WO2020110301A1 - Appareil à cycle frigorifique - Google Patents

Appareil à cycle frigorifique Download PDF

Info

Publication number
WO2020110301A1
WO2020110301A1 PCT/JP2018/044236 JP2018044236W WO2020110301A1 WO 2020110301 A1 WO2020110301 A1 WO 2020110301A1 JP 2018044236 W JP2018044236 W JP 2018044236W WO 2020110301 A1 WO2020110301 A1 WO 2020110301A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
region
heating operation
refrigeration cycle
heat transfer
Prior art date
Application number
PCT/JP2018/044236
Other languages
English (en)
Japanese (ja)
Inventor
中村　伸
加藤　央平
翼 丹田
前田　剛志
暁 八柳
森田　敦
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/JP2018/044236 priority Critical patent/WO2020110301A1/fr
Priority to JP2020557516A priority patent/JPWO2020110301A1/ja
Publication of WO2020110301A1 publication Critical patent/WO2020110301A1/fr

Links

Images

Classifications

    • 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
    • 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F17/00—Removing ice or water from heat-exchange apparatus

Definitions

  • the present invention relates to a refrigeration cycle device.
  • a fin-and-tube heat exchanger including a plurality of plate-shaped fins and a plurality of heat transfer tubes that penetrate the plurality of fins in the direction in which the plurality of fins are arranged.
  • a fin-and-tube type heat exchanger may use a heat transfer tube having a flat cross section.
  • the heat transfer tube surrounding the heat transfer tube is on the windward side in the blowing direction. Frost is likely to occur on the part of the evaporator. For this reason, the formation of frost on the fins tends to block the air passages provided between the plurality of fins.
  • Patent Document 1 Japanese Patent No. 3264525 (Patent Document 1) describes a heat exchanger capable of suppressing the formation of frost on the windward ends of the fins in the blowing direction.
  • Patent Document 1 describes a heat exchanger capable of suppressing the formation of frost on the windward ends of the fins in the blowing direction.
  • frost is formed at the windward end portion. This can be suppressed. Therefore, it is possible to prevent the air passages provided between the plurality of fins from being closed due to the formation of frost on the windward end portion.
  • the heat exchanger described in the above publication cannot suppress the formation of frost on parts other than the windward end. Therefore, the defrosting operation is required to melt the frost that has frosted around the heat transfer tubes and the portions around the heat transfer tubes of the fins. This frost is melted by the defrosting operation to form water drops.
  • the frosting operation is started again, so that air is blown to the heat exchanger. Therefore, the water droplets generated in the defrosting operation travel rearward in the air blowing direction along the surface of the flat heat transfer tube and stay in the upper part or the lower part of the flat heat transfer tube. Therefore, the water droplets generated in the defrosting operation are not properly discharged.
  • the present invention has been made in view of the above problems, and an object thereof is to suppress the formation of frost at the site of the evaporator on the windward side in the blowing direction during the heating operation, and in the defrosting operation.
  • An object of the present invention is to provide a refrigeration cycle device that can appropriately discharge generated water droplets.
  • the refrigeration cycle device of the present invention includes a compressor, a condenser, a pressure reducing device, an evaporator, and a blower fan.
  • the compressor compresses the refrigerant.
  • the condenser condenses the refrigerant compressed by the compressor.
  • the decompression device decompresses the refrigerant condensed by the condenser.
  • the evaporator evaporates the refrigerant decompressed by the decompression device.
  • the blower fan blows air to the evaporator.
  • the evaporator includes fins and heat transfer tubes that are inserted into the fins and have a flat cross section.
  • the fin includes a first region in which the heat transfer tube is inserted and a second region protruding from the heat transfer tube in a direction opposite to the air blowing direction in the heating operation.
  • the blower fan blows air from the second region to the first region in the heating operation and directs the first region to the second region after the defrosting operation is performed to melt the frost accumulated on the evaporator in the heating operation. It is configured to blow air.
  • the fin includes the second region protruding from the heat transfer tube in the direction opposite to the air blowing direction in the heating operation. For this reason, it is possible to prevent frost formation on the part of the evaporator on the windward side in the blowing direction during the heating operation.
  • the blower fan is configured to blow air from the first region to the second region after the defrosting operation is performed. For this reason, since the water droplets generated in the defrosting operation are discharged along the second region, the water droplets generated in the defrosting operation can be appropriately discharged.
  • FIG. 1 shows an example of the refrigerant circuit diagram of the refrigerating cycle device which concerns on Embodiment 1 of this invention.
  • FIG. 3 is a partial side view of the outdoor heat exchanger shown in FIG. 2.
  • FIG. 2 shows an example of the outdoor heat exchanger shown by FIG. 3.
  • FIG. 3 is a partial side view of the outdoor heat exchanger shown in FIG. 2.
  • It is a partial cross section of the modification of the evaporator which concerns on Embodiment 1 of this invention.
  • It is a time chart shows control of the air conditioner which concerns on Embodiment 1 of this invention.
  • It is a flowchart which shows the control of the air conditioner which concerns on Embodiment 1 of this invention.
  • Refrigeration cycle device 1 of the present embodiment is, for example, an air conditioner.
  • the refrigeration cycle device 1 includes a compressor 2, an indoor heat exchanger 3, an indoor fan 4, a pressure reducing device 5, an outdoor heat exchanger 10, an outdoor fan 6, and a four-way valve. 7, a temperature sensor 8, and a control device 100 are mainly provided.
  • the compressor 2, the outdoor heat exchanger 10, the pressure reducing device 5, the outdoor fan 6, the four-way valve 7, the temperature sensor 8 and the control device 100 are housed in the outdoor unit 1a, and the indoor heat exchanger 3 and the indoor fan 4 are included. Are housed in the indoor unit 1b.
  • a refrigerant circuit capable of circulating a refrigerant is configured.
  • the refrigeration cycle apparatus 1 performs a refrigeration cycle in which the refrigerant circulates in the refrigerant circuit while changing its phase.
  • the compressor 2 compresses the refrigerant.
  • the compressor 2 is configured to compress the sucked refrigerant and discharge it.
  • the compressor 2 has a variable capacity.
  • the compressor 2 is configured so that the capacity is changed by adjusting the rotation speed by changing the frequency based on an instruction from the control device 100.
  • the compressor 2 is, for example, a rotary compressor, a scroll compressor, a screw compressor, a reciprocating compressor, or the like.
  • the indoor heat exchanger 3 is for exchanging heat between the refrigerant flowing in the indoor heat exchanger 3 and the indoor air.
  • the indoor heat exchanger 3 is connected to the pressure reducing device 5 and the four-way valve 7.
  • the indoor heat exchanger 3 functions as a condenser that condenses the refrigerant compressed by the compressor 2 during the heating operation, and functions as an evaporator that evaporates the refrigerant decompressed by the decompression device 5 during the cooling operation.
  • the indoor heat exchanger 3 is, for example, a fin-and-tube heat exchanger, a microchannel heat exchanger, a shell-and-tube heat exchanger, a heat pipe heat exchanger, a double-tube heat exchanger, or a plate heat exchanger. It is a container etc.
  • the pressure reducing device 5 expands the refrigerant to reduce the pressure.
  • the decompression device 5 is configured to decompress the refrigerant condensed by the condenser.
  • the decompression device 5 is, for example, an electric expansion valve capable of adjusting the flow rate of the refrigerant.
  • the decompression device 5 may be not only an electric expansion valve, but also a mechanical expansion valve having a diaphragm for a pressure receiving portion, a capillary tube, or the like.
  • the indoor fan 4 is attached to the indoor heat exchanger 3 and supplies indoor air as a heat exchange fluid to the indoor heat exchanger 3.
  • the indoor fan 4 blows air to the indoor heat exchanger 3.
  • the indoor fan 4 adjusts the amount of air flowing around the indoor heat exchanger 3 by adjusting the number of rotations of the indoor fan 4 based on an instruction from the control device 100, and thereby the room air and the refrigerant are separated from each other. It is configured to adjust the amount of heat exchange of.
  • the outdoor heat exchanger 10 is for exchanging heat between the refrigerant flowing in the outdoor heat exchanger 10 and the outdoor air.
  • the outdoor heat exchanger 10 is connected to the pressure reducing device 5 and the four-way valve 7.
  • the outdoor heat exchanger 10 functions as an evaporator that evaporates the refrigerant decompressed by the decompression device 5 during the heating operation, and functions as a condenser that condenses the refrigerant compressed by the compressor 2 during the cooling operation.
  • the outdoor heat exchanger 10 is a fin-and-tube heat exchanger. Details of the outdoor heat exchanger 10 will be described later.
  • the outdoor fan 6 is attached to the outdoor heat exchanger 10 and supplies outdoor air to the outdoor heat exchanger 10.
  • the outdoor fan 6 blows air to the outdoor heat exchanger 10.
  • the outdoor fan 6 adjusts the amount of air flowing around the outdoor heat exchanger 10 by adjusting the number of revolutions of the outdoor fan 6 based on an instruction from the control device 100, and thereby the air between the outdoor air and the refrigerant is adjusted. It is configured to adjust the amount of heat exchange of.
  • the outdoor fan 6 is an axial fan.
  • the outdoor fan 6 is configured so that the rotation direction of the outdoor fan 6 can be switched between a forward direction and a reverse direction. The outdoor fan 6 rotates in the forward direction during the heating operation, and rotates in the reverse direction during the cooling operation and the defrosting operation.
  • the four-way valve 7 can switch the flow path of the refrigerant in the refrigeration cycle apparatus 1. During the heating operation, the four-way valve 7 is switched so as to connect the discharge port of the compressor 2 to the indoor heat exchanger 3 and connect the suction port of the compressor 2 to the outdoor heat exchanger 10. The four-way valve 7 connects the discharge port of the compressor 2 and the outdoor heat exchanger 10 and connects the suction port of the compressor 2 and the indoor heat exchanger 3 during the cooling operation and the dehumidifying operation. Can be switched.
  • the temperature sensor 8 is for measuring the temperature of the refrigerant flowing through the outdoor heat exchanger 10.
  • the temperature sensor 8 is provided in the refrigerant circuit so as to detect the liquid pipe temperature of the outdoor heat exchanger 10.
  • the control device 100 is configured to perform calculations, instructions and the like to control each means, equipment and the like of the refrigeration cycle apparatus 1.
  • the control device 100 is electrically connected to the compressor 2, the indoor fan 4, the pressure reducing device 5, the outdoor fan 6, the four-way valve 7, the temperature sensor 8 and the like, and is configured to control the operations of these. ..
  • FIG. 2 shows the external appearance of the outdoor heat exchanger 10 according to this embodiment.
  • the X direction is the lateral direction and represents the lateral direction of the fins 30 of the outdoor heat exchanger 10, that is, the width direction.
  • the Y direction is the lateral direction, and represents the direction in which the fins 30 forming the same heat exchange section are arranged in parallel.
  • the Z direction is the vertical direction, that is, the direction of gravity, and represents the longitudinal direction of the fins 30.
  • a white arrow indicates the flow direction of the air supplied to the outdoor heat exchanger 10 by the outdoor fan 6 shown in FIG. 1 during the heating operation.
  • air is supplied in the X direction by the outdoor fan 6 shown in FIG. 1 during the heating operation.
  • FIG. 3 shows a main part when the outdoor heat exchanger 10 is viewed from the Y direction.
  • FIG. 4 shows a main part when the outdoor heat exchanger 10 is viewed from the X direction. 3 and 4, two heat transfer tubes 20 arranged side by side in the Z direction are shown.
  • the outdoor heat exchanger 10 is, for example, a two-row structure heat exchanger, and includes a windward heat exchanger 10a and a leeward heat exchanger 10b.
  • Each of the windward side heat exchanger 10a and the leeward side heat exchanger 10b is a fin and tube type heat exchanger.
  • the windward-side heat exchanger 10a and the leeward-side heat exchanger 10b are arranged side by side along the flow direction of the air supplied from the outdoor fan 6 shown in FIG. 1, that is, the X direction that is the blowing direction.
  • the windward side heat exchanger 10a is arranged on the windward side in the blowing direction of the air supplied by the outdoor fan 6 shown in FIG. 1, and the leeward side heat exchanger 10b is the blowing direction of the air supplied by the outdoor fan 6. It is located on the lee side.
  • One end of the heat transfer pipe 20 of the windward heat exchanger 10a is connected to the windward header collecting pipe 10c.
  • One end of the heat transfer pipe 20 of the leeward heat exchanger 10b is connected to the leeward header collecting pipe 10d.
  • the other end of the heat transfer tube 20 of the windward heat exchanger 10a and the other end of the heat transfer tube 20 of the leeward heat exchanger 10b are connected to the inter-row connection member 10e.
  • one of the windward header collecting pipe 10c and the leeward header collecting pipe 10d is connected to the one heat transfer pipe 20 of the windward heat exchanger 10a and the leeward heat exchanger 10b.
  • the refrigerant is distributed.
  • the refrigerant distributed to the one heat transfer tube 20 of the upwind heat exchanger 10a or the downwind heat exchanger 10b passes through the inter-row connection member 10e, and the upwind heat exchanger 10a and the downwind heat exchanger. It flows into the other heat transfer tube 20 of 10b.
  • the refrigerant flowing into the other heat transfer pipe 20 of the windward heat exchanger 10a and the leeward heat exchanger 10b merges with the other of the windward header collecting pipe 10c and the leeward header collecting pipe 10d, and is shown in FIG. To the suction port of the compressor 2 or the pressure reducing device 5.
  • the windward heat exchanger 10a and the leeward heat exchanger 10b have the same configuration. Therefore, the windward heat exchanger 10a will be described below as a representative of both.
  • the heat exchange load of the outdoor heat exchanger 10 can be covered by one of the windward side heat exchanger 10a and the leeward side heat exchanger 10b, only one of the windward side heat exchanger 10a and the leeward side heat exchanger 10b can be used to generate the outdoor heat.
  • the exchanger 10 may be configured.
  • the outdoor heat exchanger 10 includes a plurality of heat transfer tubes 20 and a plurality of fins 30.
  • the plurality of heat transfer tubes 20 are arranged so that their tube axes are oriented in the Y direction.
  • the plurality of heat transfer tubes 20 penetrate the plurality of fins 30.
  • the plurality of heat transfer tubes 20 are arranged in parallel in the Z direction.
  • the plurality of heat transfer tubes 20 are arranged at intervals.
  • the heat transfer tube 20 has a flat cross section.
  • the heat transfer tube 20 has a flat shape having a long axis and a short axis in a cross section perpendicular to the tube axis.
  • the major axis of the heat transfer tube 20 is oriented in the X direction.
  • the heat transfer tube 20 is inserted into the fin 30.
  • the fin 30 is a plate-shaped body.
  • the fins 30 are attached to the heat transfer tubes 20 so that the plate surfaces of the fins 30 intersect the tube axis of the heat transfer tubes 20.
  • the fins 30 are formed in a rectangular shape whose longitudinal direction is the direction in which the plurality of heat transfer tubes 20 are arranged in parallel. That is, the longitudinal direction of the fin 30 is along the Z direction, and the width direction orthogonal to the longitudinal direction of the fin 30 is along the X direction.
  • the fin 30 is provided with an insertion portion IP into which the heat transfer tube 20 is inserted.
  • the insertion portion IP is a notch provided in the second end edge 32 of the fin 30.
  • the heat transfer tube 20 is inserted into the insertion portion IP.
  • the fin 30 has a first end edge 31 which is one end edge in the X direction and a second end edge 32 which is the other end edge in the X direction.
  • the first edge 31 is located on the leeward side during the heating operation, and the second edge 32 is located on the leeward side during the heating operation.
  • the heat transfer tube 20 is configured so that the refrigerant flows inside. Heat is exchanged between the air sent to the outdoor heat exchanger 10 and the refrigerant flowing inside the heat transfer tube 20.
  • the heat transfer tube 20 has a first end 20a that is one end in the X direction and a second end 20b that is the other end in the X direction. The first end 20a is located on the windward side during heating operation, and the second end 20b is located on the leeward side during heating operation.
  • An imaginary line connecting the first ends 20a of the plurality of heat transfer tubes 20 is defined as a straight line L1.
  • An imaginary line connecting the second ends 20b of the plurality of heat transfer tubes 20 is defined as a straight line L2.
  • the plurality of fins 30 are installed side by side along the tube axis direction of the heat transfer tube 20.
  • the fins 30 adjacent to each other are arranged with a gap FP therebetween.
  • the outdoor heat exchanger 10 is configured so that air passes through the gap FP.
  • the fins 30 come into contact with the air passing through the gap FP and transfer heat to the refrigerant flowing inside the heat transfer tubes 20.
  • the longitudinal direction of the fin 30 coincides with the gravity direction G.
  • the fin 30 includes a first area 30a and a second area 30b.
  • the first area 30a is an area in which the heat transfer tube 20 is inserted.
  • the first region 30a is a region located between the second edge 32 and the straight line L1 in the X direction.
  • the second region 30b projects from the heat transfer tube 20 in a direction opposite to the air blowing direction in the heating operation.
  • the second region 30b is a region located between the first edge 31 and the straight line L1 in the X direction.
  • the second area 30b is an area where the heat transfer tube 20 is not installed. Therefore, in the second region 30b, the heat transfer tubes 20 do not hinder the flow of water such as dew condensation water and frost melting water flowing from the upper portions of the fins 30.
  • the outdoor fan 6 blows air from the second area 30b toward the first area 30a in the heating operation, and after the defrosting operation of melting the frost that has frosted on the evaporator in the heating operation is performed, the outdoor fan 6 moves from the first area 30a to the first area 30a.
  • the air is blown toward the two areas 30b. That is, in the heating operation, air is blown from the second area 30b toward the first area 30a as indicated by an arrow F1 in FIG. After the defrosting operation is performed, air is blown from the first area 30a toward the second area 30b as indicated by an arrow F2 in FIG.
  • the fin 30 may include the third region 30c.
  • the third region 30c projects from the heat transfer tube 20 in the air blowing direction in the heating operation.
  • the third region 30c is a region located between the second edge 32 and the straight line L2 in the X direction.
  • a cutout that is connected to the insertion portion IP is formed in the third region 30c.
  • the width of the third region 30c is smaller than the width of the second region 30b.
  • FIG. 1 the flow of the refrigerant in the cooling operation is indicated by a dashed arrow, and the flow of the refrigerant in the heating operation is indicated by a solid arrow.
  • the high-temperature and high-pressure vapor refrigerant compressed by the compressor 2 reaches the outdoor heat exchanger 10 via the four-way valve 7 and is condensed by radiating heat to the outdoor air blown by the outdoor fan 6 to generate high pressure. It becomes the liquid refrigerant of.
  • the high-pressure liquid refrigerant is decompressed by expanding in the decompression device 5, and becomes a low-temperature low-pressure gas-liquid two-phase refrigerant.
  • the low-temperature low-pressure gas-liquid two-phase refrigerant reaches the indoor heat exchanger 3 from the decompression device 5 and absorbs heat from the indoor air blown by the indoor fan 4 to be evaporated and become a low-pressure vapor refrigerant.
  • This low-pressure vapor refrigerant returns to the compressor 2 via the four-way valve 7 and is compressed in the compressor 2 to circulate in the refrigerant circuit.
  • the high-temperature and high-pressure vapor refrigerant compressed in the compressor 2 reaches the indoor heat exchanger 3 via the four-way valve 7 and is condensed by radiating heat to the indoor air blown by the indoor fan 4 to generate high pressure. It becomes the liquid refrigerant of.
  • the high-pressure liquid refrigerant is decompressed by expanding in the decompression device 5, and becomes a low-temperature low-pressure gas-liquid two-phase refrigerant.
  • the low-temperature low-pressure gas-liquid two-phase refrigerant reaches the outdoor heat exchanger 10 from the pressure reducing device 5 and absorbs heat from the outdoor air blown by the outdoor fan 6 to evaporate and become a low-pressure vapor refrigerant.
  • the low-pressure vapor refrigerant returns to the compressor 2 via the four-way valve 7 and is compressed in the compressor 2 to circulate in the refrigerant circuit.
  • the temperature of the outdoor heat exchanger 10 falls below 0° C., so that the outdoor heat exchanger 10 is frosted. That is, the water vapor in the outside air is cooled by the outdoor heat exchanger 10 and becomes frost and adheres to the outdoor heat exchanger 10. This frost increases as the heating operation continues, and blocks the air passage of the outdoor heat exchanger 10. If this frost blocks the air passage of the outdoor heat exchanger 10, it causes a decrease in heat exchange performance. Therefore, during the heating operation, the defrosting operation is performed periodically (for example, once every several tens of minutes) to melt the frost in the outdoor heat exchanger 10.
  • the defrosting operation of the refrigeration cycle device 1 will be described.
  • the control device 100 causes the outdoor heat exchanger 10 to be installed. We judge that there is much frost.
  • the refrigeration cycle device 1 performs the defrosting operation based on the determination of the control device 100.
  • Defrosting operation is performed, for example, by the reverse circuit method.
  • the defrosting operation is performed by switching the four-way valve 7 from the heating operation position to the cooling operation position.
  • the refrigerant flow direction, gas-liquid phase change, and heat transfer mode are the same in the defrosting operation and the cooling operation.
  • the frost attached to the outdoor heat exchanger 10 can be melted.
  • a low-temperature low-pressure gas-liquid two-phase refrigerant flows through the indoor heat exchanger 3. It is desirable to stop the indoor fan 4 during the defrosting operation in order to prevent the cold air from blowing into the indoor space.
  • the control device 100 controls the outdoor heat exchange. It is determined that the defrosting of the container 10 has been completed. In the refrigeration cycle device 1, the four-way valve 7 is switched to the heating operation position based on the determination of the control device 100, and the heating operation is restarted.
  • FIG. 6 is a control time chart of the refrigeration cycle device 1 according to the present embodiment.
  • FIG. 6A shows the relationship between each operation and the compressor frequency.
  • FIG. 6B shows the relationship between each operation and the normal rotation and the reverse rotation of the outdoor fan.
  • FIG. 6C shows the relationship between each operation and opening/closing (ON-OFF) of the four-way valve.
  • times t1 to t5 indicate times when each operation is switched.
  • the subsequent control time chart is the same as in FIG.
  • FIG. 7 is a control flowchart of the refrigeration cycle device 1 according to the present embodiment. Note that these flowcharts are repeatedly executed periodically during the heating operation.
  • the heating operation is performed when the control device 100 requests the heating operation. If the outdoor air condition is low, frost may adhere to the outdoor heat exchanger 10 during the heating operation.
  • frost operation frost operation (frosting operation).
  • the control device 100 temporarily switches from the heating operation to the defrost operation (defrosting operation).
  • the operation when switching from the frosting operation to the defrosting operation is defined as the frost defrost switching operation (FD operation).
  • Defrosting operation is performed after FD operation. Generally, while the defrosting operation is being performed, the heat exchanger stops functioning as an evaporator, so the heating operation is also stopped. When the defrosting operation is completed, the control device 100 switches to the frosting operation again. At this time, the operation when switching from the defrosting operation to the frosting operation is defined as a defrost frost switching operation (DF operation).
  • DF operation defrost frost switching operation
  • the control device 100 ends the process. As a result, the frosting operation is continued.
  • the outdoor heat exchanger 10 is blocked by frost to the extent that the heat exchange amount decreases (YES in S11)
  • the FD operation in which the frosting operation is switched to the defrosting operation is performed (S20).
  • the outdoor fan rotation speed (N) decreases to zero.
  • the compressor frequency (CompHz) decreases to the defrosting operation start frequency (defrosting operation start Hz).
  • the defrosting operation start frequency is, for example, a frequency at which the four-way valve 7 can be switched.
  • the control device 100 determines whether or not to shift to the defrosting operation (S21).
  • a reverse circuit system by operation in a refrigerant circuit under cooling conditions is adopted as a defrosting system.
  • the outdoor heat exchanger acts as a condenser
  • the high-temperature and high-pressure refrigerant flows into the heat transfer tube of the heat exchanger and provides a heat quantity for melting frost from the inside of the heat transfer tube.
  • the outdoor fan rotation speed is maintained in the same state as during the frosting operation, the heat of the refrigerant is taken away by the low-temperature air flowing outside the heat transfer tubes of the heat exchanger to sufficiently melt the frost.
  • the outdoor fan rotation speed is set to 0 and the defrosting operation is performed.
  • this description is an example, it is necessary to change the behavior of the actuator when shifting from the frosting operation to the defrosting operation in this way, and a certain time is required for that purpose.
  • the operation within this time is defined as the FD operation.
  • opening/closing of the four-way valve may be switched when switching to the reverse circuit system. At this time, if the pressure difference between the refrigerants is large, it is difficult to switch the opening/closing of the four-way valve, so control is performed to reduce the compressor frequency to the defrosting operation start frequency (defrosting operation start Hz).
  • the control device 100 when the compressor frequency exceeds the defrosting operation start frequency (NO in S21), the control device 100 returns the process to S20. As a result, the FD operation is continued.
  • the compressor frequency is equal to or lower than the defrosting operation start frequency (YES in S21)
  • the FD operation shifts to the defrosting operation (S30).
  • the defrosting operation In the defrosting operation, the amount of heat is provided to the outdoor heat exchanger 10 that has been frosted by, for example, a reverse circuit method. In the defrosting operation, the four-way valve 7 is in the same state as the cooling cycle state. Then, it is determined whether the defrosting by the defrosting operation is completed (S31). Here, for example, when the temperature detected by the temperature sensor 8 (the liquid pipe temperature of the outdoor heat exchanger 10) becomes equal to or higher than the threshold temperature, the control device 100 melts the frost adhering to the outdoor heat exchanger 10. Is determined to have been completed.
  • DF operation As an example of the DF operation for switching from the defrosting operation to the frosting operation, a case where a reverse circuit system is adopted as in the FD operation will be described.
  • control for reducing the compressor frequency to the frosting operation start frequency is performed (S40).
  • control is performed to rotate the outdoor fan 6 in the opposite direction to that during heating operation (S41).
  • the four-way valve 7 When the frosting operation starts, the four-way valve 7 will be in the same state as the heating cycle state.
  • the compressor frequency increases.
  • the outdoor fan rotation speed is changed to normal rotation. In this way, the operation returns to the start state (S60).
  • the refrigeration cycle apparatus of the comparative example is different from refrigeration cycle apparatus 1 according to the present embodiment in that the outdoor fan is not changed to reverse rotation.
  • the water droplets generated in the defrosting operation when the frosting operation is started again, move backward in the air blowing direction along the surface of the flat heat transfer tube, and the flat heat transfer tube Stay at the top or bottom. Therefore, the water generated in the defrosting operation is not properly discharged. Therefore, the drainage performance cannot be improved.
  • the fin 30 includes the second region 30b protruding from the heat transfer tube 20 in the direction opposite to the air blowing direction in the heating operation. Therefore, it is possible to suppress the formation of frost on the second region 30b by making the temperature of the second region 30b higher than the temperature of the first region 30a. Therefore, it is possible to suppress the formation of frost on the portion of the outdoor heat exchanger 10 that functions as an evaporator on the windward side in the air blowing direction during the heating operation.
  • the outdoor fan 6 is configured to blow air from the first area 30a to the second area 30b after the defrosting operation is performed. Therefore, the water droplets generated in the defrosting operation can be pushed out to the second region 30b. Therefore, since the water droplets generated in the defrosting operation are discharged along the second region 30b, the water droplets generated in the defrosting operation can be appropriately discharged.
  • control is performed to reversely rotate the outdoor fan 6 in the DF operation, so drainage is performed in a state in which the heating capacity with the reduced compressor frequency is difficult to be exerted. Therefore, the heating operation can be performed in a state where the compressor frequency is increased and the heating capacity is sufficiently exhibited. Therefore, it is possible to improve the total heating capacity in all operating states.
  • the width of the third region 30c is larger than the width of the second region 30b. Since it is small, it becomes easy to flow the water droplets generated in the defrosting operation to the second region 30b.
  • Embodiment 2 A refrigeration cycle apparatus 1 according to Embodiment 2 of the present invention will be described with reference to FIG. 10.
  • the refrigeration cycle apparatus 1 according to Embodiments 2 to 5 of the present invention has the same configuration, operation, and effect as those of the refrigeration cycle apparatus 1 according to Embodiment 1 of the present invention described above, unless otherwise specified. ing.
  • the reverse rotation of the outdoor fan 6 is started during the DF operation and continued until the compressor frequency reaches the target value.
  • This target value is the compressor frequency when the heating capacity is sufficiently exerted.
  • This target value is, for example, a predetermined frequency equal to or lower than the maximum frequency of the compressor 2.
  • the outdoor fan 6 blows air from the first region 30a to the second region 30b until the frequency of the compressor 2 reaches the target value after the heating operation is started again after the defrosting operation is performed. It is configured.
  • the outdoor fan 6 changes from the first region 30a to the second region 30b until the frequency of the compressor 2 reaches the target value after the heating operation is started again. It is configured to blow air toward. From the time when the heating operation is started again until the frequency of the compressor 2 reaches the target value, since the heating capacity is small, the change in the blowing direction of the outdoor fan 6 is unlikely to affect the heating capacity. Therefore, it is possible to suppress the influence on the heating capacity due to the change in the blowing direction of the outdoor fan 6.
  • Embodiment 3 A refrigeration cycle apparatus 1 according to Embodiment 3 of the present invention will be described with reference to FIG.
  • the reverse rotation of the outdoor fan 6 starts during the DF operation and shifts to the normal rotation during the DF operation.
  • the outdoor fan 6 is configured to blow air from the second area 30b to the first area 30a before the heating operation is started again after the defrosting operation is performed.
  • the outdoor fan 6 is configured to blow air from the second area 30b toward the first area 30a before the heating operation is started again. Therefore, it is possible to suppress frost formation on the outdoor heat exchanger on the leeward side in the blowing direction during the heating operation. That is, if the outdoor fan 6 blows air from the first area 30a toward the second area 30b when the heating operation is started again, the first area arranged on the leeward side in the air blowing direction during the heating operation. Frost is formed on 30a. According to the refrigeration cycle apparatus 1 according to the present embodiment, the outdoor fan 6 blows air from the second region 30b toward the first region 30a before the heating operation is started again, so that the outdoor fan 6 is blown to the first region 30a. It is possible to suppress the formation of frost.
  • Embodiment 4 of the present invention will be described with reference to FIG.
  • the reverse rotation of the outdoor fan 6 is started during the DF operation, and the compressor frequency becomes equal to or lower than the frosting operation start frequency during the DF operation. It will continue even after it becomes.
  • the outdoor fan 6 is directed from the first region 30a to the second region 30b while the state where the frequency of the compressor 2 is equal to or lower than the value when the heating operation is started again (frosting operation start frequency) continues. It is configured to blow air.
  • the outdoor fan 6 keeps the first region 30a while the frequency of the compressor 2 remains below the value when the heating operation is started again. To the second region 30b. Therefore, when the frequency of the compressor 2 reaches the value at which the heating operation is started again, the outdoor fan 6 does not immediately change to the normal rotation but continues to rotate in the reverse direction. When the amount of residual water accumulated in the outdoor heat exchanger 10 is large, the outdoor fan 6 continues to rotate in the reverse direction, so that more residual water can be discharged. By making the shortening time of the defrosting operation longer than the increasing time of the DF operation, it becomes possible to reduce the total non-frosting operation time.
  • refrigeration cycle apparatus 1 according to Embodiment 5 of the present invention is a refrigeration cycle apparatus according to Embodiment 1 in that heat transfer pipe 20 of outdoor heat exchanger 10 is inclined. Different from device 1. As shown in FIGS. 13 and 14, in the refrigeration cycle apparatus 1 according to the present embodiment, the first end portion 20a of the heat transfer tube 20 of the outdoor heat exchanger 10 has a gravity direction G greater than that of the second end portion 20b. It is located below. That is, the heat transfer tube 20 is inclined downward in the gravity direction G from the first region 30a to the second region 30b.
  • the heat transfer tube 20 is inclined toward the second region 30b side, drainage is promoted as compared with the case where the heat transfer tube 20 is horizontally arranged. You can Further, since water drops collect at the lower end of the heat transfer tube 20, the collected water drops can be blown. Therefore, it becomes easy to discharge the water droplets.
  • refrigeration cycle apparatus 1 according to Embodiment 6 of the present invention differs from refrigeration cycle apparatus 1 according to Embodiment 1 in that a refrigeration cycle apparatus 1 is provided with a hot gas circuit.
  • the refrigeration cycle device 1 according to the present embodiment includes a hot gas circuit 40.
  • the defrosting operation is performed by the hot gas circuit system.
  • a high-temperature and high-pressure gas refrigerant (hot gas) is sent to the outdoor heat exchanger 10 during defrosting operation.
  • the valve 41 provided in the hot gas circuit 40 is closed during the heating operation and the cooling operation, and the valve 41 is opened during the defrosting operation.
  • the frost that has frosted on the outdoor heat exchanger 10 is melted by the hot gas that has flowed into the outdoor heat exchanger 10 through the hot gas circuit 40.
  • 1 refrigeration cycle device 2 compressor, 3 indoor heat exchanger, 4 indoor fan, 5 decompression device, 6 outdoor fan, 7 four-way valve, 8 temperature sensor, 10 outdoor heat exchanger, 20 heat transfer tube, 20a first end , 20b second end, 30 fins, 30a first area, 30b second area, 30c third area, 31 first edge, 32 second edge, 40 hot gas circuit, 100 controller.

Abstract

Appareil à cycle frigorifique qui comprend : un compresseur; un condenseur; un dispositif de décompression; un évaporateur; et un ventilateur soufflant. L'évaporateur comprend une ailette (30) et un tuyau de transfert de chaleur (20). L'ailette (30) comprend une première région (30a) dans laquelle le tuyau de transfert de chaleur (20) est inséré, et une seconde région (30b) qui fait saillie à partir du tuyau de transfert de chaleur (20) dans une direction opposée à une direction de soufflage pendant une opération de chauffage. Un ventilateur extérieur est configuré pour souffler de l'air à partir de la seconde région (30b) vers la première région (30a) pendant l'opération de chauffage, et souffler de l'air à partir de la première région (30a) vers la seconde région (30b) après l'exécution d'une opération de dégivrage, pendant l'opération de chauffage, pour faire fondre le givre déposé sur l'évaporateur.
PCT/JP2018/044236 2018-11-30 2018-11-30 Appareil à cycle frigorifique WO2020110301A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PCT/JP2018/044236 WO2020110301A1 (fr) 2018-11-30 2018-11-30 Appareil à cycle frigorifique
JP2020557516A JPWO2020110301A1 (ja) 2018-11-30 2018-11-30 冷凍サイクル装置

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2018/044236 WO2020110301A1 (fr) 2018-11-30 2018-11-30 Appareil à cycle frigorifique

Publications (1)

Publication Number Publication Date
WO2020110301A1 true WO2020110301A1 (fr) 2020-06-04

Family

ID=70853308

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2018/044236 WO2020110301A1 (fr) 2018-11-30 2018-11-30 Appareil à cycle frigorifique

Country Status (2)

Country Link
JP (1) JPWO2020110301A1 (fr)
WO (1) WO2020110301A1 (fr)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59157460A (ja) * 1983-02-22 1984-09-06 ダイキン工業株式会社 ヒ−トポンプ式空気調和機
JPS60101462A (ja) * 1983-11-09 1985-06-05 松下電器産業株式会社 蒸発器
JPS6089568U (ja) * 1983-11-26 1985-06-19 富士電機株式会社 冷凍装置
JPH04177091A (ja) * 1990-11-08 1992-06-24 Toshiba Corp 熱交換器
JPH06123587A (ja) * 1992-10-12 1994-05-06 Toshiba Corp 熱交換器
JP2004176980A (ja) * 2002-11-26 2004-06-24 Daikin Ind Ltd 冷凍装置
JP2011220554A (ja) * 2010-04-05 2011-11-04 Sumitomo Light Metal Ind Ltd フィン・アンド・チューブ型熱交換器用伝熱管及びそれを用いたフィン・アンド・チューブ型熱交換器並びにその製造方法

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58208547A (ja) * 1982-05-29 1983-12-05 三菱重工業株式会社 ヒ−トポンプのデフロスト運転方法
JPS63183335A (ja) * 1987-01-26 1988-07-28 Hitachi Ltd 空気調和機
JPS63290370A (ja) * 1987-05-21 1988-11-28 ダイキン工業株式会社 空気調和装置の除霜運転制御装置
JP2013217506A (ja) * 2012-04-04 2013-10-24 Mitsubishi Electric Corp 冷凍サイクル装置
JP6019386B2 (ja) * 2012-04-19 2016-11-02 パナソニックＩｐマネジメント株式会社 冷蔵庫
JP2015218966A (ja) * 2014-05-19 2015-12-07 ホシザキ電機株式会社 冷却装置
WO2017126019A1 (fr) * 2016-01-19 2017-07-27 三菱電機株式会社 Échangeur de chaleur
JP6701371B2 (ja) * 2016-10-28 2020-05-27 三菱電機株式会社 熱交換器及び冷凍サイクル装置

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59157460A (ja) * 1983-02-22 1984-09-06 ダイキン工業株式会社 ヒ−トポンプ式空気調和機
JPS60101462A (ja) * 1983-11-09 1985-06-05 松下電器産業株式会社 蒸発器
JPS6089568U (ja) * 1983-11-26 1985-06-19 富士電機株式会社 冷凍装置
JPH04177091A (ja) * 1990-11-08 1992-06-24 Toshiba Corp 熱交換器
JPH06123587A (ja) * 1992-10-12 1994-05-06 Toshiba Corp 熱交換器
JP2004176980A (ja) * 2002-11-26 2004-06-24 Daikin Ind Ltd 冷凍装置
JP2011220554A (ja) * 2010-04-05 2011-11-04 Sumitomo Light Metal Ind Ltd フィン・アンド・チューブ型熱交換器用伝熱管及びそれを用いたフィン・アンド・チューブ型熱交換器並びにその製造方法

Also Published As

Publication number Publication date
JPWO2020110301A1 (ja) 2021-05-20

Similar Documents

Publication Publication Date Title
US9958194B2 (en) Refrigeration cycle apparatus with a heating unit for melting frost occurring in a heat exchanger
CN109312971B (zh) 制冷循环装置
JP4874223B2 (ja) 空気調和機
JP2010139097A (ja) 空気調和機
US20110113820A1 (en) Heat transfer tube for heat exchanger, heat exchanger, refrigerating cycle apparatus, and air conditioner
US11920841B2 (en) Air-conditioning apparatus
WO2018078800A1 (fr) Échangeur thermique et dispositif à cycle de réfrigération
JP2019184207A (ja) 空気調和装置
EP3783280B1 (fr) Unité extérieure et appareil à cycle de réfrigération la comprenant
WO2019224944A1 (fr) Climatiseur
JP6692495B2 (ja) 熱交換器及び冷凍サイクル装置
US20220049869A1 (en) Air-conditioning apparatus
WO2020110301A1 (fr) Appareil à cycle frigorifique
WO2018189830A1 (fr) Dispositif à cycle de réfrigération
WO2020235030A1 (fr) Échangeur de chaleur et dispositif à cycle frigorifique faisant appel audit échangeur
CN211290633U (zh) 热交换器以及使用该热交换器的制冷循环装置
KR100505236B1 (ko) 공기조화기
WO2020194677A1 (fr) Dispositif à cycle frigorifique
WO2020202560A1 (fr) Dispositif de climatisation
WO2019106755A1 (fr) Climatiseur
WO2018011888A1 (fr) Échangeur de chaleur et dispositif à cycle de réfrigération
JP2011232008A (ja) 冷凍装置

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 18941818

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2020557516

Country of ref document: JP

Kind code of ref document: A

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 18941818

Country of ref document: EP

Kind code of ref document: A1