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WO2018185824A1 - Échangeur thermique et dispositif à cycle de réfrigération - Google Patents

Échangeur thermique et dispositif à cycle de réfrigération Download PDF

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Publication number
WO2018185824A1
WO2018185824A1 PCT/JP2017/014031 JP2017014031W WO2018185824A1 WO 2018185824 A1 WO2018185824 A1 WO 2018185824A1 JP 2017014031 W JP2017014031 W JP 2017014031W WO 2018185824 A1 WO2018185824 A1 WO 2018185824A1
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WO
WIPO (PCT)
Prior art keywords
heat transfer
fin
heat exchanger
transfer tube
tube portion
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/JP2017/014031
Other languages
English (en)
Japanese (ja)
Inventor
石橋　晃
前田　剛志
真哉 東井上
伊東　大輔
中村　伸
良太 赤岩
暁 八柳
龍一 永田
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 JP2019510523A priority Critical patent/JP6719657B2/ja
Priority to PCT/JP2017/014031 priority patent/WO2018185824A1/fr
Publication of WO2018185824A1 publication Critical patent/WO2018185824A1/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
    • 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
    • F28D1/053—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
    • F28F1/10—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
    • F28F1/14—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 longitudinally
    • F28F1/22—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 longitudinally the means having portions engaging further tubular elements

Definitions

  • the present invention relates to a heat exchanger and a refrigeration cycle apparatus.
  • a heat exchanger used in an air conditioner as an example of a refrigeration cycle apparatus is disclosed in, for example, Japanese Patent Application Laid-Open No. 2006-84078 (Patent Document 1).
  • the heat exchanger described in this publication is a small-diameter multi-tube heat exchanger having a plurality of small-diameter heat transfer tube units.
  • Each of the plurality of small-diameter heat transfer tube units is configured by laminating two symmetrical fin plates each having a groove portion for forming a tube body portion.
  • the present invention has been made in view of the above problems, and an object thereof is to provide a heat exchanger that can be easily manufactured and a refrigeration cycle apparatus including the heat exchanger.
  • the heat exchanger of the present invention includes a first heat transfer tube portion, a second heat transfer tube portion arranged so as to run parallel to the first heat transfer tube portion, and a corrugated fin having a valley portion and a peak portion.
  • the fin includes a first surface and a second surface opposite to the first surface.
  • the trough is configured such that the fin protrudes in a direction from the first surface toward the second surface.
  • the mountain portion is configured such that the fin protrudes in a direction from the second surface toward the first surface.
  • the 1st heat exchanger tube part is connected to the trough part in the 1st surface of a fin.
  • the 2nd heat exchanger tube part is connected to the peak part in the 2nd surface of a fin.
  • the valley and the mountain are arranged side by side along the wind direction of the wind flowing into the fin.
  • the first heat transfer tube portion is connected to the fin valley portion, and the second heat transfer tube portion is connected to the fin peak portion. For this reason, the assembly to the fin of the 1st heat exchanger tube part and the 2nd heat exchanger tube part is easy. Therefore, it is easy to manufacture the heat exchanger.
  • FIG. 4 is a sectional view taken along line IV-IV in FIG. 3. It is a side view which shows roughly the structure of the heat exchanger in the modification 1 of one embodiment of this invention.
  • FIG. 6 is a sectional view taken along line VI-VI in FIG. 5. It is a front view which shows roughly the structure of the heat exchanger in the modification 2 of one embodiment of this invention. It is a front view which shows roughly the structure of the heat exchanger in the modification 3 of one embodiment of this invention.
  • FIG. 9 is a cross-sectional view taken along line IX-IX in FIG. 8. It is sectional drawing in the cross-sectional position corresponding to FIG. 2 which shows schematically the structure of the heat exchanger in the modification 4 of one embodiment of this invention. It is a figure which shows the refrigerant circuit of the refrigerating-cycle apparatus in one embodiment of this invention.
  • FIG. 1 is a perspective view of a heat exchanger 1 in the present embodiment.
  • FIG. 2 is a front view of the heat exchanger 1 in the present embodiment.
  • FIG. 3 is a side view of the heat exchanger 1 in the present embodiment.
  • FIG. 4 is a cross-sectional view of the heat exchanger 1 in the present embodiment.
  • the heat exchanger 1 in the present embodiment is a finned tube heat exchanger.
  • the heat exchanger 1 in this Embodiment is used for an air conditioner, an air-conditioning freezer, etc., for example.
  • the heat exchanger 1 in the present embodiment includes a first heat transfer tube portion 10, a second heat transfer tube portion 20, fins 30, an inlet header 40, an outlet header 50, an inlet pipe 60, and an outlet pipe 70. It has.
  • the first heat transfer tube portion 10, the second heat transfer tube portion 20, and the fins 30 are disposed between the inlet header 40 and the outlet header 50.
  • the first heat transfer tube portion 10 and the second heat transfer tube portion 20 are connected to the inlet header 40 and the outlet header 50 so that the refrigerant flows from the inlet header 40 to the outlet header 50, respectively.
  • the inlet header 40 is disposed so as to face the outlet header 50.
  • the inlet header 40 is disposed below the outlet header 50 in the gravity direction D2.
  • Each of the inlet header 40 and the outlet header 50 has a refrigerant passage through which a refrigerant flows.
  • An inlet pipe 60 is connected to the inlet header 40.
  • An outlet pipe 70 is connected to the outlet header 50.
  • the first heat transfer tube portion 10 and the second heat transfer tube portion 20 are integrally configured by being connected to the fins 30.
  • the first heat transfer tube portion 10, the second heat transfer tube portion 20, and the fins 30 that are integrally configured constitute one heat transfer unit 100.
  • a plurality of heat transfer units 100 are arranged side by side in the step direction D1.
  • the first heat transfer tube portion 10 extends in the gravity direction D2.
  • the first heat transfer tube portion 10 is a cylindrical tube.
  • the 1st heat exchanger tube part 10 is comprised so that a refrigerant
  • the 1st heat exchanger tube part 10 is comprised by the linear form.
  • the first heat transfer tube section 10 has a plurality of first heat transfer tubes 11.
  • the plurality of first heat transfer tubes 11 are arranged in parallel to each other.
  • the first heat transfer tube portion 10 has two first heat transfer tubes 11.
  • the second heat transfer tube portion 20 is arranged so as to run in parallel with the first heat transfer tube portion 10.
  • the second heat transfer tube portion 20 is disposed in parallel with the first heat transfer tube portion 10.
  • the second heat transfer tube portion 20 is disposed so as to be adjacent to the first heat transfer tube portion 10 in the column direction D3.
  • the second heat transfer tube portion 20 extends in the gravity direction D2.
  • the second heat transfer tube 21 is a cylindrical tube.
  • the 2nd heat exchanger tube part 20 is comprised so that a refrigerant
  • the 2nd heat exchanger tube part 20 is constituted in the shape of a straight line.
  • the second heat transfer tube section 20 has a plurality of second heat transfer tubes 21.
  • the plurality of second heat transfer tubes 21 are arranged in parallel to each other.
  • Each of the plurality of second heat transfer tubes 21 is arranged alternately with each of the plurality of first heat transfer tubes 11.
  • the second heat transfer tube section 20 has two first heat transfer tubes 11.
  • the fin 30 is configured to meander in a wave shape.
  • the fins 30 extend in the direction of gravity.
  • the fin 30 is formed of an integral plate. That is, the fin 30 has a plane extending in the direction of gravity.
  • the corrugated fin 30 has a valley 30a, a mountain 30b, an upwind extending portion 30c, and an upwind extending portion 30d.
  • the valley part 30a and the peak part 30b are arranged so as to be adjacent to each other. That is, the valleys 30a and the peaks 30b are alternately arranged.
  • the valley portion 30 a and the mountain portion 30 b are arranged side by side along the wind direction A of the wind flowing into the fins 30.
  • the fin 30 has a first surface 31 and a second surface 32.
  • the second surface 32 is located on the opposite side to the first surface 31.
  • the trough 30a is configured such that the fins 30 protrude in a direction from the first surface 31 toward the second surface 32.
  • the peak portion 30 b is configured such that the fins 30 protrude in the direction from the second surface 32 toward the first surface 31. That is, the valley part 30a and the peak part 30b are configured to protrude in opposite directions.
  • the first heat transfer tube portion 10 is connected to the valley portion 30 a on the first surface 31 of the fin 30.
  • the 1st heat exchanger tube part 10 is arrange
  • the second heat transfer tube portion 20 is connected to the peak portion 30 b on the second surface 32 of the fin 30.
  • the 2nd heat exchanger tube part 20 is arrange
  • the valley portion 30a has a plurality of valleys 30a1
  • the mountain portion 30b has a plurality of peaks 30b1.
  • the valley part 30a has two valleys 30a1, and the peak part 30b has two peaks 30b1.
  • Each of the two first heat transfer tubes 11 is connected to each of the two valleys 30a1.
  • Each of the two second heat transfer tubes 21 is connected to each of the two peaks 30b1. That is, four heat transfer tube groups including the first heat transfer tube 11 and the second heat transfer tube 21 are connected to one fin 30.
  • the windward extending portion 30c is configured to extend straight from the valley portion 30a or the mountain portion 30b arranged on the most windward side toward the windward side. Extending straight toward the windward means extending along the wind direction toward the windward. That is, the windward extending portion 30c may be inclined or curved as long as it extends in the wind direction toward the windward.
  • the windward extending portion 30c extends along the column direction D3.
  • the windward extending part 30c is arranged at the center C in the direction in which the valley part 30a and the peak part 30b protrude.
  • the windward extending portion 30c has a dimension larger than the diameter of each of the first heat transfer tube portion 10 and the second heat transfer tube portion 20 in the column direction D3.
  • the windward extending portion 30c has a dimension smaller than the distance (row pitch) between the first heat transfer tube portion 10 and the second heat transfer tube portion 20 in the row direction D3.
  • the leeward extending part 30d is configured to extend straight from the valley part 30a and the mountain part 30b arranged most leeward of the wind toward the leeward side.
  • To extend straight toward the lee means to extend along the wind direction toward the lee. That is, the leeward extending portion 30d may be inclined or curved as long as it extends in the wind direction toward the leeward.
  • the leeward extending part 30d extends along the column direction D3.
  • the leeward extending part 30d is arranged at the center C in the direction in which the valley part 30a and the peak part 30b protrude.
  • the leeward extending part 30d has a dimension larger than the diameter of each of the first heat transfer tube part 10 and the second heat transfer tube part 20 in the column direction D3.
  • the leeward extending portion 30d has a dimension smaller than the distance (row pitch) between the first heat transfer tube portion 10 and the second heat transfer tube portion 20 in the row direction D3.
  • the first heat transfer tube portion 10, the second heat transfer tube portion 20, and the fins 30 are made of the same material.
  • Each material of the 1st heat exchanger tube part 10, the 2nd heat exchanger tube part 20, and the fin 30 is copper, for example.
  • Each of the 1st heat exchanger tube part 10 and the 2nd heat exchanger tube part 20, and the fin 30 are connected by brazing. In this case, copper brazing may be used.
  • the refrigerant flows into the inlet header 40 from the inlet pipe 60 connected to the inlet header 40 in a gas-liquid two-phase state.
  • the gas-liquid two-phase refrigerant is distributed from the inlet header 40 to each tube group of the first heat transfer tube portion 10 and the second heat transfer tube portion 20 and rises toward the outlet header 50.
  • the gas-liquid two-phase refrigerant flows through the first heat transfer tube portion 10 and the second heat transfer tube portion 20, the air and heat around the first heat transfer tube portion, the second heat transfer tube portion 20, and the fins 30 are heated. It becomes a gas state by exchanging.
  • the gaseous refrigerant merges at the outlet header 50 and flows out from the outlet pipe 70 connected to the outlet header 50.
  • the effect of the heat exchanger 1 in this Embodiment is demonstrated.
  • the first heat transfer tube portion 10 is connected to the valley portion 30 a of the fin 30, and the second heat transfer tube portion 20 is connected to the peak portion 30 b of the fin 30. .
  • the assembly to the fin 30 of the 1st heat exchanger tube part 10 and the 2nd heat exchanger tube part 20 is easy. Therefore, manufacture of the heat exchanger 1 is easy.
  • the valley portion 30a and the mountain portion 30b are arranged side by side along the wind direction A of the wind flowing into the fins 30, the draft resistance of the wind flowing along the fins 30 can be reduced. Therefore, the heat exchange efficiency can be improved.
  • the fin 30 has a corrugated shape
  • the fin 30 and the air come into contact between the fin 30 on the leeward side and the leeward side of the fin 30 compared to the case where the fin 30 has a linear shape.
  • the area increases. For this reason, the heat transfer area of the fin 30 can be expanded.
  • the fin 30 has a corrugated shape
  • the flow of air flowing along the fin 30 meanders. For this reason, the distance which the fin 30 and air contact increases. Therefore, heat exchange efficiency can be improved.
  • the first heat transfer tube portion 10, the second heat transfer tube portion 20, and the fins 30 extend in the direction of gravity.
  • condensed water adheres to the first heat transfer tube unit 10, the second heat transfer tube unit 20, and the fins 30. Since the first heat transfer tube portion 10, the second heat transfer tube portion 20 and the fin 30 extend in the gravity direction D2, the condensed water is transferred to the first heat transfer tube portion 10, the second heat transfer tube portion 20 and the fin 30 and discharged downward. can do. Thereby, condensed water is drained without delay. Therefore, the drainage performance during normal operation and defrost operation after frosting is improved, and heat exchanger performance can be maintained high.
  • the fin 30 has the windward extending portion 30c that extends straight from the valley portion 30a and the mountain portion 30b that are disposed most upwind toward the windward side. Is included. For this reason, when the heat exchanger 1 is used as an evaporator, generation
  • the fin 30 includes the leeward extending portion 30d that extends straight from the valley portion 30a and the ridge portion 30b arranged most leeward toward the leeward side. Yes. For this reason, the air flowing downstream from the leeward extending portion 30d can be rectified. Further, the heat transfer area of the fins 30 can be increased by the leeward extending portion 30d.
  • the fin 30 in the present embodiment is formed of an integral plate, the first heat transfer tube portion 10, the second heat transfer tube portion 20, and the fin 30 can be integrated. Therefore, the fin 30 to which the first heat transfer tube portion 10 and the second heat transfer tube portion 20 are connected can be handled as a single heat transfer tube. For this reason, it becomes easy to handle the 1st heat exchanger tube part 10, the 2nd heat exchanger tube part 20, and the fin 30 at the time of manufacture of heat exchanger 1. Therefore, the manufacturability of the heat exchanger 1 is increased.
  • each of the first heat transfer tube portion 10, the second heat transfer tube portion 20, and the fins 30 is made of the same material. For this reason, the heat transfer resistance between each of the first heat transfer tube portion 10 and the second heat transfer tube portion 20 and the fins 30 can be minimized. Thereby, heat exchange efficiency can be improved.
  • the 1st heat exchanger tube part 10 and the 2nd heat exchanger tube part 20, and the fin 30 can be brazed with the same material. For this reason, each of the 1st heat exchanger tube part 10 and the 2nd heat exchanger tube part 20 compared with the case where each of the 1st heat exchanger tube part 10, the 2nd heat exchanger tube part 20, and the fin 30 is comprised with a different material. The contact resistance between each and the fin 30 can be reduced. Thereby, heat exchange efficiency can be improved.
  • the heat exchanger 1 of each modified example has the same configuration as that of the heat exchanger 1 of the present embodiment, and thus the same configuration is denoted by the same reference numeral. Do not repeat the explanation.
  • FIG. 5 is a side view of the heat exchanger 1 in Modification 1 of the present embodiment.
  • FIG. 6 is a cross-sectional view of the heat exchanger 1 in Modification 1 of the present embodiment.
  • a plurality of heat transfer units 100 are arranged in two rows.
  • the plurality of heat transfer units 100 include a heat transfer unit 101 in a row (windward row) arranged on the windward side and a heat transfer unit 102 in a row (leeward row) arranged on the windward side.
  • Each of the heat transfer unit 101 in the windward row and the heat transfer unit 102 in the leeward row are connected to the row-crossing header 80, and are connected to each other via the row-header header 80.
  • the heat transfer unit 101 in the windward row and the heat transfer unit 102 in the leeward row are arranged so as to be shifted from each other in the step direction D1.
  • the first heat transfer tube portion 10 and the second heat transfer tube portion 20 of the heat transfer unit 101 in the windward row, and the first heat transfer tube portion 10 and the second heat transfer tube portion 20 of the heat transfer unit 102 in the leeward row. Is arranged by shifting the distance of half the pitch (stage pitch) of the first heat transfer tube portion 10 and the second heat transfer tube portion 20 in the step direction D1.
  • the refrigerant flows into the inlet header 40 in a gas-liquid two-phase state from an inlet pipe 60 connected to the inlet header 40 of the heat transfer unit 101 in the windward row.
  • the refrigerant in the gas-liquid two-phase state is distributed from the inlet header 40 to each tube group of the first heat transfer tube portion 10 and the second heat transfer tube portion 20, rises toward the outlet header 50, and then passes through the row header 80. It moves to the heat transfer unit 102 in the leeward row and is distributed to the first heat transfer tube portion 10 and the second heat transfer tube portion 20 of the heat transfer unit 101 in the leeward row.
  • the refrigerant in the gas-liquid two-phase state flows through the first heat transfer tube portion 10 and the second heat transfer tube portion 20 of the heat transfer unit 102 in the leeward row, and thus the first heat transfer tube portion 10 and the second heat transfer tube portion 20. And it will be in a gas state by exchanging heat with the air around the fin 30.
  • the gaseous refrigerant merges at the outlet header 50 and flows out from the outlet pipe 70 connected to the outlet header 50.
  • the heat exchanger 1 in the first modification of the present embodiment in the heat transfer unit 101 in the windward row and the heat transfer unit 102 in the leeward row, from the first heat transfer tube portion 10 and the second heat transfer tube portion 20. Are arranged in a state shifted by a half (half pitch) of the step pitch in the step direction D1. For this reason, a temperature boundary layer is newly constructed at the front edge of the fin 30 of the leeward heat transfer unit 102. Thereby, a heat transfer rate improves.
  • FIG. 7 is a side view of the heat exchanger 1 in Modification 2 of the present embodiment.
  • the heat exchanger 1 includes the first heat transfer tube portion 10 and the second heat transfer tube portion near the inlet header 40. 20 is bent. Specifically, the first heat transfer tube portion 10 and the second heat transfer tube portion 20 are bent inward in the column direction D3. The first heat transfer tube portion 10 and the second heat transfer tube portion 20 are bent between the fin 30 and the inlet header 40. The dimension of the inlet header 40 in the column direction D3 is smaller than the dimension of the outlet header 50 in the column direction.
  • the volume of the inlet header 40 is reduced, so that the inlet header 40 can be reduced in size.
  • the refrigerant is distributed to the tube group. It is possible to reduce variations in the refrigerant flow rate. Therefore, when the heat exchanger 1 is used as an evaporator, it is possible to prevent the superheat region from being varied due to the liquid refrigerant being biased in the heat exchanger 1. Thereby, it can suppress that heat exchange efficiency falls.
  • FIG. 8 is a side view of the heat exchanger 1 in Modification 3 of the present embodiment.
  • FIG. 9 is a cross-sectional view of the heat exchanger 1 in Modification 3 of the present embodiment.
  • fin 30 includes a first fin portion 301 and a second fin portion 302.
  • the 2nd fin part 302 is arrange
  • the 1st fin part 301 and the 2nd fin part 302 contain the trough part 30a and the peak part 30b, respectively.
  • Valley portions 30a and peak portions 30b of first fin portion 301 are opposite to valley portions 30a and peak portions 30b of second fin portion 302 with respect to first heat transfer tube portion 10 and second heat transfer tube portion 20, respectively.
  • the 1st fin part 301 and the 2nd fin part 302 are joined to the 1st heat exchanger tube part 10 and the 2nd heat exchanger tube part 20 by turns in the reverse direction.
  • arrangement positioning of each 1st surface 31 and the 2nd surface 32 becomes reverse.
  • the trough part 30a and the peak part 30b of the 1st fin part 301 are with respect to each of the 1st heat exchanger tube part 10 and the 2nd heat exchanger tube part 20.
  • the second fin portion is disposed on the opposite side to the valley portion 30a and the peak portion 30b.
  • the 1st fin part 301 and the 2nd fin part 302 are mutually arrange
  • the manufacturing method of the heat exchanger 1 in the modification 3 of this Embodiment is demonstrated.
  • the manufacturing method of the heat exchanger 1 in the modification 3 of this Embodiment is provided with the following structure.
  • the tube group consisting of the fins 30, the first heat transfer tube portion 10, and the second heat transfer tube portion 20 is combined.
  • the fins 30 are pulled from both sides in the row direction D3 (width direction).
  • the fins 30 are pulled in the column direction D3 (width direction).
  • the tube group which consists of the 1st heat exchanger tube part 10 and the 2nd heat exchanger tube part 20 is inserted in the inlet header 40, the outlet header 50, and the row crossing header 80, respectively.
  • a brazing material is disposed at the joint between each tube group and each header, and brazing in the furnace is performed.
  • FIG. 10 is a cross-sectional view of the heat exchanger 1 in Modification 4 of the present embodiment.
  • the heat transfer units 100 adjacent to each other in the step direction D1 are shifted in the column direction D3.
  • the heat transfer units 100 adjacent to each other in the step direction D1 have a dimension (half pitch) that is half the pitch (row pitch) between the first heat transfer tube portion 10 and the second heat transfer tube portion 20 in the row direction D3. It's off.
  • the first heat transfer tube portion 10 and the second heat transfer tube portion 20 of the heat transfer unit 100 adjacent to each other in the step direction D1 are shifted in the column direction D3.
  • 1st heat exchanger tube part 10 and the 2nd heat exchanger tube part 20 of the heat transfer unit 100 adjacent to the stage direction D1 have not shifted
  • FIG. 6 is a refrigerant circuit diagram of an air-conditioning refrigeration apparatus as an example of the refrigeration cycle apparatus 300 in the present embodiment.
  • the air-conditioning refrigeration apparatus as an example of the refrigeration cycle apparatus 300 of the present embodiment includes a compressor 33, a condensation heat exchanger 34, an expansion device 35, an evaporating heat exchanger 36, A first blower 37 and a second blower 38 are provided.
  • the refrigerant circuit is configured by the compressor 33, the condensing heat exchanger 34, the expansion device 35, and the evaporating heat exchanger 36 being connected via a pipe.
  • the refrigerant circulates through the refrigerant circuit in the order of the compressor 33, the condensation heat exchanger 34, the expansion device 35, and the evaporating heat exchanger 36 as indicated by arrows in the figure.
  • the compressor 33 is configured to compress the refrigerant.
  • the compressor 33 is configured to circulate a refrigerant with the heat exchanger.
  • the condensation heat exchanger 34 functions as a condenser and is configured to condense the refrigerant compressed by the compressor 33.
  • the condensing heat exchanger 34 is provided with a first blower 37.
  • the first blower 37 is configured to adjust the amount of heat exchange between the refrigerant and the air in the condensing heat exchanger 34.
  • the expansion device 35 is configured to depressurize the refrigerant condensed by the condensation heat exchanger 34.
  • the evaporating heat exchanger 36 functions as an evaporator and is configured to evaporate the refrigerant decompressed by the expansion device 35.
  • the evaporative heat exchanger 36 is provided with a second blower 38.
  • the second blower 38 is configured to adjust the amount of heat exchange between the refrigerant and the air in the evaporative heat exchanger 36.
  • the heat exchanger 1 in the present embodiment described above can be used for either or both of the condensation heat exchanger 34 and the evaporation heat exchanger 36.
  • the air-conditioning refrigeration apparatus as an example of the refrigeration cycle apparatus 300 with high energy efficiency can be realized.
  • energy efficiency is constituted by the following equation.
  • Heating energy efficiency indoor heat exchanger (condenser) capacity / total input
  • Cooling energy efficiency indoor heat exchanger (evaporator) capacity / total input
  • coolants such as R410A, R32, HFO1234yf.
  • the heat exchanger 1 in this Embodiment mentioned above is used suitably with an outdoor unit, even when the heat exchanger 1 in this Embodiment mentioned above is used with an indoor unit, there can exist the same effect. it can.
  • the refrigeration cycle apparatus 300 in the present embodiment at least one of the condensation heat exchanger 34 and the evaporation heat exchanger 36 as the heat exchanger 1 and the condensation heat exchanger 34 and the evaporation as the heat exchanger 1 are used. And a compressor 33 that circulates refrigerant between at least one of the heat exchangers 36. For this reason, the refrigerating-cycle apparatus 300 with which manufacture of the heat exchanger 1 is easy can be provided.

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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)

Abstract

L'invention concerne un échangeur thermique (1) pourvu d'une première unité de tuyau de transfert de chaleur (10), d'une seconde unité de tuyau de transfert de chaleur (20) et d'ailettes en forme ondulée (30) ayant des parties de vallée et des parties de crête. Chaque ailette (30) présente une première surface et une deuxième surface. La première unité de tuyau de transfert de chaleur (10) est reliée à des parties de vallée sur la première surface de l'ailette (30). La seconde unité de tuyau de transfert de chaleur (20) est reliée à des parties de crête sur la seconde surface de l'ailette (30). Les parties de vallée et les parties de crête sont disposées dans un agencement parallèle de façon à suivre la direction de courant d'air dans laquelle de l'air s'écoule sur les ailettes (30).
PCT/JP2017/014031 2017-04-04 2017-04-04 Échangeur thermique et dispositif à cycle de réfrigération Ceased WO2018185824A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2019510523A JP6719657B2 (ja) 2017-04-04 2017-04-04 熱交換器および冷凍サイクル装置
PCT/JP2017/014031 WO2018185824A1 (fr) 2017-04-04 2017-04-04 Échangeur thermique et dispositif à cycle de réfrigération

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021014522A1 (fr) * 2019-07-22 2021-01-28 三菱電機株式会社 Échangeur de chaleur, son procédé de production et dispositif de conditionnement d'air
JPWO2020044391A1 (ja) * 2018-08-27 2021-05-13 三菱電機株式会社 熱交換器、熱交換器ユニット、及び冷凍サイクル装置
US11656011B2 (en) * 2019-01-22 2023-05-23 Hitachi Energy Switzerland Ag Condenser

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5618869U (fr) * 1979-07-20 1981-02-19
JPH07218172A (ja) * 1993-12-09 1995-08-18 Sanden Corp 熱交換器およびその製造方法
JP2004263881A (ja) * 2003-01-23 2004-09-24 Showa Denko Kk 伝熱フィン、熱交換器、カーエアコン用エバポレータ及びコンデンサ
JP2006084078A (ja) * 2004-09-15 2006-03-30 Daikin Ind Ltd 細径多管式熱交換器の細径伝熱管ユニット
JP2006162141A (ja) * 2004-12-06 2006-06-22 Matsushita Electric Ind Co Ltd 熱交換器
JP2011190966A (ja) * 2010-03-12 2011-09-29 Denso Corp 熱交換器
JP2015017776A (ja) * 2013-07-12 2015-01-29 株式会社デンソー 熱交換器用フィン

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5618869U (fr) * 1979-07-20 1981-02-19
JPH07218172A (ja) * 1993-12-09 1995-08-18 Sanden Corp 熱交換器およびその製造方法
JP2004263881A (ja) * 2003-01-23 2004-09-24 Showa Denko Kk 伝熱フィン、熱交換器、カーエアコン用エバポレータ及びコンデンサ
JP2006084078A (ja) * 2004-09-15 2006-03-30 Daikin Ind Ltd 細径多管式熱交換器の細径伝熱管ユニット
JP2006162141A (ja) * 2004-12-06 2006-06-22 Matsushita Electric Ind Co Ltd 熱交換器
JP2011190966A (ja) * 2010-03-12 2011-09-29 Denso Corp 熱交換器
JP2015017776A (ja) * 2013-07-12 2015-01-29 株式会社デンソー 熱交換器用フィン

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPWO2020044391A1 (ja) * 2018-08-27 2021-05-13 三菱電機株式会社 熱交換器、熱交換器ユニット、及び冷凍サイクル装置
US11656011B2 (en) * 2019-01-22 2023-05-23 Hitachi Energy Switzerland Ag Condenser
WO2021014522A1 (fr) * 2019-07-22 2021-01-28 三菱電機株式会社 Échangeur de chaleur, son procédé de production et dispositif de conditionnement d'air
JPWO2021014522A1 (ja) * 2019-07-22 2021-11-25 三菱電機株式会社 熱交換器、その製造方法および空気調和装置
CN114174757A (zh) * 2019-07-22 2022-03-11 三菱电机株式会社 热交换器、其制造方法以及空调装置
JP7118279B2 (ja) 2019-07-22 2022-08-15 三菱電機株式会社 熱交換器、その製造方法および空気調和装置
CN114174757B (zh) * 2019-07-22 2023-10-27 三菱电机株式会社 热交换器、其制造方法以及空调装置

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