WO2019176089A1 - Échangeur de chaleur et dispositif à cycle frigorifique - Google Patents

Échangeur de chaleur et dispositif à cycle frigorifique Download PDF

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Publication number
WO2019176089A1
WO2019176089A1 PCT/JP2018/010453 JP2018010453W WO2019176089A1 WO 2019176089 A1 WO2019176089 A1 WO 2019176089A1 JP 2018010453 W JP2018010453 W JP 2018010453W WO 2019176089 A1 WO2019176089 A1 WO 2019176089A1
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WO
WIPO (PCT)
Prior art keywords
heat exchange
exchange tube
header
chamber
refrigerant
Prior art date
Application number
PCT/JP2018/010453
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English (en)
Japanese (ja)
Inventor
崇史 畠田
司 高山
亜由美 小野寺
亮輔 是澤
聖史 原瀬
Original Assignee
東芝キヤリア株式会社
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 東芝キヤリア株式会社 filed Critical 東芝キヤリア株式会社
Priority to PCT/JP2018/010453 priority Critical patent/WO2019176089A1/fr
Priority to JP2020506080A priority patent/JP6906101B2/ja
Priority to CN201880084931.0A priority patent/CN111527356B/zh
Publication of WO2019176089A1 publication Critical patent/WO2019176089A1/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
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • 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

Definitions

  • Embodiments of the present invention relate to a heat exchanger and a refrigeration cycle apparatus.
  • a heat exchanger that exchanges heat between the refrigerant and the outside air is used.
  • frost adheres (frosts) to the heat exchanger.
  • the refrigeration cycle apparatus stops the normal operation and performs the defrosting operation.
  • a heat exchanger that can complete defrosting in a short defrosting operation is required.
  • the problem to be solved by the present invention is to provide a heat exchanger and a refrigeration cycle apparatus capable of completing defrosting in a short defrosting operation.
  • the heat exchanger includes a first header and a second header, and a plurality of heat exchange tubes.
  • the first header and the second header are formed in a cylindrical shape, and are arranged side by side so as to be separated from each other.
  • the plurality of heat exchange tubes are arranged at intervals in the central axis direction of the first header and the second header, and both end portions open to the inside of the first header and the second header.
  • the plurality of heat exchange tubes have a first heat exchange tube and a second heat exchange tube.
  • a gas-liquid two-phase refrigerant with a large liquid phase component flows.
  • the second heat exchange tube communicates with the first heat exchange tube, and a gas-liquid two-phase refrigerant with a large gas phase component flows.
  • the second heat exchange tube has an upper second heat exchange tube and a lower second heat exchange tube.
  • the upper second heat exchange tube is disposed above the first heat exchange tube.
  • the lower second heat exchange tube is disposed below the first heat exchange tube.
  • FIG. 4 is a partial cross-sectional view taken along line F4-F4 of FIG.
  • the schematic block diagram of the heat exchanger of 1st Embodiment The schematic block diagram of the heat exchanger of the modification of 1st Embodiment.
  • the flowchart of a defrost method The schematic block diagram of the heat exchanger of 2nd Embodiment.
  • the X direction, the Y direction, and the Z direction are defined as follows.
  • the Z direction is the central axis direction (extending direction) of the first header and the second header.
  • the Z direction is a vertical direction
  • the + Z direction is an upward direction.
  • the X direction is the central axis direction (extending direction) of the heat exchange tube.
  • the X direction is a horizontal direction
  • the + X direction is a direction from the first header to the second header.
  • the Y direction is a direction perpendicular to the X direction and the Z direction.
  • FIG. 1 is a schematic configuration diagram of a refrigeration cycle apparatus.
  • the refrigeration cycle apparatus 1 includes a compressor 2, a four-way valve 3, an outdoor heat exchanger (heat exchanger) 4, an expansion device 5, an indoor heat exchanger 6, and a control unit. 9 and.
  • the components of the refrigeration cycle apparatus 1 are sequentially connected by a pipe 7.
  • the flow direction of the refrigerant during the heating operation is indicated by a broken line arrow
  • the flow direction of the refrigerant during the defrosting (cooling) operation is indicated by a solid line arrow.
  • the compressor 2 has a compressor body 2A and an accumulator 2B.
  • the compressor main body 2A compresses the low-pressure gas refrigerant taken into the inside into a high-temperature / high-pressure gas refrigerant.
  • the accumulator 2B separates the gas-liquid two-phase refrigerant and supplies the gas refrigerant to the compressor body 2A.
  • the four-way valve 3 reverses the refrigerant flow direction and switches between heating operation and defrosting operation.
  • the refrigerant flows in the order of the compressor 2, the four-way valve 3, the indoor heat exchanger 6, the expansion device 5, and the outdoor heat exchanger 4.
  • the refrigeration cycle apparatus 1 causes the indoor heat exchanger 6 to function as a condenser, causes the outdoor heat exchanger 4 to function as an evaporator, and heats the room.
  • the refrigerant flows in the order of the compressor 2, the four-way valve 3, the outdoor heat exchanger 4, the expansion device 5, and the indoor heat exchanger 6.
  • the refrigeration cycle apparatus 1 causes the outdoor heat exchanger 4 to function as a condenser, causes the indoor heat exchanger 6 to function as an evaporator, and defrosts the outdoor heat exchanger 4.
  • the condenser converts the high-temperature and high-pressure gaseous refrigerant discharged from the compressor 2 to the outside air and condenses it into a high-pressure liquid refrigerant.
  • the evaporator converts the low-temperature and low-pressure liquid refrigerant sent from the expansion device 5 into a low-pressure gas refrigerant by absorbing heat from outside air and vaporizing it.
  • a blower fan 4 a is provided in the vicinity of the outdoor heat exchanger 4. The blower fan 4 a blows outside air to the outdoor heat exchanger 4.
  • the expansion device 5 lowers the pressure of the high-pressure liquid refrigerant sent from the condenser to make a low-temperature / low-pressure liquid refrigerant.
  • the control unit 9 controls operations of the compressor 2, the four-way valve 3, the expansion device 5, and the like.
  • the refrigerant that is the working fluid circulates while changing phase between the gas refrigerant and the liquid refrigerant, dissipates heat in the process of phase change from the gas refrigerant to the liquid refrigerant, and the gas from the liquid refrigerant It absorbs heat in the process of phase change to the refrigerant. And heating, defrosting, etc. are performed using these heat dissipation and heat absorption.
  • FIG. 2 is a front view of the heat exchanger according to the first embodiment.
  • FIG. 3 is a partial perspective view of the heat exchanger according to the first embodiment.
  • the heat exchanger 4 of the embodiment is used as the outdoor heat exchanger 4 of the refrigeration cycle apparatus 1.
  • the heat exchanger 4 of the embodiment may be used as the indoor heat exchanger 6 of the refrigeration cycle apparatus 1.
  • the case where the heat exchanger 4 of the embodiment is used as the outdoor heat exchanger 4 of the refrigeration cycle apparatus 1 will be described as an example.
  • the heat exchanger 4 includes a first header 10, a second header 20, a heat exchange tube 30, and fins 40.
  • the first header 10 is formed of a material having high thermal conductivity and low specific gravity, such as aluminum or an aluminum alloy.
  • the first header 10 is formed in a cylindrical shape, for example, a cylindrical shape having a circular cross section. Both end portions in the Z direction of the first header 10 are closed. A plurality of through holes into which the heat exchange tubes 30 are inserted are formed on the outer peripheral surface of the first header 10.
  • the second header 20 is formed in the same manner as the first header 10.
  • the first header 10 and the second header 20 are arranged side by side in the X direction so as to be separated from each other.
  • the heat exchange tube 30 is formed of a material having high thermal conductivity and low specific gravity, such as aluminum or aluminum alloy. As shown in FIG. 3, the heat exchange tube 30 is formed in a flat tubular shape. That is, the heat exchange tube 30 has a predetermined width in the Y direction, is thin in the Z direction, and extends long in the X direction.
  • FIG. 4 is a partial cross-sectional view taken along line F4-F4 of FIG.
  • the outer shape of the heat exchange tube 30 is formed in an oval shape.
  • a plurality of refrigerant flow paths 34 are formed side by side in the Y direction. Adjacent refrigerant flow paths 34 are partitioned by flow path walls 35 parallel to the XZ plane. The plurality of refrigerant flow paths 34 penetrate the heat exchange tube 30 in the X direction.
  • a plurality of heat exchange tubes 30 are arranged at intervals in the Z direction. Both ends of the heat exchange tube 30 are inserted into through holes formed in the outer peripheral surfaces of the first header 10 and the second header 20. Thereby, both ends of the refrigerant flow path 34 of the heat exchange tube 30 are opened inside the first header 10 and the second header 20. The space between the first header 10 and the second header 20 and the heat exchange tube 30 is sealed and fixed by brazing or the like.
  • the fin 40 is formed of a material having high thermal conductivity and low specific gravity, such as aluminum or aluminum alloy. As shown in FIGS. 2 and 3, the fin 40 is a plate fin formed in a flat plate shape. The fin 40 is disposed in parallel with the YZ plane. The length of the fin 40 in the Z direction is equal to or slightly shorter than the length of the first header 10 and the second header 20 in the Z direction.
  • the width of the fin 40 in the Y direction is larger than the width of the heat exchange tube 30 in the Y direction.
  • a notch 43 is formed from the + Y direction end of the fin 40 to the ⁇ Y direction.
  • the heat exchange tube 30 is inserted into the notch 43.
  • the heat exchange tubes 30 and the fins 40 are fixed by brazing or the like.
  • the plurality of fins 40 are arranged at intervals in the X direction.
  • the heat exchanger 4 distributes the outside air to the outside air flow path by the blower fan 4a (see FIG. 1).
  • the heat exchanger 4 exchanges heat between the outside air flowing through the outside air flow path and the refrigerant flowing through the refrigerant flow path 34.
  • Heat exchange is performed indirectly via the heat exchange tubes 30 and the fins 40.
  • the fins 40 may be provided with irregularities. The unevenness generates turbulent flow in the outside air flowing through the outside air flow path, and improves heat exchange efficiency.
  • the fins 40 in the embodiment are plate fins, but may be corrugated fins.
  • the corrugated fin is formed in a corrugated shape and is disposed between adjacent heat exchange tubes 30.
  • FIG. 5 is a schematic configuration diagram of the heat exchanger 4 of the first embodiment.
  • the heat exchange tube 30 is represented by a box.
  • One box in FIG. 5 includes a plurality of heat exchange tubes 30 that are arranged next to each other and have similar functions.
  • the first header 10 has a plurality of partition members.
  • the partition member is arranged in parallel with the XY plane and partitions the inside of the first header 10 in the Z direction.
  • the plurality of partition members divide the inside of the first header 10 into a plurality of chambers.
  • the plurality of partition members include an upper partition member 15H, a lower partition member 15L, and an intermediate partition member 15s.
  • the upper partition member 15H is disposed above (+ Z direction), and the lower partition member 15L is disposed below ( ⁇ Z direction).
  • a first chamber 11 is formed between the upper partition member 15H and the lower partition member 15L.
  • a second chamber 12 is formed between the upper partition member 15 ⁇ / b> H and the upper end portion of the first header 10.
  • a lowermost second chamber 12z is formed between the lower partition member 15L and the lower end portion of the first header 10.
  • the intermediate partition member 15s is disposed in the first chamber 11 between the upper partition member 15H and the lower partition member 15L.
  • a plurality of intermediate partition members 15s divide the first chamber 11 into a plurality of first small chambers 11a and 11z.
  • four intermediate partition members 15s divide the first chamber 11 into five first small chambers 11a and 11z.
  • the heights in the Z direction of the five first small chambers 11a and 11z are equal.
  • the second header 20 has a plurality of partition members.
  • the plurality of partition members include an upper partition member 25H, a lower partition member 25L, and an intermediate partition member 25s.
  • the upper partition member 25H is disposed at the same height as the upper partition member 15H of the first header 10.
  • the lower partition member 25L is disposed above the lower partition member 15L of the first header 10.
  • the lower partition member 25L is disposed at the same height as the intermediate partition member 15s disposed at the lowermost portion of the first chamber 11 of the first header 10.
  • a first chamber 21 is formed between the upper partition member 25H and the lower partition member 25L.
  • a second chamber 22 is formed between the upper partition member 25 ⁇ / b> H and the upper end portion of the second header 20.
  • a lowermost chamber 20z is formed between the lower partition member 25L and the lower end portion of the second header 20.
  • the intermediate partition member 25s is disposed in the first chamber 21 between the upper partition member 25H and the lower partition member 25L.
  • a plurality of intermediate partition members 25s divide the first chamber 21 into a plurality of first small chambers 21a.
  • three intermediate partition members 25s divide the first chamber 21 into four first small chambers 21a.
  • the heights in the Z direction of the four first small chambers 21a are equal.
  • the height of the first small chambers 11a and 11z of the first header 10 is equal to the height of the first small chamber 21a of the second header 20.
  • the intermediate partition member 25s is also disposed in the second chamber 22 between the upper partition member 25H and the upper end portion of the second header 20.
  • a plurality of intermediate partition members 25s divide the second chamber 22 into a plurality of second small chambers 22a.
  • three intermediate partition members 25s divide the second chamber 22 into four second small chambers 22a.
  • the heights in the Z direction of the four second small chambers 22a are equal.
  • the height of the second small chamber 22a is larger than the height of the first small chamber 21a.
  • the heat exchange tube 30 includes a first heat exchange tube 31 and a second heat exchange tube 32.
  • the first heat exchange tube 31 is disposed closer to the lower side than the center in the Z direction of the heat exchanger 4.
  • the second heat exchange tube 32 includes an upper second heat exchange tube 32u and a lower second heat exchange tube 32z.
  • the upper second heat exchange tube 32 u is disposed above the first heat exchange tube 31.
  • the lower second heat exchange tube 32 z is disposed below the first heat exchange tube 31 and is disposed at the lowermost position of the plurality of heat exchange tubes 30.
  • the first end of the first heat exchange tube 31 in the ⁇ X direction opens into the first chamber 11 of the first header 10.
  • a plurality of first heat exchange tubes 31 are opened in the plurality of first small chambers 11a and 11z formed in the first chamber 11, respectively.
  • the same number of first heat exchange tubes 31 are opened to the plurality of first small chambers 11a and 11z, respectively.
  • the lowermost first heat exchange tube 31z opens in the lowermost first small chamber 11z arranged at the lowermost position among the plurality of first small chambers 11a, 11z.
  • the lowermost first heat exchange tube 31 z is disposed at the lowermost part of the first heat exchange tube 31. Therefore, the lowermost first heat exchange tube 31z is closest to the lower second heat exchange tube 32z.
  • the second end portion in the + X direction of the first heat exchange tube 31 opens into the first chamber 21 or the lowermost chamber 20z of the second header 20.
  • the lowermost first heat exchange tube 31z opens into the lowermost chamber 20z.
  • An upper first heat exchange tube 31 u disposed above the lowermost first heat exchange tube 31 z opens into the first chamber 21.
  • a plurality of upper first heat exchange tubes 31u are opened in the plurality of first small chambers 21a formed in the first chamber 21, respectively.
  • the number of upper first heat exchange tubes 31u opened in the first small chamber 11a of the first header 10 and the number of upper first heat exchange tubes 31u opened in the first small chamber 21a of the second header 20 are the same.
  • a first end portion in the ⁇ X direction of the upper second heat exchange tube 32 u opens into the second chamber 12 of the first header 10.
  • a first end portion in the ⁇ X direction of the lower second heat exchange tube 32z opens into the lowermost second chamber 12z of the first header 10.
  • a second end portion in the + X direction of the upper second heat exchange tube 32 u opens into the second chamber 22 of the second header 20.
  • a plurality of second upper heat exchange tubes 32u are opened in the plurality of second small chambers 22a formed in the second chamber 22, respectively.
  • the same number of upper second heat exchange tubes 32 u are opened in each of the four second small chambers 22 a.
  • the number of upper second heat exchange tubes 32u that open to the second small chamber 22a is greater than the number of upper first heat exchange tubes 31u that open to the first small chamber 21a.
  • a second end portion in the + X direction of the lower second heat exchange tube 32z opens into the lowermost chamber 20z of the second header 20.
  • the number of lower second heat exchange tubes 32z is equal to or greater than the number of lowermost first heat exchange tubes 31z.
  • the first header 10 includes a first refrigerant port 17, a second refrigerant port 18, and a temperature sensor 14.
  • the first refrigerant port 17 includes a first refrigerant port 17a formed in each of the plurality of first small chambers 11a constituting the first chamber 11, and a lowermost first refrigerant port 17z formed in the lowermost first small chamber 11z. It is configured.
  • the first refrigerant port 17a and the lowermost first refrigerant port 17z constituting the first refrigerant port 17 of the heat exchanger 4 are joined by a connection pipe 17b and connected to the same constituent member of the refrigeration cycle apparatus 1. In the example of FIG. 1, the first refrigerant port 17 of the outdoor heat exchanger 4 is connected to the expansion device 5.
  • the second refrigerant port 18 includes a second refrigerant port 18a formed above (upper half) of the second chamber 12, and a lowermost second refrigerant port 18z formed in the lowermost second chamber 12z. Yes.
  • the second refrigerant port 18a and the lowermost second refrigerant port 18z constituting the second refrigerant port 18 of the heat exchanger 4 are joined by a connection pipe 18b and connected to the same component of the refrigeration cycle apparatus 1.
  • the second refrigerant port 18 of the outdoor heat exchanger 4 is connected to the four-way valve 3.
  • the temperature sensor 14 is connected to the lowermost first refrigerant port 17z constituting the first refrigerant port 17.
  • the temperature sensor 14 outputs a signal corresponding to the temperature of the refrigerant flowing through the first refrigerant port 17 to the control unit 9 of the refrigeration cycle apparatus 1.
  • the controller 9 detects the temperature of the refrigerant flowing through the first refrigerant port 17 based on the signal input from the temperature sensor 14.
  • the second header 20 has a connection channel 26.
  • the connection channel 26 connects between the first chamber 21 and the second chamber 22.
  • Connection flow paths 26 a are respectively formed between the plurality of first small chambers 21 a formed in the first chamber 21 and the plurality of second small chambers 22 a formed in the second chamber 22.
  • the connection channel 26 a connects the nth (n is a natural number) first small chamber 21 a from above the first chamber 21 and the nth second small chamber 22 a from below the second chamber 22. To do. Thereby, the intersection of the plurality of connection flow paths 26 is avoided, and the layout is simplified.
  • the connection channel 26a may connect the first small chamber 21a and the second small chamber 22a in a combination other than the above.
  • FIG. 6 is a schematic configuration diagram of a heat exchanger 104 according to a modification of the first embodiment.
  • the heat exchanger 104 does not have the intermediate partition members 15 s and 25 s in the first header 10 and the second header 20. That is, the first chamber 11 of the first header 10 is not divided into a plurality of first small chambers. The first chamber 21 of the second header 20 is not divided into a plurality of first small chambers. The second chamber 22 of the second header 20 is not divided into a plurality of second small chambers.
  • the first refrigerant port 17 is formed below the first chamber 11 of the first header 10.
  • the connection channel 26 connects the upper side of the first chamber 21 of the second header 20 and the lower side of the second chamber 22.
  • a refrigerant flow path in the heat exchanger 4 of the first embodiment will be described. As described above, in FIG. 5, the flow direction of the refrigerant during the heating operation is indicated by a broken line arrow, and the flow direction of the refrigerant during the defrosting operation is indicated by a solid line arrow.
  • a refrigerant flow path when the refrigeration cycle apparatus 1 performs the heating operation will be described.
  • the outdoor heat exchanger 4 functions as an evaporator.
  • the liquid refrigerant that has flowed out of the expansion device 5 is evenly distributed by a refrigerant distribution mechanism (not shown), and configures the first refrigerant port 17 of the heat exchanger 4 shown in FIG. 5 via the connection pipe 17b. It flows into the first refrigerant port 17a and the lowermost first refrigerant port 17z.
  • the refrigerant flows from the first refrigerant port 17a into the first small chamber 11a constituting the first chamber 11 of the first header 10, and flows from the lowermost first refrigerant port 17z into the lowermost first small chamber 11z.
  • the refrigerant flows from the first small chamber 11a into the upper first heat exchange tube 31u, and flows from the lowermost first small chamber 11z into the lowermost first heat exchange tube 31z.
  • the refrigerant absorbs heat from the outside air.
  • the liquid refrigerant changes to a gas-liquid two-phase refrigerant with a large amount of liquid phase components. That is, a gas-liquid two-phase refrigerant with a large liquid phase component flows through the first heat exchange tube 31.
  • the refrigerant flows from the upper first heat exchange tube 31u into the first small chamber 21a, and flows from the lowermost first heat exchange tube 31z into the lowermost chamber 20z.
  • the refrigerant flows from the first small chamber 21a through the connection channel 26a and flows into the second small chamber 22a.
  • the refrigerant flows from the second small chamber 22a into the upper second heat exchange tube 32u, and flows from the lowermost chamber 20z into the lower second heat exchange tube 32z.
  • the refrigerant absorbs heat from the outside air.
  • the gas-liquid two-phase refrigerant having a large liquid phase component is changed to a gas-liquid two-phase refrigerant having a large gas phase component. That is, a gas-liquid two-phase refrigerant with a large amount of gas phase components flows through the second heat exchange tube 32.
  • the refrigerant flows into the second chamber 12 from the upper second heat exchange tube 32u, and flows into the lowermost second chamber 12z from the lower second heat exchange tube 32z.
  • the refrigerant flows out of the heat exchanger 4 from the second refrigerant port 18a and the lowermost second refrigerant port 18z.
  • the gaseous refrigerant flowing out from the outdoor heat exchanger 4 shown in FIG. 1 flows into the compressor 2 through the four-way valve 3.
  • the refrigerant includes the first small chamber 11a of the first header 10, the upper first heat exchange tube 31u, the first small chamber 21a of the second header, the connection channel 26a, the second small chamber 22a of the second header, and the upper portion.
  • the second heat exchange tube 32u is circulated.
  • the refrigerant is the lowermost first small chamber 11z of the first header 10, the lowermost first heat exchange tube 31z, the lowermost chamber 20z of the second header, the lower second heat exchange tube 32z, and the lowermost of the first header 10. Circulates through the second chamber 12z.
  • These refrigerant distribution paths constitute a module.
  • a plurality of modules are arranged in parallel.
  • a refrigerant flow path when the refrigeration cycle apparatus 1 performs a defrosting operation will be described.
  • the refrigerant in the case of performing the defrosting operation circulates opposite to the case of performing the heating operation.
  • the outdoor heat exchanger 4 functions as a condenser.
  • the gaseous refrigerant flowing out from the compressor 2 through the four-way valve flows into the second refrigerant port 18 of the heat exchanger 4 shown in FIG.
  • the refrigerant flows into the second chamber 12 and the lowermost second chamber 12z of the first header 10 from the second refrigerant ports 18a and 18z.
  • the refrigerant flows into the second heat exchange tube 32 from the second chamber 12 and the lowermost second chamber 12z.
  • the refrigerant radiates heat to the outside air.
  • a gaseous refrigerant changes to a gas-liquid two-phase refrigerant with many gaseous phase components. That is, a gas-liquid two-phase refrigerant with a large amount of gas phase components flows through the second heat exchange tube 32.
  • the refrigerant flows from the second heat exchange tube 32 into the second chamber 22 and the lowermost chamber 20z of the second header 20.
  • the refrigerant flows from the second chamber 22 through the connection channel 26 and flows into the first chamber 21.
  • the refrigerant flows into the first heat exchange tube 31 from the first chamber 21 and the lowermost chamber 20z of the second header 20.
  • the refrigerant radiates heat to the outside air.
  • the gas-liquid two-phase refrigerant with a large amount of gas phase components changes to a gas-liquid two-phase refrigerant with a large amount of liquid phase components. That is, a gas-liquid two-phase refrigerant with a large liquid phase component flows through the first heat exchange tube 31.
  • the refrigerant flows from the first heat exchange tube 31 into the first chamber 11 of the first header 10.
  • the refrigerant flows from the first chamber 11 into the first refrigerant port 17.
  • the refrigerant flows out from the first refrigerant port 17 to the outside of the heat exchanger 4.
  • the liquid refrigerant flowing out from the outdoor heat exchanger 4 shown in FIG. 1 flows into the expansion device 5.
  • the gas-liquid two-phase refrigerant having a large liquid phase component flows through the first heat exchange tube 31, and the gas phase component of the second heat exchange tube 32 is supplied.
  • Many gas-liquid two-phase refrigerants circulate. That is, the gas-liquid two-phase refrigerant having more liquid phase components flows through the first heat exchange tube 31 than the second heat exchange tube 32.
  • a gas-liquid two-phase refrigerant having more gas phase components than the first heat exchange tube 31 flows.
  • a gas-liquid two-phase refrigerant with a large amount of gas phase components flows into the second heat exchange tube 32.
  • the refrigerant radiates heat to the outside air, so that the liquid phase component of the gas-liquid two-phase refrigerant increases.
  • the upper second heat exchange tube 32 u occupying most of the second heat exchange tube 32 is disposed above the first heat exchange tube 31. Therefore, the liquid phase component of the refrigerant flows from the upper second heat exchange tube 32u to the first heat exchange tube 31 according to gravity. Thereby, the refrigerant
  • FIG. 7 is a flowchart of the defrosting method.
  • the control unit 9 of the refrigeration cycle apparatus 1 performs a heating operation (S02).
  • the controller 9 switches the four-way valve 3 and causes the refrigerant to flow in the order of the compressor 2, the four-way valve 3, the indoor heat exchanger 6, the expansion device 5, and the outdoor heat exchanger 4.
  • the outdoor heat exchanger 4 functions as an evaporator.
  • the refrigerant flowing through the heat exchange tube 30 absorbs heat from the outside air flowing through the outside air flow path. Therefore, condensed water adheres to the fins 40 and the heat exchange tubes 30 constituting the outside air flow path.
  • the condensed water flows downward through the plate-like fins 40 and stays at the lowermost part of the heat exchanger 4.
  • the condensed water freezes and frost adheres. Therefore, frost tends to adhere to the lowermost part of the heat exchanger 4.
  • the control unit 9 reduces the temperature of the refrigerant by narrowing the expansion device 5.
  • the refrigerant temperature decreases to less than 0 ° C.
  • the controller 9 determines whether the refrigerant temperature Te detected based on the signal from the temperature sensor 14 is less than 0 ° C. (S04).
  • the control unit 9 substitutes Te for Te0 (S06).
  • the controller 9 determines whether or not the difference ⁇ Te between the refrigerant temperature Te0 detected last time and the newly detected refrigerant temperature Te exceeds a predetermined value ⁇ (S08).
  • the predetermined value ⁇ is set to 3 to 10 ° C., for example.
  • the difference ⁇ Te exceeds the predetermined value ⁇
  • the refrigerant temperature is rapidly decreased.
  • the control unit 9 sharply decreases the refrigerant temperature.
  • the control unit 9 determines that the heat exchanger 4 has been frosted (S10). At this time, the control unit 9 stops the operation of the compressor 2.
  • the controller 9 stops the operation of the blower fan 4a of the heat exchanger 4.
  • the control unit 9 performs a defrosting operation (S12).
  • the control unit 9 switches the four-way valve and causes the refrigerant to flow in the order of the compressor 2, the four-way valve 3, the outdoor heat exchanger 4, the expansion device 5, and the indoor heat exchanger 6.
  • the control unit 9 starts the operation of the compressor 2.
  • the controller 9 does not operate the blower fan 4a.
  • the high-temperature gaseous refrigerant that has flowed out of the compressor 2 flows into the second heat exchange tube 32 of the heat exchanger 4.
  • the gaseous refrigerant radiates heat in the process of flowing through the second heat exchange tube 32.
  • the heat exchanger 4 of the embodiment includes a lower second heat exchange tube 32z as the second heat exchange tube 32 in addition to the upper second heat exchange tube 32u. In the process in which the high-temperature gaseous refrigerant flows through the lower second heat exchange tube 32z, the frost adhering to the lowermost part of the heat exchanger 4 is melted.
  • the refrigerant that has flowed into the lower second heat exchange tube 32z flows from the lowermost chamber 20z into the lowermost first heat exchange tube 31z, and flows out from the lowermost first refrigerant port 17z.
  • the controller 9 determines whether the refrigerant temperature exceeds the predetermined value ⁇ (S14).
  • the predetermined value ⁇ is set to 3 to 15 ° C., for example.
  • the temperature sensor 14 is connected to the lowermost first refrigerant port 17 z below the first chamber 11 of the first header 10. Therefore, the control unit 9 can accurately determine the completion of defrosting at the lowermost part of the heat exchanger 4.
  • the control unit 9 determines that the defrosting has been completed (S16). At this time, the control unit 9 stops the operation of the compressor 2.
  • the controller 9 resumes the heating operation (S18). At this time, the controller 9 switches the four-way valve 3 and causes the refrigerant to flow in the order of the compressor 2, the four-way valve 3, the indoor heat exchanger 6, the expansion device 5, and the outdoor heat exchanger 4. Thus, the process of the defrosting method is completed.
  • the heat exchanger 4 of the embodiment includes the first header 10 and the second header 20 and the plurality of heat exchange tubes 30.
  • the first header 10 and the second header 20 are formed in a cylindrical shape, and are arranged side by side in the X direction so as to be separated from each other.
  • the plurality of heat exchange tubes 30 are arranged at intervals in the central axis direction (Z direction) of the first header 10 and the second header 20, and both end portions open to the inside of the first header 10 and the second header 20. .
  • the plurality of heat exchange tubes 30 have a first heat exchange tube 31 and a second heat exchange tube 32. In the first heat exchange tube 31, a gas-liquid two-phase refrigerant with a large amount of liquid phase components flows.
  • the second heat exchange tube 32 communicates with the first heat exchange tube 31 and a gas-liquid two-phase refrigerant with a large amount of gas phase components flows.
  • the second heat exchange tube 32 has an upper second heat exchange tube 32u and a lower second heat exchange tube 32z.
  • the upper second heat exchange tube 32 u is disposed above the first heat exchange tube 31.
  • the lower second heat exchange tube 32 z is disposed below the first heat exchange tube 31.
  • the second heat exchange tube 32 has a lower second heat exchange tube 32z. Therefore, the heat exchanger 4 can efficiently defrost the frost adhering to the lowermost part. Therefore, defrosting can be completed in a short defrosting operation.
  • the first header 10 and the second header 20 have a plurality of chambers divided in the Z direction.
  • the second header 20 has a first chamber 21, a second chamber 22, and a lowermost chamber 20z as a plurality of chambers.
  • an upper first heat exchange tube 31u which is a part of the first heat exchange tube 31, is opened.
  • the second chamber 22 communicates with the first chamber 21, and the upper second heat exchange tube 32u is opened.
  • both the lower second heat exchange tube 32z and the lowermost first heat exchange tube 31z which is the first heat exchange tube 31 closest to the lower second heat exchange tube 32z are opened.
  • Both the lower second heat exchange tube 32z and the lowermost first heat exchange tube 31z open in the lowermost chamber 20z. Therefore, a connection flow path that connects the lower second heat exchange tube 32z and the lowermost first heat exchange tube 31z is unnecessary. Thereby, the manufacturing cost of the heat exchanger 4 is suppressed.
  • the number of upper second heat exchange tubes 32 u that open to the second chamber 22 of the second header 20 is greater than the number of upper first heat exchange tubes 31 u that open to the first chamber 21 of the second header 20.
  • a gas-liquid two-phase refrigerant with a large amount of a gas phase component flows through the upper second heat exchange tube 32u. Since the number of the upper second heat exchange tubes 32u is larger than the number of the upper first heat exchange tubes 31u, the pressure loss in the refrigerant flow process is suppressed. On the other hand, a gas-liquid two-phase refrigerant with a large liquid phase component flows through the upper first heat exchange tube 31u.
  • the gas phase component of the gas-liquid two-phase refrigerant may flow through the upper part of the heat exchange tube (out of gas), and the liquid phase component may stay in the lower part of the heat exchange tube (liquid pool). Since the number of the upper first heat exchange tubes 31u is smaller than the number of the upper second heat exchange tubes 32u, the flow path cross-sectional area of the upper first heat exchange tube 31u is small. Therefore, the gas-liquid two-phase refrigerant circulates integrally in the upper first heat exchange tube 31u. Thereby, since a liquid pool is suppressed and a refrigerant
  • the refrigeration cycle apparatus 1 has a heat exchanger 4, a temperature sensor 14, and a control unit 9.
  • the temperature sensor 14 is connected to the lowermost first refrigerant port 17z below the first chamber 11 where the first heat exchange tube 31 is opened in the first header 10, and outputs a signal corresponding to the refrigerant temperature.
  • the controller 9 controls the defrosting operation based on the output signal of the temperature sensor 14.
  • the temperature sensor 14 is connected to the lowermost first refrigerant port 17 z at the lowermost position of the first chamber 11. Therefore, the control unit 9 can accurately determine the completion of defrosting at the lowest part of the heat exchanger 4 based on the output signal of the temperature sensor 14. Therefore, defrosting can be completed in a short defrosting operation.
  • the temperature sensor 14 is connected to the lowermost first refrigerant port 17z.
  • the temperature sensor 14 connected to the lowermost first refrigerant port 17z may be affected by the refrigerant temperature of the lowermost second refrigerant port 18z.
  • the temperature sensor 14 may be connected to the first refrigerant port 17a below (lower half) of the first chamber 11 of the first header 10 other than the lowermost first refrigerant port 17z.
  • the temperature sensor 14 may be connected to the first refrigerant port 17a of the first small chamber 11a adjacent above the lowermost first small chamber 11z. Thereby, the temperature sensor 14 becomes difficult to be influenced by the refrigerant temperature of the lowermost second refrigerant port 18z.
  • FIG. 8 is a schematic configuration diagram of the heat exchanger 204 of the second embodiment.
  • the heat exchanger 204 of the second embodiment shown in FIG. 8 is different from the heat exchanger 4 of the first embodiment shown in FIG.
  • configurations other than those described below are the same as the configurations of the first embodiment.
  • connection channel 19 allows the lowermost second chamber 12z of the first header 10 and the second chamber 12 to communicate with each other.
  • the connection channel 19 is connected to the lower side of the second chamber 12.
  • the refrigerant flowing through the refrigeration cycle apparatus 1 is mixed with lubricating oil (compressor oil) of the compressor 2.
  • compressor oil lubricating oil
  • the gas phase component of the gas-liquid two-phase refrigerant increases in the process of flowing through the upper second heat exchange tube 32u.
  • the liquid compressor oil mixed in the refrigerant falls below the second chamber 12 and stays there. Therefore, the compressor oil may be insufficient in the compressor 2.
  • the heat exchanger 204 of the second embodiment has a connection channel 19 that communicates the lowermost second chamber 12z of the first header 10 with the lower portion of the second chamber 12.
  • the gaseous refrigerant flowing out from the lowermost second chamber 12z flows through the connection channel 19 and flows into the lower portion of the second chamber 12.
  • the gaseous refrigerant blows up the compressor oil staying below the second chamber 12 and flows out from the second refrigerant port 18.
  • compressor oil returns to a compressor, the shortage of compressor oil in compressor 2 can be controlled.
  • the heat exchanger 4 of the above-described embodiment has a configuration in which the refrigerant flows into the first header 10, is folded at the second header 20, and flows out from the first header 10.
  • the heat exchanger may be configured such that the refrigerant is folded back multiple times at each header.
  • the heat exchanger 4 of the embodiment has a configuration in which the same number of upper second heat exchange tubes are opened with respect to the plurality of second small chambers 22 a formed in the second header 20.
  • the heat exchanger may have a configuration in which different numbers of upper second heat exchange tubes are open to the plurality of second small chambers 22a.
  • the heat exchanger 4 has the second heat exchange tube 32 through which the gas-liquid two-phase refrigerant having a large amount of gas phase components flows.
  • the second heat exchange tube 32 has a lower second heat exchange tube 32z disposed below the first heat exchange tube 31. Thereby, defrosting can be completed in a short defrosting operation.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

La présente invention concerne un échangeur de chaleur qui selon un mode de réalisation comprend : un premier collecteur, un second collecteur et une pluralité de tubes d'échange de chaleur. La pluralité de tubes d'échange de chaleur comprend un premier tube d'échange de chaleur et un second tube d'échange de chaleur. Un fluide frigorigène gaz-liquide dans lequel un composant en phase liquide est un composant principal s'écoule à travers le premier tube d'échange de chaleur. Le second tube d'échange de chaleur communique avec le premier tube d'échange de chaleur et un fluide frigorigène gaz-liquide dans lequel un composant en phase gazeuse est un composant principal s'écoule à travers le second tube d'échange de chaleur. Le second tube d'échange de chaleur comprend un second tube d'échange de chaleur supérieur et un second tube d'échange de chaleur inférieur. Le second tube d'échange de chaleur supérieur est disposé au-dessus du premier tube d'échange de chaleur. Le second tube d'échange de chaleur inférieur est disposé en-dessous du premier tube d'échange de chaleur.
PCT/JP2018/010453 2018-03-16 2018-03-16 Échangeur de chaleur et dispositif à cycle frigorifique WO2019176089A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
PCT/JP2018/010453 WO2019176089A1 (fr) 2018-03-16 2018-03-16 Échangeur de chaleur et dispositif à cycle frigorifique
JP2020506080A JP6906101B2 (ja) 2018-03-16 2018-03-16 熱交換器および冷凍サイクル装置
CN201880084931.0A CN111527356B (zh) 2018-03-16 2018-03-16 热交换器以及制冷循环装置

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PCT/JP2018/010453 WO2019176089A1 (fr) 2018-03-16 2018-03-16 Échangeur de chaleur et dispositif à cycle frigorifique

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CN113339909B (zh) * 2021-05-31 2022-06-03 青岛海信日立空调系统有限公司 热泵空调系统

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JPS62108971A (ja) * 1985-11-06 1987-05-20 株式会社日立製作所 ヒ−トポンプ用熱交換器
JPH10220989A (ja) * 1997-02-05 1998-08-21 Nippon Light Metal Co Ltd 熱交換器及びその除霜方法
US20080023182A1 (en) * 2006-07-25 2008-01-31 Henry Earl Beamer Dual mode heat exchanger assembly
JP2012163319A (ja) * 2011-01-21 2012-08-30 Daikin Industries Ltd 熱交換器および空気調和機
WO2013005729A1 (fr) * 2011-07-05 2013-01-10 シャープ株式会社 Échangeur de chaleur et climatiseur le comportant
CN104949318A (zh) * 2015-06-30 2015-09-30 广东美的制冷设备有限公司 换热器、空调系统以及换热方法
JP2017194201A (ja) * 2016-04-19 2017-10-26 日立ジョンソンコントロールズ空調株式会社 空気調和機

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CN2401837Y (zh) * 1999-11-12 2000-10-18 海尔集团公司 高效除霜空调器
JP5609916B2 (ja) * 2012-04-27 2014-10-22 ダイキン工業株式会社 熱交換器
JP5574028B1 (ja) * 2013-07-31 2014-08-20 株式会社富士通ゼネラル 空気調和装置
CN105135753A (zh) * 2015-08-12 2015-12-09 浙江康盛热交换器有限公司 热泵空调用微通道换热器
CN105352344B (zh) * 2015-11-23 2017-05-03 广东美的制冷设备有限公司 一种平行流换热器及含有其的空调和空调的控制方法

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5079854A (fr) * 1973-11-20 1975-06-28
JPS5393453A (en) * 1977-01-28 1978-08-16 Hitachi Ltd Defrost device of heat exchanger
JPS62108971A (ja) * 1985-11-06 1987-05-20 株式会社日立製作所 ヒ−トポンプ用熱交換器
JPH10220989A (ja) * 1997-02-05 1998-08-21 Nippon Light Metal Co Ltd 熱交換器及びその除霜方法
US20080023182A1 (en) * 2006-07-25 2008-01-31 Henry Earl Beamer Dual mode heat exchanger assembly
JP2012163319A (ja) * 2011-01-21 2012-08-30 Daikin Industries Ltd 熱交換器および空気調和機
WO2013005729A1 (fr) * 2011-07-05 2013-01-10 シャープ株式会社 Échangeur de chaleur et climatiseur le comportant
CN104949318A (zh) * 2015-06-30 2015-09-30 广东美的制冷设备有限公司 换热器、空调系统以及换热方法
JP2017194201A (ja) * 2016-04-19 2017-10-26 日立ジョンソンコントロールズ空調株式会社 空気調和機

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