EP2031334A1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

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Publication number
EP2031334A1
EP2031334A1 EP07744382A EP07744382A EP2031334A1 EP 2031334 A1 EP2031334 A1 EP 2031334A1 EP 07744382 A EP07744382 A EP 07744382A EP 07744382 A EP07744382 A EP 07744382A EP 2031334 A1 EP2031334 A1 EP 2031334A1
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EP
European Patent Office
Prior art keywords
heat exchanger
refrigerant
heat transfer
transfer tubes
airflow
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.)
Granted
Application number
EP07744382A
Other languages
German (de)
English (en)
Other versions
EP2031334B1 (fr
EP2031334A4 (fr
Inventor
Takahiro Ozaki
Ikuhiro Iwata
Masakazu Okamoto
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.)
Daikin Industries Ltd
Original Assignee
Daikin Industries Ltd
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Filing date
Publication date
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Publication of EP2031334A1 publication Critical patent/EP2031334A1/fr
Publication of EP2031334A4 publication Critical patent/EP2031334A4/fr
Application granted granted Critical
Publication of EP2031334B1 publication Critical patent/EP2031334B1/fr
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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
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • 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
    • F28D1/05308—Assemblies of conduits connected side by side or with individual headers, e.g. section type radiators
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/08—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being otherwise bent, e.g. in a serpentine or zig-zag
    • F28D7/082—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being otherwise bent, e.g. in a serpentine or zig-zag with serpentine or zig-zag configuration
    • F28D7/085—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being otherwise bent, e.g. in a serpentine or zig-zag with serpentine or zig-zag configuration in the form of parallel conduits coupled by bent portions
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0229—Double end plates; Single end plates with hollow spaces
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/26—Safety or protection arrangements; Arrangements for preventing malfunction for allowing differential expansion between elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2270/00—Thermal insulation; Thermal decoupling

Definitions

  • the present invention relates to a heat exchanger of an air conditioner that uses CO2 refrigerant.
  • an air conditioner that uses CO2 refrigerant ensures the comfort of heating by raising the discharge air temperature during heating operation close to the compressor discharge temperature.
  • structural improvements to promote heat exchange have been made in a heat exchanger (gas cooler) that includes fins and heat transfer tubes.
  • a method is employed which accelerates the refrigerant flow rate by making the cross section of heat transfer tubes on the downstream side of the refrigerant flow during heating operation smaller than the cross section of other heat transfer tubes, and thereby activates heat transfer from the refrigerant by the effect of turbulent flow (for example, see Patent Document 1).
  • Patent Document 1 JP-A Publication No. H10-176867
  • An object of the present invention is to provide a heat exchanger with improved heat exchange performance.
  • a heat exchanger is a heat exchanger that allows supercritical refrigerant to radiate heat to the air, including a plurality of plate fins and a plurality of heat transfer tubes.
  • Each plate fin has a plurality of through-holes on the planar surface arranged substantially parallel to airflow.
  • the heat transfer tubes are inserted into the through-holes in the plate fins.
  • Four or more rows of heat transfer tubes arranged in the direction crossing the airflow are formed in the upstream-to-downstream direction of the airflow.
  • Each plate fin is divided between at least one pair of adjacent rows.
  • the refrigerant flows from the heat transfer tubes in the row on the downstream side of the airflow to the heat transfer tubes in the row on the upstream side of the airflow.
  • the airflow exchanges heat with higher temperature refrigerant as the airflow moves downstream.
  • each plate fin is divided, heat transfer on the plate fin surface is suppressed, and the difference in temperature between the refrigerant and the air is appropriately maintained throughout the radiation process.
  • the amount of heat exchanged with the airflow increases, and heat exchange performance improves.
  • a heat exchanger according to a second aspect of the present invention is the heat exchanger according to the first aspect of the present invention, wherein each plate fin is divided between all adjacent rows.
  • a heat exchanger according to a third aspect of the present invention is the heat exchanger according to the first aspect of the present invention, wherein each plate fin is divided from one end to the other end.
  • a heat exchanger according to a fourth aspect of the present invention is the heat exchanger according to the first aspect of the present invention, wherein each plate fin is partially divided from one end to the other end.
  • a heat exchanger according to a fifth aspect of the present invention is the heat exchanger according to the first aspect of the present invention, wherein a plurality of passages are formed through which the refrigerant flows from the heat transfer tubes in the row on the downstream side of the airflow to the heat transfer tubes in the row on the upstream side of the airflow.
  • a heat exchanger according to a sixth aspect of the present invention is the heat exchanger according to the first aspect of the present invention, wherein the heat transfer tubes extend in one of the height, width, and depth directions whichever is the shortest dimension.
  • the distance in which the refrigerant moves in the long axis direction of the heat transfer tubes is shortened, and the difference in temperature between the refrigerant and the air is appropriately maintained throughout the radiation process.
  • the amount of heat exchanged with the airflow increases, and heat exchange performance improves.
  • a heat exchanger according to a seventh aspect of the present invention is the heat exchanger according to the first aspect of the present invention, wherein the tube outer diameter of the heat transfer tubes is equal to or less than 4 mm.
  • a heat exchanger according to an eighth aspect of the present invention is the heat exchanger according to the first aspect of the present invention, wherein the refrigerant is CO2.
  • This heat exchanger uses CO2 whose ozone destruction coefficient is low and thus does not lead to the destruction in the air environment.
  • a heat exchanger is the heat exchanger according to the fifth aspect of the present invention, further including a first plate attached to end portions of the plurality of passages, a connecting tube connected to a refrigerant pipe through which the refrigerant circulates, and a wide-mouth container.
  • the wide-mouth container collects the refrigerant that flows out from each end portion of the plurality of passages, or guides the refrigerant that flows out from the connecting tube to each end portion of the plurality of passages.
  • the wide-mouth container is closely attached to the first plate.
  • This heat exchanger is low in cost because there is no need to connect the refrigerant pipe to each end portion of the passages.
  • a heat exchanger according to a tenth aspect of the present invention is the heat exchanger according to the first aspect of the present invention, further including a second plate attached to end portions of the plurality of heat transfer tubes and a third plate having a plurality of depressed portions formed therein for interconnecting the end portions of the appropriate adjacent heat transfer tubes.
  • the third plate is closely attached to the second plate. Consequently, the work to interconnect the end portions of the heat transfer tubes with U-shaped tubes becomes unnecessary, and therefore the cost is low.
  • the airflow exchanges heat with higher temperature refrigerant as the airflow moves downstream.
  • each plate fin is divided, heat transfer on the plate fin surface is suppressed, and the difference in temperature between the refrigerant and the air is appropriately maintained throughout the radiation process.
  • the amount of heat exchanged with the airflow increases, and heat exchange performance improves.
  • the dividing process of the plate fins is simplified, and also a function to suppress heat transfer on the plate fin surface is ensured.
  • the processing cost is reduced and also heat exchange performance improves.
  • the distance of the passages through which the refrigerant flows is optimized, and the difference in temperature between the refrigerant and the air is appropriately maintained throughout the radiation process.
  • the amount of heat exchanged with the airflow increases, and heat exchange performance improves.
  • the flow rate of the refrigerant flowing through the heat transfer tubes is accelerated and the flow of the refrigerant becomes a turbulent flow.
  • the amount of heat exchange between the refrigerant and the heat transfer tubes increases, and heat exchange performance improves.
  • the heat exchanger according to the eighth aspect of the present invention uses CO2 whose ozone destruction coefficient is low and thus does not lead to the destruction in the air environment.
  • the heat exchanger according to the ninth aspect of the present invention is low in cost because there is no need to connect the refrigerant pipe to each end portion of the passages.
  • the heat exchanger according to the tenth aspect of the present invention is low in cost because the work to interconnect the end portions of the heat transfer tubes with U-shaped tubes becomes unnecessary.
  • Figure 1 is a refrigeration circuit of an air conditioner that uses CO2 refrigerant.
  • An air conditioner 1 includes a refrigeration circuit in which a compressor 2, a four way valve 3, an outdoor heat exchanger 4, an expansion valve 5, and an indoor heat exchanger 6 are interconnected via a refrigerant pipe.
  • the solid line arrow and the broken line arrow indicate the flow direction of the refrigerant, and the air conditioner 1 can switch between heating operation and cooling operation by switching the flow direction of the refrigerant by the four way valve 3.
  • the outdoor heat exchanger 4 functions as a gas cooler, and the indoor heat exchanger 6 functions as an evaporator.
  • the outdoor heat exchanger 4 functions as an evaporator, and the indoor heat exchanger 6 functions as a gas cooler.
  • the outdoor heat exchanger 4 and the indoor heat exchanger 6 both include plate fins 11 (see Figure 3 ) and heat transfer tubes 12 (see Figure 3 ). The refrigerant in the heat transfer tubes 12 exchanges heat with the airflow through the plate fms 11.
  • a point A is the suction side of the compressor 2 during heating operation
  • a point B is the discharge side of the compressor 2 during heating operation
  • a point C is the refrigerant outlet side of the indoor heat exchanger 6 during heating operation
  • a point D is the refrigerant inlet side of the outdoor heat exchanger 4 during heating operation.
  • Figure 2(a) is a pressure-enthalpy diagram for CO2 refrigerant.
  • the vertical axis represents pressure P and the horizontal axis represents enthalpy H.
  • a line Tk is the isotherm that passes through a critical point K
  • a line Tx is the isotherm of temperature Tx.
  • Tx is greater than Tk (Tx > Tk), and the CO2 refrigerant will not become liquefied or enter a two-phase state on the right side of the isotherm Tk.
  • the region in which the pressure is equal to or greater than critical pressure Pk on the right side of the isotherm Tk is called a supercritical state.
  • the air conditioner 1 that uses the heat exchanger of the present embodiment is operated in a refrigeration cycle that includes the supercritical state.
  • Points A, B, C, and D in Figure 2(a) represent the states of the refrigerant corresponding to the points A, B, C, and D in Figure 1 .
  • Figure 2(b) is a temperature-entropy diagram for CO2 refrigerant.
  • the vertical axis represents temperature T and the horizontal axis represents entropy S.
  • Points A, B, C, and D in Figure 2(b) represent the states of the refrigerant corresponding to the points A, B, C, and D in Figure 1 .
  • the temperature of the refrigerant drops from the point B on the discharge side of the compressor 2 to the point C on the refrigerant outlet side of the indoor heat exchanger 6. Accordingly, the temperature distribution on the surface of the indoor heat exchanger 6 is such that the temperature on the upstream side of the refrigerant flow is higher and the temperature on the downstream side thereof is lower.
  • the difference in temperature between the air and the indoor heat exchanger 6 becomes more stabilized when the airflow passes from the downstream side of the refrigerant to the upstream side of the refrigerant, and the amount of heat exchange between the air and the indoor heat exchanger 6 increases.
  • FIG 3 is a perspective view to show the structure of the indoor heat exchanger according to the embodiment of the present invention.
  • the indoor heat exchanger 6 is a cross fin-type heat exchanger.
  • the plate fins 11 are thin and flat plates made of aluminum, and each plate fin 11 has a plurality of the through-holes 11 a formed therein.
  • Each heat transfer tube 12 includes a straight tube 12a to be inserted through the through-holes 11a in the plate fins 11, and U-shaped tubes 12b and 12c that interconnect the end portions of the adjacent the straight tubes 12a.
  • each heat transfer tube 12 in the present embodiment are integrally formed, and the U-shaped tube 12c is connected to the end portion of the straight tube 12a by welding or the like after the straight tube 12a is inserted into the through-holes 11 a in the plate fins 11.
  • Figure 4 is a configuration view of passages of the indoor heat exchanger according to the embodiment of the present invention.
  • the solid lines in Figure 4 represent the U-shaped tubes 12b on the front side of the figure, and the broken lines represent the U-shaped tubes 12c on the opposite side.
  • the refrigerant flows separately into the six heat transfer tubes 12 in the row 72 and flows out from the six heat transfer tubes 12 in the row 61 through six passages 81 to 86. In this way, because the refrigerant circulates separately through the plurality of passages 81 to 86, the difference in temperature between the refrigerant and the air is appropriately maintained throughout the radiation process, and the amount of heat exchanged with the airflow increases.
  • Each plate fin 11 is divided between the row 61 and the row 62. Each plate fin 11 is also divided between the following rows: the row 63 and the row 64; the row 65 and the row 66; the row 67 and the row 68; the row 69 and the row 70; and the row 71 and the row 72. Thereby, the heat on the surface of the plate fins 11 is prevented from transferring over divided portions 13. Thus, the surface temperature on the plate fins 11 is maintained high and the amount of heat exchanged with the airflow increases.
  • the direction in which the straight tubes 12a of the heat transfer tubes 12 extend is the depth of the indoor heat exchanger 6.
  • the depth is the shortest dimension among the height, width, and depth.
  • the tube outer diameter of the heat transfer tubes 12 is equal to or less than 4 mm such that the flow of the refrigerant in the heat transfer tubes 12 becomes turbulent flow.
  • FIG. 5 is a longitudinal cross sectional view of an indoor unit that uses the indoor heat exchanger according to the embodiment of the present invention.
  • An indoor unit 101 has the indoor heat exchanger 6 mounted in a casing 102.
  • a fan 103 is arranged above the indoor heat exchanger 6, and an air discharge port 102a is provided above the fan 103.
  • An air suction inlet 102b is provided below the indoor heat exchanger 6.
  • the indoor heat exchanger 6 has a first header 14 attached on the upstream side of the airflow for dividing and guiding the refrigerant to each inlet of the passages 81 to 86.
  • the indoor heat exchanger 6 has a second header 15 attached on the downstream side of the airflow for guiding the refrigerant that flows out from each outlet of the passages 81 to 86 to the refrigerant pipe.
  • the indoor unit 101 can provide comfortable heating.
  • the indoor heat exchanger 6 is a heat exchanger that allows supercritical CO2 refrigerant to radiate heat to the air, and includes the plurality of plate fins 11 and the plurality of heat transfer tubes 12.
  • Each plate fin 11 has the plurality of through-holes 11a on the planar surface arranged substantially parallel to the airflow.
  • the heat transfer tubes 12 are inserted into the through-holes 11 a in the plate fins 11.
  • Four or more rows 61 to 72 of the heat transfer tubes 12 arranged in the direction crossing the airflow are formed in the upstream-to-downstream direction of the airflow.
  • Each plate fin 11 is divided between at least one pair of adjacent rows 61 and 62.
  • the refrigerant flows from the heat transfer tubes 12 in the row 72 on the downstream side of the airflow to the heat transfer tubes 12 in the row 61 on the upstream side of the airflow.
  • the airflow exchanges heat with higher temperature refrigerant as the airflow moves downstream.
  • each plate fin 11 is divided, heat transfer on the surface of the plate fins 11 is suppressed, and the difference in temperature between the refrigerant and the air is appropriately maintained throughout the radiation process.
  • the amount of heat exchanged with the airflow increases, and heat exchange performance improves.
  • This indoor heat exchanger 6 has the plurality of passages 81 to 86 formed for allowing the refrigerant to flow from the heat transfer tubes 12 in the row 72 on the downstream side of the airflow to the heat transfer tubes 12 in the row 61 on the upstream side of the airflow.
  • the heat transfer tubes extend in one of the height, width, and depth directions of the indoor heat exchanger 6 whichever is the shortest dimension.
  • the distance of the straight tubes 12a of the heat transfer tubes 12 is shortened, a decrease in temperature of the refrigerant is suppressed, and the difference in temperature between the refrigerant and the air is appropriately maintained throughout the radiation process.
  • the amount of heat exchanged with the airflow increases, and heat exchange performance improves.
  • the tube outer diameter of the heat transfer tubes 12 is equal to or less than 4 mm.
  • the flow rate of the refrigerant flowing through the heat transfer tubes 12 is accelerated and the flow of the refrigerant becomes a turbulent flow.
  • the amount of heat exchange between the refrigerant and the heat transfer tubes 12 increases, and heat exchange performance improves.
  • FIG 6 is a perspective view of an indoor heat exchanger according to a first alternative embodiment of the embodiment of the present invention.
  • Plates 31 and 32 are attached to the end portions, i.e., inlet and outlet, of the plurality of passages 81 to 86 (see Figure 4 ), and the plates 31 and 32 are more rigid than the plate fins 11.
  • An inlet side header 91 includes a connecting tube 91a connected to the refrigerant pipe, and a wide-mouth container 91b that covers the inlets of the plurality of passages 81 to 86. The inlet side header 91 is closely bonded to the plate 31.
  • An outlet side header 92 includes a connecting tube 92a connected to the refrigerant pipe, and a wide-mouth container 92b that covers the outlets of the plurality of passages 81 to 86.
  • the outlet side header 92 is closely bonded to the plate 32.
  • a plate 33 is attached to the end portions of the heat transfer tubes 12 as a whole and is more rigid than the plate fins 11.
  • the plate 33 has a plate 93 closely bonded thereto.
  • Figure 7(a) is a rear view of the first alternative embodiment
  • Figure 7(b) is a cross sectional view taken along line D-D of Figure 7(a)
  • Figure 7(c) is a cross sectional view taken along line E-E of Figure 7(a) .
  • the plate 93 in the figure has a plurality of depressed portions 93a each interconnecting the end portions of the heat transfer tubes 12.
  • the depressed portions 93a correspond to the U-shaped tubes 12c of the embodiment shown in Figure 3 .
  • the plurality of depressed portions 93a are formed by drawing the plate 93, and therefore it is economical.
  • This indoor heat exchanger 6 further includes the plates 31 and 32 attached to the end portions of the plurality of passages 81 to 86; the connecting tubes 91a and 92a connected to the refrigerant pipe through which the refrigerant circulates; and the wide-mouth containers 91 b and 92b.
  • the wide-mouth containers 91 b and 92b collect the refrigerant that flows out from each end portion of the plurality of passages 81 to 86 to the connecting tubes 91a and 92a, or guide the refrigerant that flows out from the connecting tubes 91a and 92a to each end portion of the plurality of passages 81 to 86.
  • the wide-mouth containers 91 b and 92b are closely attached to the plates 31 and 32. Consequently, there is no need to connect the refrigerant pipe to each end portion of the passages 81 to 86, and therefore the cost is low.
  • This indoor heat exchanger 6 further includes the plate 33 attached to the end portions of the plurality of the heat transfer tubes 12; and the plate 93 having the plurality of depressed portions 93a formed therein for interconnecting the end portions of the heat transfer tubes 12.
  • the plate 93 is closely attached to the plate 33. Consequently, the work to interconnect the end portions of the heat transfer tubes 12 with U-shaped tubes becomes unnecessary, and therefore the cost is low.
  • Figure 8 is a configuration view of the indoor heat exchanger in Figure 4 with the passages being modified. Similar to Figure 4 , the solid lines in Figure 4 represent the U-shaped tubes 12b on the front side of the figure, and the broken lines represent the U-shaped tubes 12c on the opposite side.
  • the refrigerant that flowed into the heat transfer tubes 12 in the row 72 of passages 87 to 89 flows to the respective adjacent heat transfer tubes 12 in the same row 72; then flows to the heat transfer tubes 12 in the row 71 disposed further upstream of the airflow by one row; subsequently flows to the respective adjacent heat transfer tubes 12 in the same row 71; then further flows to the heat transfer tubes 12 in next row 70 disposed further upstream of the airflow by one row.
  • the refrigerant flows to the heat transfer tubes 12 in the row 61 on the most upstream side of the airflow while changing the direction of the flow.
  • Figure 9 is a configuration view of the indoor heat exchanger in Figure 4 with the pitch of the heat transfer tubes and the plate fins being modified
  • Figure 10 is a configuration view of the indoor heat exchanger in Figure 8 with the pitch of the heat transfer tubes and the plate fins being modified.
  • the heat transfer tubes 12 are arranged at the same pitch therebetween in the vertical direction.
  • a plate fin 21 is partially divided by slits 23 in the substantially middle of the pitch and also between all adjacent rows 61 to 72.
  • the slits 23 are formed by a single perforation per plate fin 11, and therefore the processing cost is reduced.
  • the present invention has a good heat exchange performance, and is useful for a heat exchanger of an air conditioner that uses CO2 refrigerant.

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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)
EP07744382.8A 2006-05-31 2007-05-30 Échangeur de chaleur Active EP2031334B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2006152488A JP4760542B2 (ja) 2006-05-31 2006-05-31 熱交換器
PCT/JP2007/060968 WO2007139137A1 (fr) 2006-05-31 2007-05-30 Échangeur de chaleur

Publications (3)

Publication Number Publication Date
EP2031334A1 true EP2031334A1 (fr) 2009-03-04
EP2031334A4 EP2031334A4 (fr) 2014-01-15
EP2031334B1 EP2031334B1 (fr) 2020-07-08

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ID=38778655

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07744382.8A Active EP2031334B1 (fr) 2006-05-31 2007-05-30 Échangeur de chaleur

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EP (1) EP2031334B1 (fr)
JP (1) JP4760542B2 (fr)
WO (1) WO2007139137A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130240177A1 (en) * 2012-03-13 2013-09-19 Blissfield Manufacturing Company Nested heat exchanger
CN103392109A (zh) * 2011-02-23 2013-11-13 大金工业株式会社 空调机用热交换器
EP3040671A1 (fr) * 2013-08-28 2016-07-06 Mitsubishi Heavy Industries, Ltd. Refroidisseur d'air, dispositif de refroidissement et installation nucléaire
US10670311B2 (en) 2015-05-29 2020-06-02 Hitachi-Johnson Controls Air Conditioning, Inc. Heat exchanger

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2017036900A (ja) * 2015-08-13 2017-02-16 三菱重工業株式会社 放熱器およびそれを用いた超臨界圧冷凍サイクル
US20220049869A1 (en) * 2018-12-04 2022-02-17 Mitsubishi Electric Corporation Air-conditioning apparatus
KR102660705B1 (ko) * 2022-12-29 2024-04-26 고려대학교 산학협력단 열교환기

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JPS6312081U (fr) * 1986-07-11 1988-01-26
JPH10274490A (ja) * 1997-03-28 1998-10-13 Kimura Kohki Co Ltd プレートフィンコイル
US20020023744A1 (en) * 1999-12-10 2002-02-28 Kwang-Il Kim Manufacturing method for split heat exchanger having oval tubes in zigzag pattern
JP2005098672A (ja) * 2003-09-03 2005-04-14 Toyo Radiator Co Ltd チューブレス熱交換器

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JP3540530B2 (ja) 1996-12-13 2004-07-07 東芝キヤリア株式会社 空気調和装置
JP2000304380A (ja) * 1999-04-22 2000-11-02 Aisin Seiki Co Ltd 熱交換器

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JPS6312081U (fr) * 1986-07-11 1988-01-26
JPH10274490A (ja) * 1997-03-28 1998-10-13 Kimura Kohki Co Ltd プレートフィンコイル
US20020023744A1 (en) * 1999-12-10 2002-02-28 Kwang-Il Kim Manufacturing method for split heat exchanger having oval tubes in zigzag pattern
JP2005098672A (ja) * 2003-09-03 2005-04-14 Toyo Radiator Co Ltd チューブレス熱交換器

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See also references of WO2007139137A1 *

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10048018B2 (en) 2011-02-23 2018-08-14 Daikin Industries, Ltd. Heat exchanger for air conditioner
CN103392109A (zh) * 2011-02-23 2013-11-13 大金工业株式会社 空调机用热交换器
EP2674717A1 (fr) * 2011-02-23 2013-12-18 Daikin Industries, Ltd. Échangeur de chaleur pour climatiseur
EP2674717A4 (fr) * 2011-02-23 2014-01-01 Daikin Ind Ltd Échangeur de chaleur pour climatiseur
AU2012221582B2 (en) * 2011-02-23 2015-05-14 Daikin Industries, Ltd. Heat exchanger for air conditioner
CN103392109B (zh) * 2011-02-23 2015-11-25 大金工业株式会社 空调机用热交换器
US20130240177A1 (en) * 2012-03-13 2013-09-19 Blissfield Manufacturing Company Nested heat exchanger
EP3040671A1 (fr) * 2013-08-28 2016-07-06 Mitsubishi Heavy Industries, Ltd. Refroidisseur d'air, dispositif de refroidissement et installation nucléaire
EP3040671A4 (fr) * 2013-08-28 2017-05-03 Mitsubishi Heavy Industries, Ltd. Refroidisseur d'air, dispositif de refroidissement et installation nucléaire
US10319482B2 (en) 2013-08-28 2019-06-11 Mitsubishi Heavy Industries, Ltd. Air cooler, intercooler and nuclear facility
US11289218B2 (en) 2013-08-28 2022-03-29 Mitsubishi Heavy Industries, Ltd. Air cooler, intercooler and nuclear facility
US11289217B2 (en) 2013-08-28 2022-03-29 Mitsubishi Heavy Industries, Ltd. Intercooler for nuclear facility
US10670311B2 (en) 2015-05-29 2020-06-02 Hitachi-Johnson Controls Air Conditioning, Inc. Heat exchanger

Also Published As

Publication number Publication date
JP2007322060A (ja) 2007-12-13
EP2031334B1 (fr) 2020-07-08
JP4760542B2 (ja) 2011-08-31
WO2007139137A1 (fr) 2007-12-06
EP2031334A4 (fr) 2014-01-15

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