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WO2017068723A1 - Échangeur de chaleur et appareil à cycle de réfrigération - Google Patents

Échangeur de chaleur et appareil à cycle de réfrigération Download PDF

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Publication number
WO2017068723A1
WO2017068723A1 PCT/JP2015/079994 JP2015079994W WO2017068723A1 WO 2017068723 A1 WO2017068723 A1 WO 2017068723A1 JP 2015079994 W JP2015079994 W JP 2015079994W WO 2017068723 A1 WO2017068723 A1 WO 2017068723A1
Authority
WO
WIPO (PCT)
Prior art keywords
flat tube
heat exchanger
flat
plate
fin
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/JP2015/079994
Other languages
English (en)
Japanese (ja)
Inventor
石橋　晃
真哉 東井上
伊東　大輔
中村　伸
繁佳 松井
裕樹 宇賀神
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to JP2017546376A priority Critical patent/JP6425829B2/ja
Priority to PCT/JP2015/079994 priority patent/WO2017068723A1/fr
Publication of WO2017068723A1 publication Critical patent/WO2017068723A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • 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
    • F28D1/053—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 straight
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements

Definitions

  • the present invention relates to a heat exchanger and a refrigeration cycle apparatus including plate-like fins and flat tubes.
  • Patent Document 1 describes a heat exchanger including a plate-like fin and a plurality of flat heat transfer tubes inserted in the plate-like fin and arranged in parallel in the step direction.
  • the plate-like fin is provided with a slit formed by cutting and raising. In this heat exchanger, heat transfer between the air is promoted by the slit, so that the heat transfer performance can be improved.
  • the present invention has been made to solve the above-described problems, and an object thereof is to provide a heat exchanger and a refrigeration cycle apparatus that can further improve the heat exchanger capability.
  • the heat exchanger according to the present invention includes a plate-like fin, and a first flat tube and a second flat tube that intersect with the plate-like fin and extend in parallel with each other, and the plate-like fin In the parallel plane, the long axis of the first flat tube and the long axis of the second flat tube are parallel to each other, and the first flat tube and the second flat tube among the plate-like fins.
  • Is formed with a slit portion extending in parallel with the long axis of the first flat tube and the long axis of the second flat tube, and the length of the slit portion is The length of the long axis of one flat tube and the length of the long axis of the second flat tube are shorter than each other, and the entire slit portion is formed by the first flat tube and the second flat tube.
  • a straight line connecting one end of each major axis direction along the plate-like fin, the first flat tube, and the second flat tube A straight line connecting each of the other ends of the axial direction along the plate-like fins, in which is provided between the.
  • the refrigeration cycle apparatus according to the present invention includes the heat exchanger according to the present invention.
  • the heat exchanger capability of the heat exchanger can be further improved.
  • FIG. 7 is a cross-sectional view showing a VII-VII cross section of FIG. 6. It is a refrigerant circuit figure of the refrigerating cycle device concerning Embodiment 5 of the present invention.
  • FIG. 1 is a top view showing the overall configuration of the heat exchanger according to the present embodiment.
  • This heat exchanger is accommodated in an outdoor unit of a refrigeration cycle apparatus such as an air conditioner, for example.
  • the heat exchanger includes a plate-like fin and a flat tube, and a refrigerant (an example of a heat medium) that flows through the flat tube and air (an example of an external fluid) that flows along the plate-like fins; It is a fin tube type heat exchanger which performs heat exchange of.
  • the relative dimensional relationship and shape of each component may be different from the actual one.
  • the heat exchanger has heat exchange portions 1a and 1b arranged in two rows along the air flow direction.
  • the heat exchange part 1a is located downstream of the heat exchange part 1b in the air flow.
  • Each of the heat exchange parts 1a and 1b includes a plate-like fin 10 and a flat tube 11 which will be described later.
  • a distribution header 30 that is a liquid-side header tank and a gas header 31 that is a gas-side header tank are disposed at one end of the heat exchange units 1a and 1b. The other ends of the heat exchange parts 1a and 1b are bent so that the heat exchange part 1a is on the inside and the heat exchange part 1b is on the outside.
  • Some flat tubes 11 of the heat exchanging section 1 a are connected to the gas header 31 via joints 18.
  • a part of the flat tube 11 of the heat exchange part 1 b is connected to the distribution header 30 via a joint 18.
  • a part of the flat tubes 11 of the heat exchange part 1 a and a part of the flat tubes 11 of the heat exchange part 1 b are connected via a joint 18 and a U bend 16. Examples of these connection relationships and the configuration of the joint 18 will be described later in a second embodiment.
  • FIG. 2 is a diagram schematically showing a partial configuration of the heat exchanger according to the present embodiment.
  • disconnected by the surface parallel to the plate-shaped fin 10 is shown.
  • each of the heat exchanging portions 1 a and 1 b of the heat exchanger includes a plate-like fin 10 and a plurality of flat tubes 11 that intersect with the plate-like fin 10 and extend in parallel with each other. ing.
  • the flat tube 11 is a heat transfer tube having a flat cross-sectional shape such as an ellipse, an ellipse, or a rectangle.
  • the plurality of flat tubes 11 are arranged such that their long axes in a plane parallel to the plate fins 10 are parallel to each other and parallel to the air flow direction.
  • the long axis of the flat tube 11 in a plane parallel to the plate-like fin 10 may be simply referred to as the long axis of the flat tube 11.
  • the short axis of the flat tube 11 in a plane parallel to the plate-like fin 10 may be simply referred to as the short axis of the flat tube 11.
  • the plurality of flat tubes 11 are arranged in parallel with each other through a predetermined gap in the direction of the short axis of the flat tubes 11. Inside the flat tube 11, a plurality of refrigerant flow paths partitioned by partition walls are formed.
  • the plate-like fin 10 has a rectangular flat plate shape.
  • the plate-like fins 10 are arranged so that the longitudinal direction thereof is parallel to the direction of gravity.
  • a plurality of the plate-like fins 10 are arranged in parallel in a direction orthogonal to the paper surface in FIG.
  • a plurality of notches 12 for inserting a plurality of flat tubes 11 are formed at the downstream end of the plate-like fin 10 in the air flow.
  • the flat tube 11 inserted into the notch 12 is joined to the plate fin 10 by brazing or the like.
  • a flat portion 13 extending along the longitudinal direction of the plate fin 10 is formed at the upstream end of the plate fin 10 in the air flow.
  • the flat portion 13 is a region that is formed substantially flat without the notches 12 and the later-described slit portions 14 and the like being formed in the plate-like fin 10.
  • the flat part 13 becomes a drainage channel for draining condensed water when the heat exchanger operates as an evaporator.
  • the heat exchange units 1a and 1b are arranged such that the arrangement of the plurality of flat tubes 11 in the heat exchange unit 1a and the arrangement of the plurality of flat tubes 11 in the heat exchange unit 1b are shifted from each other by a half pitch.
  • a straight slit portion 14 extending in parallel with the long axis of the flat tube 11 is formed in a region between the two adjacent flat tubes 11 in the plate-like fin 10.
  • the slit part 14 of this example is comprised by one long hole with the both ends of the extending
  • the length b in the extending direction of the slit portion 14 is shorter than the length a of the long axis of the flat tube 11 (b ⁇ a).
  • the entire slit portion 14 includes an imaginary straight line L1 that connects one end 11-1 in the major axis direction of two adjacent flat tubes 11 along the plate-like fins 10, and each of the two flat tubes 11. It is provided between an imaginary straight line L2 connecting the other ends 11-2 in the major axis direction along the plate-like fins 10.
  • one end 11-1 of the flat tube 11 is an end portion on the upstream side of the flat tube 11 in the air flow
  • the other end 11-2 of the flat tube 11 is on the downstream side of the flat tube 11 in the air flow. It is an end.
  • the slit portion 14 is provided below the center line 15 between the long axes of the two adjacent flat tubes 11. For example, the distance between the slit portion 14 and the upper surface of the flat tube 11 adjacent below the slit portion 14 is shorter than the length of the short axis of the flat tube 11.
  • the temperature of the refrigerant flowing through each flat tube 11 in the heat exchanger varies depending on the state of the refrigerant (for example, pressure and dryness). For this reason, when heat transfer occurs between the flat tubes 11 via the plate-like fins 10, heat loss occurs.
  • the length b of the slit portion 14 is shorter than the length a of the long axis of the flat tube 11, and the entire slit portion 14 is formed by the two adjacent flat tubes 11.
  • a straight line L2 connected to each other Therefore, heat loss can be reduced without greatly reducing the fin efficiency related to the heat exchange capability.
  • the entire slit portion 14 is provided between the straight line L1 and the straight line L2, the front edge portion (the upstream end portion in the air flow) of the plate-like fin 10 is provided.
  • the notch 12 and the slit part 14 are not formed. Therefore, a decrease in strength of the plate-like fin 10 can be suppressed.
  • the slit portion 14 is formed below the center line 15 between the long axes of the two adjacent flat tubes 11. For this reason, when the heat exchanger operates as an evaporator, the condensed water staying at the upper portion of the flat tube 11 can be drained to the front flat portion 13 by surface tension. Therefore, an increase in the ventilation resistance of the heat exchanger can be suppressed.
  • FIG. 3 is an explanatory diagram of the heat exchanger according to the present embodiment.
  • FIG. 3 shows ten flat tubes 11 arranged in five rows in the vertical direction and in two rows in the air flow direction.
  • the flat tubes of the heat exchange unit 1a arranged on the downstream side in the air flow may be referred to as flat tubes 11a1 to 11a5 in order from the top, and the heat exchange unit 1b arranged on the upstream side in the air flow.
  • These flat tubes may be referred to as flat tubes 11b1 to 11b5 in order from the top.
  • FIG. 3 also shows the refrigerant flow when the heat exchanger operates as a condenser.
  • a hairpin tube bent into a hairpin shape at the center in the tube axis direction is used as the flat tube 11.
  • the ends of the two flat tubes 11 (for example, the flat tube 11 a 1 and the flat tube 11 a 2) adjacent to each other in the vertical direction are integrally connected via the hairpin portion 17.
  • the two flat tubes 11 adjacent in the vertical direction may actually be constituted by one tube.
  • a plurality of refrigerant paths are constituted by a plurality of flat tubes 11 in the heat exchanger.
  • Each of the plurality of refrigerant paths circulates the refrigerant in series.
  • the plurality of refrigerant paths are connected in parallel, for example.
  • One refrigerant path includes eight flat tubes 11a1 to 11a4 and 11b1 to 11b4.
  • the front end portion of the flat tube 11a4 is connected to the gas header 31 via a refrigerant pipe (not shown) serving as an inlet portion of the refrigerant path.
  • the superheated gas refrigerant supplied from the gas header 31 flows into the flat tube 11a4 through the refrigerant pipe.
  • the end on the back side of the flat tube 11a4 and the end on the back side of the flat tube 11a3 are connected via a hairpin portion 17.
  • the end portion on the near side of the flat tube 11a3 and the end portion on the near side of the flat tube 11a2 are connected via a U-bend 16.
  • the end on the back side of the flat tube 11 a 2 and the end on the back side of the flat tube 11 a 1 are connected via a hairpin portion 17.
  • An end on the near side of the flat tube 11a1 and an end on the near side of the flat tube 11b1 are connected via a U-bend 16.
  • the end on the back side of the flat tube 11b1 and the end on the back side of the flat tube 11b2 are connected via a hairpin portion 17.
  • An end portion on the near side of the flat tube 11b2 and an end portion on the near side of the flat tube 11b3 are connected via a U-bend 16.
  • the end on the back side of the flat tube 11b3 and the end on the back side of the flat tube 11b4 are connected via a hairpin portion 17.
  • the front end of the flat tube 11b4 is connected to the distribution header 30 via a refrigerant pipe (not shown) serving as an outlet of the refrigerant path. From the flat tube 11b4, the supercooled liquid refrigerant flows out to the distribution header 30 through the refrigerant pipe.
  • the flat tubes 11a5 and 11b5 constitute a part of another refrigerant path connected in parallel with the refrigerant path.
  • the flat tube 11 adjacent to the upper side of the flat tube 11a1 is connected to a refrigerant pipe serving as an inlet portion of another refrigerant path, and the flat tube adjacent to the upper side of the flat tube 11b1.
  • 11 is connected to a refrigerant pipe serving as an outlet of the refrigerant path.
  • a circular pipe having a circular cross section is used as the refrigerant pipe connected to the inlet and outlet parts of the refrigerant path and the U bend 16. For this reason, the flat tube 11 and the refrigerant pipe or the U bend 16 are connected via the joints 18 respectively.
  • FIG. 4 is a diagram showing a configuration of the joint 18 according to the present embodiment.
  • a side view (a) and a front view (b) of the joint 18 are shown together.
  • a circular pipe portion 18 a having a circular cross-sectional shape is provided at one end portion of the joint 18.
  • the other end portion of the joint 18 is provided with a flat tube portion 18b having a flat cross-sectional shape.
  • a flow path shape conversion part 18c for converting the flow path shape is provided.
  • the circular pipe portion 18 a is connected to a circular pipe such as a refrigerant pipe or a U bend 16
  • the flat pipe portion 18 b is connected to the flat pipe 11.
  • the inner diameter of the circular pipe portion 18a is larger than the inner diameter of the flat tube portion 18b in the short axis direction and smaller than the inner diameter of the flat tube portion 18b in the long axis direction.
  • the flat tube 11 (for example, the flat tubes 11 a 4 and 11 b 4) connected to the inlet or outlet of the refrigerant path, the flat tube 11 adjacent in the vertical direction, and separate
  • the slit part 14 is formed only between the flat tubes 11 (for example, the flat tubes 11a5 and 11b5) constituting a part of the refrigerant path.
  • the slit part 14 is not formed between the flat tubes 11 other than the above.
  • the superheated gas refrigerant supplied from the gas header 31 flows into the flat tube 11a4.
  • the refrigerant that has flowed into the flat tube 11a4 as superheated gas becomes a two-phase state due to heat radiation to the air, and sequentially flows through the flat tubes 11a3, 11a2, 11a1, 11b1, 11b2, 11b3, and 11b4. From the flat tube 11 b 4, the refrigerant that has become supercooled liquid flows out to the distribution header 30.
  • the superheated gas refrigerant flows through the flat tube 11a4 connected to the inlet portion of the refrigerant path, and the supercooled liquid refrigerant flows through the flat tube 11b4 connected to the outlet portion of the refrigerant path.
  • Two-phase refrigerant mainly circulates through the other flat tubes 11a3, 11a2, 11a1, 11b1, 11b2, and 11b3.
  • two-phase refrigerant mainly circulates in the flat tubes 11a5 and 11b5 that constitute part of the middle of another refrigerant path.
  • the flat tube 11 (for example, the flat tubes 11a4 and 11b4) connected to the inlet portion or the outlet portion of the refrigerant path, the flat tube 11 adjacent to the flat tube 11 in the vertical direction, and one of the other refrigerant paths.
  • a slit portion 14 that suppresses heat transfer is formed. Therefore, according to this Embodiment, since the heat loss between adjacent refrigerant
  • the slit portion 14 is not formed between the flat tubes 11 other than the above. Therefore, according to the present embodiment, it is possible to suppress a decrease in fin efficiency and a decrease in strength of the plate-like fin 10.
  • FIG. 5 is a diagram schematically showing a partial configuration of the heat exchanger according to the present embodiment.
  • the slit part 14 in this Embodiment has the some slit 14a arrange
  • the plurality of slits 14a are arranged in a straight line at regular intervals.
  • Each of the slits 14a is constituted by a long hole whose both ends in the extending direction are closed.
  • the strength of the plate-like fin 10 can be improved and a decrease in fin efficiency can be suppressed. Therefore, the heat exchange capability of the heat exchanger can be further improved.
  • FIG. 6 is a diagram schematically showing a partial configuration of the heat exchanger according to the present embodiment.
  • 7 is a cross-sectional view showing a VII-VII cross section of FIG.
  • a cut-and-raised portion 19 in which the plate-like fins 10 in the region are cut and raised is formed in a region between the adjacent flat tubes 11 in the plate-like fin 10.
  • a heat transfer promoting slit 20 that promotes heat transfer with respect to the air flow is formed.
  • the slit portion 14 is provided below the cut and raised portion 19. That is, the slit portion 14 is provided between the cut and raised portion 19 and the flat tube 11 adjacent to the lower portion of the cut and raised portion 19.
  • the condensed water drained from the heat transfer promoting slit 20 is held in the slit portion 14 below the condensed water.
  • the condensed water held in the slit portion 14 is drained from the front flat portion 13 without staying on the upper surface of the flat tube 11 below. Therefore, according to the present embodiment, it is possible to suppress an increase in the ventilation resistance of the heat exchanger while improving the heat exchanger capability by the heat transfer promoting slit 20.
  • FIG. 8 is a refrigerant circuit diagram of the refrigeration cycle apparatus according to the present embodiment.
  • the refrigeration cycle apparatus includes a compressor 33, a condensation heat exchanger 34, an expansion device 35, and an evaporating heat exchanger 36.
  • the condensing heat exchanger 34 and the evaporation heat exchanger 36 are provided with a blower 37 that blows air and a blower motor 38 that rotationally drives the blower 37.
  • the refrigeration cycle apparatus may include a four-way valve that switches the flow direction of the refrigerant.
  • the heat exchanger includes the plate-like fins 10 and the first flat tubes 11 that intersect with the plate-like fins 10 and extend in parallel with each other (for example, in FIG. The flat tube 11a4) and the second flat tube 11 (for example, the flat tube 11a5 shown in FIG. 3), and the long axis of the first flat tube 11 in a plane parallel to the plate fin 10
  • the major axes of the second flat tubes 11 are parallel to each other, and the region between the first flat tube 11 and the second flat tube 11 in the plate-like fin 10 is the same as that of the first flat tube 11.
  • a slit portion 14 extending in parallel with the major axis and the major axis of the second flat tube 11 is formed, and the length b of the slit portion 14 is the length a of the major axis of the first flat tube 11 and the first axis.
  • the length of the long axis of the two flat tubes 11 is shorter than the length a, and the entire slit portion 14 is the first flat tube.
  • the other end 11-2 in the axial direction is provided between the straight line L2 connecting the plate-like fins 10 with each other.
  • the first flat tube 11 (for example, the flat tube 11a4 illustrated in FIG. 3) is the second flat tube 11 (for example, the flat tube 11a5 illustrated in FIG. 3).
  • the slit portion 14 is formed closer to the second flat tube 11 than the center line 15 between the first flat tube 11 and the second flat tube 11. May be.
  • the condensed water staying at the top of the flat tube 11 can be drained to the front flat portion 13 by surface tension. Therefore, an increase in the ventilation resistance of the heat exchanger can be suppressed.
  • the first flat tube 11 (for example, the flat tube 11a4 shown in FIG. 3) constitutes a part of the refrigerant path, and at the inlet or outlet of the refrigerant path.
  • the second flat tube 11 (for example, the flat tube 11a5 shown in FIG. 3) may constitute a part of another refrigerant path connected in parallel with the refrigerant path. .
  • the slit portion 14 may have a plurality of slits 14a arranged in a perforation.
  • the first flat tube 11 is disposed above the second flat tube 11, and the first flat tube 11 among the plate-like fins 10.
  • a cut and raised portion 19 is formed in a region between the first flat tube 11 and the second flat tube 11, and the slit portion 14 may be formed closer to the second flat tube 11 than the cut and raised portion 19. .
  • the refrigeration cycle apparatus includes the heat exchanger according to the above embodiment.
  • a refrigerant such as R410A, R32, HFO-1234yf can be used as a heat medium that circulates inside the flat tube 11.
  • air and refrigerant are exemplified as the working fluid, but the same effect can be obtained even when other gas, liquid, gas-liquid mixed fluid is used.
  • the heat exchanger accommodated in the outdoor unit is exemplified, but the same effect can be obtained even when the present invention is applied to the heat exchanger accommodated in the indoor unit.
  • a refrigerating machine oil such as a mineral oil, an alkylbenzene oil, an ester oil, an ether oil or a fluorine oil can be used. Regardless of whether or not the refrigerant and the refrigerating machine oil are compatible, the same effect can be obtained in any refrigerating machine oil used.
  • the slit part 14 was notched from the downstream edge part of the plate-like fin 10 in the flow of air, for example It may be a notch.
  • the present invention can be used in a heat pump device and the like that need to be easily manufactured, improve heat exchange capability, and improve energy saving performance.
  • 1a, 1b heat exchange section 10 plate fin, 11, 11a1, 11a2, 11a3, 11a4, 11a5, 11b1, 11b2, 11b3, 11b4, 11b5 flat tube, 11-1 one end, 11-2 other end, 12 notch , 13 flat part, 14 slit part, 14a slit, 15 center line, 16 U bend, 17 hairpin part, 18 joint, 18a circular pipe part, 18b flat pipe part, 18c flow path shape conversion part, 19 cut and raised part, 20 Slit for heat transfer, 30 distribution header, 31 gas header, 33 compressor, 34 condensing heat exchanger, 35 throttling device, 36 evaporating heat exchanger, 37 blower, 38 blower motor, L1, L2 straight line.

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

Abstract

La présente invention concerne un échangeur de chaleur et un appareil à cycle de réfrigération permettant d'améliorer davantage les performances d'échange de chaleur. L'échangeur de chaleur est pourvu de plaques-ailettes ainsi que d'un premier tube aplati et d'un second tube aplati. L'axe principal du premier tube aplati et l'axe principal du second tube aplati sont parallèles l'un par rapport à l'autre dans un plan parallèle aux plaques-ailettes. Une fente s'étendant parallèlement à l'axe principal du premier tube aplati et à l'axe principal du second tube aplati est formée dans la région de plaque-ailette entre le premier tube aplati et le second tube aplati. La longueur de la fente est plus courte que la longueur de l'axe principal du premier tube aplati et que la longueur de l'axe principal du second tube aplati. La fente entière est prévue entre une ligne droite reliant une extrémité dans la direction d'axe principal du premier tube aplati et du second tube aplati le long des plaques-ailettes et une ligne droite reliant l'autre extrémité dans la direction d'axe principal du premier tube aplati et du second tube aplati le long des plaques-ailettes.
PCT/JP2015/079994 2015-10-23 2015-10-23 Échangeur de chaleur et appareil à cycle de réfrigération Ceased WO2017068723A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2017546376A JP6425829B2 (ja) 2015-10-23 2015-10-23 熱交換器及び冷凍サイクル装置
PCT/JP2015/079994 WO2017068723A1 (fr) 2015-10-23 2015-10-23 Échangeur de chaleur et appareil à cycle de réfrigération

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Application Number Priority Date Filing Date Title
PCT/JP2015/079994 WO2017068723A1 (fr) 2015-10-23 2015-10-23 Échangeur de chaleur et appareil à cycle de réfrigération

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WO2017068723A1 true WO2017068723A1 (fr) 2017-04-27

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019008997A1 (fr) * 2017-07-05 2019-01-10 日立ジョンソンコントロールズ空調株式会社 Échangeur thermique extérieur pour climatiseur et climatiseur doté de celui-ci
WO2019009158A1 (fr) * 2017-07-03 2019-01-10 ダイキン工業株式会社 Échangeur de chaleur
JP6644194B1 (ja) * 2019-01-21 2020-02-12 三菱電機株式会社 室外機及び空気調和装置
CN113357937A (zh) * 2017-12-07 2021-09-07 浙江盾安机械有限公司 翅片及换热器

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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WO2019009158A1 (fr) * 2017-07-03 2019-01-10 ダイキン工業株式会社 Échangeur de chaleur
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JPWO2019008997A1 (ja) * 2017-07-05 2019-11-07 日立ジョンソンコントロールズ空調株式会社 空気調和機の室外熱交換器及びこれを備える空気調和機
US11274838B2 (en) 2017-07-05 2022-03-15 Hitachi-Johnson Controls Air Conditioning, Inc. Air-conditioner outdoor heat exchanger and air-conditioner including the same
JP7050065B2 (ja) 2017-07-05 2022-04-07 日立ジョンソンコントロールズ空調株式会社 空気調和機の室外熱交換器及びこれを備える空気調和機
CN113357937A (zh) * 2017-12-07 2021-09-07 浙江盾安机械有限公司 翅片及换热器
CN113357937B (zh) * 2017-12-07 2024-06-11 浙江盾安机械有限公司 翅片及换热器
JP6644194B1 (ja) * 2019-01-21 2020-02-12 三菱電機株式会社 室外機及び空気調和装置
WO2020152738A1 (fr) * 2019-01-21 2020-07-30 三菱電機株式会社 Échangeur de chaleur et dispositif de climatisation
US12000633B2 (en) 2019-01-21 2024-06-04 Mitsubishi Electric Corporation Outdoor unit and air-conditioning apparatus

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