 4. Thereby, cooling in the refrigerator 1 is restarted.
  • the controller 30 determines the rotation speed per unit time of the machine room fan 3b from the normal rotation speed X2 per unit time. Is also set to a small rotational speed X1. The reason why the number of revolutions per unit time is reduced will be described.
  • the drain water generated by the defrosting is collected in the drain water evaporation dish 8, so that the heat radiation amount of the drain water evaporation condenser 2a is increased.
  • time (DELTA) t after a defrost operation stop the rotation speed per unit time of the machine room fan 5b is made low compared with the time of normal operation. As a result, it is possible to realize an energy-saving operation that suppresses the power of the machine room fan 5b while securing a heat radiation amount equivalent to that in the normal state.
  • step S105 when a predetermined time ⁇ t has elapsed from time t2, the process proceeds to step S106.
  • the time ⁇ t is a time expected to decrease until the drain water generated by the defrosting disappears or to a certain amount.
  • a predetermined fixed length can be set by examination through experiments or simulations.
  • step S106 the controller 30 sets the rotation speed per unit time of the machine room fan 3b to the normal rotation in the second cooling operation period that is a period until the cooling operation is completed following the first cooling operation period. Change to number X2.
  • the unit of the machine room fan 5b is controlled. Since an energy-saving operation can be performed without providing a sensor for controlling the number of revolutions per hour, the cost can be reduced.
  • the number of revolutions per unit time of the machine room fan 5b can be lowered, so that energy saving is realized without deteriorating the performance of the refrigeration cycle. can do. Furthermore, since the rotational speed per unit time of the machine room fan 5b is lowered when drain water is present, the noise of the machine room fan 5b can be reduced.
  • Emodiment 2 The configuration of the refrigerator according to the second embodiment is substantially the same as the configuration of the refrigerator according to the first embodiment, but the control method for the machine room fan 5b is different.
  • the amount of drain water generated by the defrosting operation varies depending on the operation state of the refrigerator and the surrounding environment before the defrosting operation.
  • the drain water cold heat source can be effectively utilized.
  • the refrigerators of the second to fifth embodiments detect or estimate the amount of drain water in addition to the function of the refrigerator of the first embodiment, and rotate the machine room fan 5b per unit time according to the amount of drain water.
  • a function of setting a time for lowering the number (hereinafter referred to as low rotation speed time) ⁇ t is provided.
  • FIG. 6 is a structural diagram of a cross-sectional view of the refrigerator 52 according to the second embodiment.
  • the refrigerator 52 according to the present embodiment includes door opening / closing sensors 34a, 34b, and 34c as sensors for detecting or estimating the amount of drain water stored in the drain water evaporation tray after completion of the defrosting operation.
  • the humid air that forms frost on the evaporator 4 is generated when outside air enters the cabinet by opening and closing the door. For this reason, in the operation section before the defrosting operation is started, the number of frosting increases as the number of times the door is opened and closed is longer and the door is opened longer. If the amount of frost formation is large, the amount of drain water generated by the defrosting operation increases.
  • the door open / close sensor 34a outputs a signal indicating that the door of the storage chamber 7a is opened, and outputs a signal indicating that the door is closed when the door of the storage chamber 7a is closed.
  • the door opening / closing sensor 34b outputs a signal indicating that the storage chamber 7b is opened when the door of the storage chamber 7b is opened, and outputs a signal indicating that the door is closed when the door of the storage chamber 7b is closed.
  • the door opening / closing sensor 34c outputs a signal indicating that the storage chamber 7c is opened when the door of the storage chamber 7c is opened, and outputs a signal indicating that the door is closed when the door of the storage chamber 7c is closed.
  • the controller 30 obtains the low rotation speed time ⁇ t during the current cooling operation period of the machine room fan 5b according to the output signals of the door opening / closing sensors 34a, 34b, 34c in the previous cooling operation period.
  • FIG. 7 is a flowchart showing a procedure for obtaining the low rotational speed time ⁇ t of the machine room fan 5b in the second embodiment.
  • step S201 the controller 30 sets the number of times Na of opening the door of the storage chamber 7a, the number of times Nb of opening the door of the storage chamber 7b, and the number of times Nc of opening the door of the storage chamber 7c to 0. Set.
  • step S202 the controller 30 sets the total time Ta when the door of the storage chamber 7a is opened, the total time Tb when the door of the storage chamber 7b is opened, and the total time Tc when the door of the storage chamber 7c is opened to 0. To do.
  • step S203 when the defrosting operation is started, the process proceeds to step S207, and when the defrosting operation is not started, the process proceeds to step S204.
  • step S204 the controller 30 obtains the number Na of opening times of the door of the storage chamber 7a and the total opening time Ta based on the output signal of the door opening / closing sensor 34a.
  • step S205 the controller 30 obtains the number Nb of times when the door of the storage chamber 7b is opened and the total time Tb of the opening based on the output signal of the door opening / closing sensor 34b.
  • step S206 the controller 30 obtains the number Nc of times when the door of the storage chamber 7c is opened and the total time Tc of the opening based on the output signal of the door opening / closing sensor 34c.
  • step S207 when the defrosting operation is completed, the process proceeds to step S208.
  • step S208 the controller 30 obtains an added value N of Na, Nb, and Nc.
  • step S209 the controller 30 calculates an added value T of Ta, Tb, and Tc.
  • step S211 the controller 30 obtains the low rotation speed time ⁇ t according to the magnitude of Y.
  • the low rotation speed time ⁇ t may be set in proportion to Y.
  • step S212 when the power of the refrigerator 52 is turned off, the process is completed, and when the power of the refrigerator 52 is kept on, the process returns to step S201.
  • FIG. 8 is a flowchart showing the procedure of the process in step S204 of FIG.
  • the procedure of steps S205 and S206 in FIG. 7 is the same as this.
  • step S301 when the controller 30 receives a signal indicating that the door of the storage chamber 7a is opened from the door opening / closing sensor 34a, the controller 30 advances the process to step S302.
  • step S302 the controller 30 starts a timer.
  • step S303 when the controller 30 receives a signal indicating that the door of the storage chamber 7a is closed from the door opening / closing sensor 34a, the controller 30 advances the process to step S304.
  • step S304 the controller 30 adds a timer value to the total time Ta when the door of the storage chamber 7a is opened.
  • step S305 the controller 30 increases the number Na of times that the door of the storage chamber 7a is opened by one.
  • the present embodiment it is possible to estimate the amount of drain water generated by the defrosting operation based on the output of the door opening / closing sensor and set the low rotation speed time of the machine room fan. it can.
  • the configuration of the refrigerator according to the third embodiment is the same as the configuration of the refrigerator according to the first embodiment, but the control method for the machine room fan 5b is different.
  • FIG. 9 is a structural diagram of a cross-sectional view of the refrigerator 53 of the third embodiment.
  • the refrigerator 53 of the present embodiment includes an outside air humidity sensor 33 as a sensor for detecting or estimating the amount of drain water.
  • the controller 30 obtains the low rotation speed time ⁇ t in the current cooling operation period of the machine room fan 5b according to the output signal of the humidity sensor 35 in the previous cooling operation period.
  • the controller 30 lengthens the low rotational speed time ⁇ t for decreasing the rotational speed per unit time of the machine room fan 5b if the average humidity of the outside air during the previous cooling operation period is high, and decreases if the average humidity is low.
  • the rotation time ⁇ t is shortened.
  • FIG. 10 is a flowchart showing a procedure for obtaining the low rotational speed time ⁇ t of the machine room fan 5b in the third embodiment.
  • step S401 the controller 30 sets the average humidity M of the outside air to zero.
  • step S402 when the defrosting operation is started, the process proceeds to step S406, and when the defrosting operation is not started, the process proceeds to step S403.
  • step S403 the controller 30 advances the process to step S404 when a predetermined time has elapsed since the previous external humidity measurement.
  • step S404 the controller 30 receives the signal representing the outside air humidity output from the outside air humidity sensor 33 and acquires the humidity S of the outside air.
  • step S405 the controller 30 calculates the average M of the outside air humidity up to the present based on the acquired outside air humidity S.
  • step S406 when the defrosting operation is completed, the process proceeds to step S407.
  • step S407 the controller 30 obtains the low rotation speed time ⁇ t according to the average M of the outside air humidity.
  • the low rotation speed time ⁇ t may be set in proportion to M.
  • step S408 when the power of the refrigerator 53 is turned off, the process ends, and when the power of the refrigerator 53 is kept on, the process returns to step S401.
  • the amount of drain water generated by the defrosting operation is estimated based on the output of the outside air humidity sensor, and the low rotation time of the machine room fan can be set. it can.
  • FIG. 11 is a structural diagram of a cross-sectional view of the refrigerator 54 according to the fourth embodiment.
  • the refrigerator 54 of the present embodiment includes the rotation speed sensor 31 of the compressor 1 as a sensor that detects or estimates the amount of drain water.
  • the rotation speed sensor 31 detects the rotation speed (rotational speed) of the compressor 1 per unit time.
  • the controller 30 obtains the current low rotational speed time ⁇ t of the machine room fan 5b according to the output signal of the rotational speed sensor 31 of the compressor 1 in the immediately preceding cooling operation period.
  • the compressor 1 When the number of rotations per unit time of the compressor 1 is high, the compressor 1 is operated with a large refrigerating capacity proportional to it, so that more cooling is performed. The higher the number of revolutions per unit time of the compressor 1 during the cooling operation period before the defrosting operation, the larger the cooling operation is performed, so the amount of frost formation on the evaporator 4 also increases. Therefore, if the total number of revolutions per unit time of the compressor 1 during the previous cooling operation period is high, the controller 30 increases the low revolution time ⁇ t that lowers the revolutions per unit time of the machine room fan 5b. If the total number of revolutions per unit time of the compressor 1 during the previous cooling operation period is low, the low revolution number time ⁇ t for lowering the revolution number per unit time of the machine room fan 5b is shortened.
  • FIG. 12 is a flowchart showing a procedure for obtaining the low rotational speed time ⁇ t of the machine room fan 5b in the fourth embodiment.
  • step S501 the controller 30 sets the total number R of rotations of the compressor 1 to zero.
  • step S502 when the defrosting operation is started, the process proceeds to step S506, and when the defrosting operation is not started, the process proceeds to step S503.
  • step S503 the controller 30 advances the process to step S504 when the unit time has elapsed since the previous acquisition of the rotational speed P of the compressor 1 per unit time.
  • step S504 the controller 30 receives a signal representing the rotational speed per unit time of the compressor 1 output from the rotational speed sensor 31, and acquires the rotational speed P per unit time of the compressor 1.
  • step S505 the controller 30 adds the acquired rotation speed P per unit time to the total rotation speed R of the compressor 1.
  • step S506 when the defrosting operation is completed, the process proceeds to step S507.
  • step S507 the controller 30 obtains the low rotational speed time ⁇ t according to the total rotational speed R of the compressor 1.
  • the low rotation speed time ⁇ t may be set in proportion to R.
  • step S508 when the power of the refrigerator 54 is turned off, the process is completed, and when the power of the refrigerator 54 is kept on, the process returns to step S501.
  • the amount of drain water generated by the defrosting operation is estimated based on the output of the rotation sensor of the compressor, and the low rotation time of the machine room fan is set. be able to.
  • the low revolution number time ⁇ t may be obtained based on the average number of revolutions per unit time of the compressor.
  • Emodiment 5 The configuration of the refrigerator according to the fifth embodiment is the same as the configuration of the refrigerator according to the first embodiment, but the control method of the machine room fan 5b is different, so that point will be described.
  • FIG. 13 is a structural diagram of a cross-sectional view of the refrigerator according to the fourth embodiment.
  • the refrigerator 55 of the present embodiment includes a temperature sensor 32 that detects the temperature of the evaporator as a sensor that detects or estimates the amount of drain water.
  • the heaters 37 and 38 installed near the evaporator 4 are used for defrosting, so that the temperature gradually rises when the heaters 37 and 38 are energized. At this time, if the amount of frost formation is large, the heat capacity of the frost formation increases, so the temperature rise of the evaporator 4 is delayed.
  • FIG. 14 is a diagram showing the relationship between the amount of frost formation and the rate of temperature rise of the evaporator 4 during the defrosting operation.
  • the amount of frost formation can be detected by the rate of temperature rise of the evaporator 4. Since the amount of drain water increases as the frost amount increases during the defrosting operation, the amount of drain water can also be detected by detecting the rate of temperature rise of the evaporator 4.
  • the controller 30 obtains the time td required for the temperature of the evaporator 4 detected by the temperature sensor 32 to increase by ⁇ Tdef after the start of the defrosting operation as the temperature increase rate of the evaporator 4. . Based on td in the previous defrosting operation period, the controller 30 obtains the low rotation speed time ⁇ t in the current cooling operation period. If td is long (that is, if the temperature increase rate is low), the amount of frost formation is large. Therefore, the controller 30 sets the low rotation time ⁇ t to be long, and if td is short (that is, if the temperature increase rate is large) Since the amount of frost is small, the low revolution time ⁇ t is set short.
  • FIG. 15 is a flowchart showing a procedure for calculating the low rotational speed time ⁇ t of the machine room fan 5b in the fifth embodiment.
  • step S601 when the defrosting operation is started in step S601, the process proceeds to step S602.
  • step S602 the controller 30 starts a timer.
  • step S ⁇ b> 603 the controller 30 receives a signal representing the temperature of the evaporator 4 output from the temperature sensor 32 and acquires the temperature of the evaporator 4.
  • the controller 30 advances the process to step S604.
  • step S604 the controller 30 sets the timer value to the temperature rise required time td.
  • step S605 the controller 30 obtains the low rotation speed time ⁇ t according to the magnitude of the temperature rise required time td.
  • the low rotation speed time ⁇ t may be set in proportion to td.
  • step S606 when the defrosting operation is completed, the process proceeds to step S607.
  • step S607 when the power of the refrigerator 55 is turned off, the process ends, and when the power of the refrigerator 55 is kept on, the process returns to step S501.
  • the amount of drain water generated by the defrosting operation is estimated based on the output of the temperature sensor that detects the temperature of the evaporator, and the low rotation speed of the machine room fan is estimated. You can set the time.
  • the present invention is not limited to the above embodiment, and includes, for example, the following modifications.
  • (1) Use of a plurality of sensors In the above-described embodiment, the low rotation speed time ⁇ of the machine room fan is obtained based on the output of one type of sensor, but based on the combination of the outputs of the plurality of types of sensors, The low rotation time ⁇ t of the machine room fan may be obtained.
  • (2) Adjustment of the rotation speed of the machine room fan 3b In the above-described embodiment, the machine room fan 3b is adjusted during the entire first cooling operation period of ⁇ t from the start of the cooling operation following the end of the defrosting operation period.
  • the rotation speed per unit time is set to the rotation speed X1 smaller than the normal rotation speed X2 per unit time, it is not limited to this.
  • the rotation number per unit time of the machine room fan 3b in the second cooling operation period is set to a normal rotation number X2 and the machine room fan 3b of the machine room fan 3b in a part of the first cooling operation period.
  • the number of revolutions per unit time is set to a number of revolutions X1 smaller than the usual number of revolutions X2 per unit time, and in a period other than a part of the first cooling operation period, per unit time of the machine room fan 3b. May be set to the same or higher rotational speed than the normal rotational speed X2 per unit time.
  • the energy required for operating the machine room fan 3b in this way is the first cooling operation period and the second cooling period.
  • the rotational speed per unit time of the machine room fan 3b may be smaller than the energy required to operate at the normal rotational speed X2 per unit time.
  • the rotation speed per unit time of at least a part of the machine room fan 3b in the first cooling operation period is a fixed value X1
  • the rotation speed per unit time of the machine room fan 3b in the second cooling operation period is a fixed value. It is not limited to X2. These values are not necessarily fixed values, and the number of revolutions per unit time of at least a part of the machine room fan 3b in the first cooling operation period is equal to that of the machine room fan 3b in the second cooling operation period. What is necessary is just to satisfy
  • the machine room fan 3b may be stopped during at least a part of the first cooling operation period.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Defrosting Systems (AREA)
  • Removal Of Water From Condensation And Defrosting (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Abstract

La présente invention concerne un réfrigérateur qui est équipé d'un dispositif à cycle de réfrigération (81), qui est configuré de sorte qu'un réfrigérant circule à travers un compresseur (1), un condenseur refroidi par eau (2a), un condenseur refroidi par air (2b), un dispositif de décompression, et un évaporateur (4) dans cet ordre, pendant une période d'opération de refroidissement. Un plateau de dégivrage (4) stocke l'eau de dégivrage générée par l'évaporateur (4). Le condenseur refroidi par eau (2a) est logé dans le plateau de dégivrage (4). Un ventilateur (5b) envoie de l'air au condenseur refroidi par air (2b). La période d'opération de refroidissement comprend une première période d'opération de refroidissement qui suit une période d'opération de dégivrage et une deuxième période d'opération de refroidissement qui suit la première période d'opération de refroidissement. La vitesse de rotation du ventilateur (5b) pendant au moins une partie de la première période d'opération de refroidissement est inférieure à celle du ventilateur (5b) pendant la deuxième période d'opération de refroidissement.
PCT/JP2016/056277 2016-03-01 2016-03-01 Réfrigérateur WO2017149664A1 (fr)

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PCT/JP2016/056277 WO2017149664A1 (fr) 2016-03-01 2016-03-01 Réfrigérateur
JP2018502913A JP6611905B2 (ja) 2016-03-01 2016-03-01 冷蔵庫
CN201680082180.XA CN108885050B (zh) 2016-03-01 2016-03-01 冰箱
TW106104049A TWI683080B (zh) 2016-03-01 2017-02-08 冰箱

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CN109708394A (zh) * 2018-12-06 2019-05-03 青岛海尔股份有限公司 用于冰箱的散热风机的控制方法及控制系统
CN111609633A (zh) * 2019-02-26 2020-09-01 青岛海尔股份有限公司 风冷冰箱
WO2023011910A1 (fr) * 2021-08-04 2023-02-09 BSH Hausgeräte GmbH Appareil de froid avec ventilateur de condenseur et procédé pour faire fonctionner un appareil de froid équipé d'un ventilateur de condenseur

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CN110375477B (zh) * 2018-04-13 2024-04-19 青岛海尔制冷电器有限公司 制冷室位于冷冻间室底部的冰箱
KR20200062698A (ko) * 2018-11-27 2020-06-04 엘지전자 주식회사 냉장고 및 그의 제어방법
EP3882546A4 (fr) 2019-01-03 2021-11-17 Hefei Midea Refrigerator Co., Ltd. Réfrigérateur ainsi que procédé de commande et dispositif de commande de celui-ci
CN113776254B (zh) * 2019-12-13 2022-10-11 广东哈士奇制冷科技股份有限公司 一种具有化霜功能的冰箱
CN115540436A (zh) * 2021-06-30 2022-12-30 青岛海尔电冰箱有限公司 制冷设备
CN115540435A (zh) * 2021-06-30 2022-12-30 青岛海尔电冰箱有限公司 冰箱
CN113776268A (zh) * 2021-09-23 2021-12-10 珠海格力电器股份有限公司 一种冰箱冷凝风扇控制方法、系统及冰箱

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CN109708394A (zh) * 2018-12-06 2019-05-03 青岛海尔股份有限公司 用于冰箱的散热风机的控制方法及控制系统
CN109708394B (zh) * 2018-12-06 2020-10-30 青岛海尔股份有限公司 用于冰箱的散热风机的控制方法及控制系统
CN111609633A (zh) * 2019-02-26 2020-09-01 青岛海尔股份有限公司 风冷冰箱
CN111609633B (zh) * 2019-02-26 2022-03-25 海尔智家股份有限公司 风冷冰箱
WO2023011910A1 (fr) * 2021-08-04 2023-02-09 BSH Hausgeräte GmbH Appareil de froid avec ventilateur de condenseur et procédé pour faire fonctionner un appareil de froid équipé d'un ventilateur de condenseur

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TWI683080B (zh) 2020-01-21
CN108885050A (zh) 2018-11-23
TW201741609A (zh) 2017-12-01
JP6611905B2 (ja) 2019-11-27
CN108885050B (zh) 2022-02-01
JPWO2017149664A1 (ja) 2018-11-22

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