WO2008007694A1 - Échangeur de chaleur de type à ailettes et tubes, et son tube de retour coudé - Google Patents

Échangeur de chaleur de type à ailettes et tubes, et son tube de retour coudé Download PDF

Info

Publication number
WO2008007694A1
WO2008007694A1 PCT/JP2007/063807 JP2007063807W WO2008007694A1 WO 2008007694 A1 WO2008007694 A1 WO 2008007694A1 JP 2007063807 W JP2007063807 W JP 2007063807W WO 2008007694 A1 WO2008007694 A1 WO 2008007694A1
Authority
WO
WIPO (PCT)
Prior art keywords
groove
tube
return bend
hairpin
pipe
Prior art date
Application number
PCT/JP2007/063807
Other languages
English (en)
Japanese (ja)
Inventor
Hiroyuki Takahashi
Tsuneo Haba
Akihiko Ishibashi
Original Assignee
Kobelco & Materials Copper Tube, Ltd.
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 Kobelco & Materials Copper Tube, Ltd. filed Critical Kobelco & Materials Copper Tube, Ltd.
Priority to EP07790611.3A priority Critical patent/EP2042825B1/fr
Priority to CN2007800213773A priority patent/CN101466992B/zh
Publication of WO2008007694A1 publication Critical patent/WO2008007694A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • 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
    • 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
    • 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
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • 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
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • 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
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F28F1/422—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element with outside means integral with the tubular element and inside means integral with the tubular element
    • 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
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/09—Improving heat transfers
    • 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
    • F28F9/0246—Arrangements for connecting header boxes with flow lines

Definitions

  • the present invention is a heat exchanger such as an air conditioner, and in particular, a refrigerant such as a chlorofluorocarbon refrigerant or a natural refrigerant is allowed to flow inside the pipe, and a large number of fins formed of aluminum or the like are installed in parallel on the outer surface of the pipe.
  • a refrigerant such as a chlorofluorocarbon refrigerant or a natural refrigerant is allowed to flow inside the pipe, and a large number of fins formed of aluminum or the like are installed in parallel on the outer surface of the pipe.
  • the fin-and-tube heat exchanger and the return bend pipe connected to the hairpin pipe.
  • Patent Document 1 or Patent Document 2 proposes a fin-and-tube heat exchanger using a smooth tube having a smooth inner surface as a return bend tube and an inner grooved tube as a hairpin tube.
  • the return bend pipe is described as a U-bend pipe
  • the hairpin pipe is described as an electric sewing pipe.
  • Patent Document 2 the return bend pipe is described as a U-bend pipe
  • the hairpin pipe is described as a heat transfer pipe.
  • Patent Document 3 proposes a fin-and-tube heat exchanger for an evaporator (evaporator) using an internally grooved tube as a return bend tube and a smooth tube as a hairpin tube.
  • a return bend pipe is described as a U-bend pipe
  • a hairpin pipe is described as a tube.
  • Patent Document 4 discloses a fin-and-tube heat exchanger using inner grooved tubes for both the return bend tube and the hairpin tube.
  • Patent Document 1 Japanese Utility Model Publication No. 63-154986 (Example, FIGS. 1 to 4)
  • Patent Document 2 JP-A-11-190597 (paragraphs 0022 to 0026, FIG. 1)
  • Patent Document 3 Japanese Utility Model Publication No. 4-122986 (paragraphs 0007 to 0008, FIG. 1)
  • Patent Document 4 Japanese Unexamined Patent Publication No. 2006-98033 (Claim 1, FIG. 4) Disclosure of the invention
  • the non-uniform refrigerant liquid film means that the liquid film thickness becomes non-uniform, and if the liquid film thickness is non-uniform, the thick part of the liquid film A state difference (a function of the surface tension of the refrigerant liquid film and the curvature of the liquid film) occurs in the thin part.
  • this state difference occurs, in principle, a liquid film with a thin refrigerant liquid film is pulled in a direction where the refrigerant liquid film is thicker. The thin part of the liquid film becomes thinner, and evaporation is promoted in this part, while the thick part of the refrigerant liquid film remains. The remaining refrigerant liquid film results in a dry-out state except for the remaining portion, which reduces the effective heat transfer area and lowers the evaporation performance.
  • the present invention has been made in view of the above problems, and it is an object of the present invention to provide a fin-and-tube heat exchanger that can further improve the evaporation performance of the heat exchanger and its return bend pipe. Say it.
  • a first aspect of the present invention provides a hairpin portion in which a large number of hairpin tubes are arranged in parallel, and a retarder in which a large number of return bend tubes joined to the hairpin tube ends of the hairbin portions are arranged in parallel.
  • a fin-and-tube heat exchanger having a bent portion and a fin portion composed of a large number of fins arranged in parallel at regular intervals on the outer surface of the hairpin tube, wherein a refrigerant is supplied into the tube,
  • Groove pitch ratio (P1 / P2) satisfies 0.665-2.
  • / S2 is configured as a fin-and-tube heat exchanger satisfying 0.3 to 3.6.
  • the predetermined first groove is formed on the inner surface of the return bend pipe of the fin-and-tube heat exchanger, so that the refrigerant liquid film is flattened on the return bend pipe inlet side. Furthermore, an “annular flow” can be formed in the refrigerant liquid film inside the pipe, and the disturbance of the refrigerant liquid film in the return bend pipe can be reduced.
  • a uniform “annular flow” is formed inside the tube, and the liquid film in the straight portion of the hairpin tube becomes uniform.
  • heat exchange with the outside of the tube is stabilized and evaporation performance is improved.
  • a second groove lead angle ( ⁇ 2) formed by the second groove of the hairpin tube and the tube axis is 15 ° or more.
  • At least a part of the refrigerant flow path constituted by the hairpin tube and the return bend pipe is branched to form a plurality of refrigerant flow paths.
  • the refrigerant flow rate of the fin-and-tube heat exchanger is branched, so that the refrigerant mass velocity per branch is lowered, and in particular, the refrigerant velocity at the return bend pipe inlet side is lowered.
  • the “annular flow” of the refrigerant liquid film formed inside the pipe is further stabilized.
  • a uniform “annular flow” is formed inside the tube, and the liquid film of the refrigerant becomes uniform in the straight portion of the hairpin tube. The heat exchange with the outside of the tube is stabilized and the evaporation performance is further improved.
  • the refrigerant is a hydrated fluorocarbon non-azeotropic refrigerant mixture.
  • the evaporation performance of the heat exchanger is further improved, and the pressure loss of the refrigerant is reduced.
  • a second aspect of the present invention is a fin-and-tube heat exchange which is joined to a tube end of a hepin tube provided with a large number of fins arranged in parallel at regular intervals on an outer surface, and a refrigerant is supplied into the tube.
  • a refrigerant is supplied into the tube.
  • Groove pitch ratio (P1 / P2) satisfies 0.665-2.
  • the first groove cross-sectional area (S1) per groove in the cross section perpendicular to the tube axis of the first groove and the second cross-sectional area (S2) per groove in the cross section perpendicular to the tube axis of the second groove It is constructed as a return bend pipe that satisfies the groove cross-sectional area ratio (S1 / S2) of 0.3 to 3.6.
  • the groove pitch ratio (P1 / P2) and the groove cross-sectional area ratio (S1 / S2) are predetermined.
  • the “swirl flow” of the liquid refrigerant formed in the hairpin tube is maintained even in the return bend tube.
  • the coolant liquid film can be flattened on the return bend tube inlet side, and the coolant liquid film inside the tube becomes uniform. Flow "can be formed. As a result, the disturbance of the refrigerant liquid film inside the return bend pipe is reduced.
  • the groove depth ratio (hl / h2) within a predetermined range, it is difficult for the refrigerant liquid film to be disturbed, which makes it difficult for the refrigerant to detach inside the pipe.
  • a uniform “annular flow” is formed inside the pipe, and the liquid film of the refrigerant in the straight pipe portion of the hairpin pipe is uniform. Therefore, heat exchange with the outside of the tube is stabilized, and the evaporation performance is further improved.
  • the foot length of the return bend pipe (U is preferably 1.0 to 1.5 times the pitch (P)).
  • the leg length of the return bend tube (U is set to a predetermined multiple of the bending pitch (P).
  • P the bending pitch
  • the “circular flow” is sufficiently formed in the refrigerant liquid film in the straight pipe part up to the bent part, and the refrigerant liquid film in the bent part of the return bend pipe is disturbed ( Peeling flow) Does not occur.
  • the “annular flow” flows in, forming a uniform liquid film in the straight portion of the hairpin tube, and heat exchange with the outside of the tube. The conversion is stabilized and the evaporation performance is further improved.
  • the material of the return bend tube is preferably made of a material having a lower thermal conductivity than the material of the hairpin tube.
  • the heat conductivity of the tube main body is lower than that of the hairpin tube, thereby suppressing heat loss in the return bend tube.
  • Reducing the heat loss in the return bend pipe causes the refrigerant liquid film to splash due to the evaporation of the refrigerant inside the return bend pipe or the collapse of the “annular flow” of the refrigerant liquid film. Disturbance (separated flow) does not occur.
  • the “annular flow” flows in, forming a uniform liquid film in the straight tube portion of the hairpin tube, and heat from the outside of the tube. Exchange is stabilized and evaporation performance is further improved.
  • the material of the return bend tube is preferably made of a copper alloy that is more heat resistant than the material of the hairpin tube.
  • the first maximum inner diameter (ID1) of the return bend tube is preferably (ID1) ⁇ (ID2) in relation to the second maximum inner diameter (ID2) of the hairpin tube.
  • the fin-and-tube heat exchanger of the first aspect of the present invention it is possible to improve the evaporation performance of the heat exchanger by using the return bend pipe.
  • the ring is formed on the refrigerant liquid film inside the pipe.
  • the refrigerant liquid film in the straight portion of the hairpin tube becomes uniform, and the evaporation performance of the heat exchanger can be improved.
  • the evaporation performance of the heat exchanger can be further improved. It becomes possible.
  • FIG. 1 is a perspective view showing a configuration of a return bend pipe according to the present invention.
  • FIG. 2 is a partially broken front view showing an example of a fin-and-tube heat exchanger incorporating a return bend pipe according to the present invention.
  • FIG. 3 (a) is a perspective view of the heat exchanger of FIG. 2 as viewed from the return bend tube side, (b) is a perspective view of the heat exchanger as viewed from the hairpin tube side, and (c) is the inside of the heat exchanger.
  • FIG. 6 is a schematic diagram schematically showing the flow of the refrigerant.
  • FIG. 4 is an enlarged end view when cut in the tube axis direction showing an example of a joint portion between a hairpin tube and a return bend tube.
  • FIG. 5 (a) is an end view perpendicular to the axis of the return bend pipe, and (b) is a partially enlarged end view of (a).
  • FIG. 6 (a) is an end view of the hairpin tube perpendicular to the tube axis, and (b) is a partially enlarged end view of (a).
  • FIG. 7] (a) and (b) are schematic views schematically showing the flow of refrigerant in a heat exchanger according to another embodiment of the present invention.
  • FIG. 8 (a) is a schematic diagram of a suction type wind tunnel used for measuring the evaporation performance of a heat exchanger, and (b) is a schematic diagram of a refrigerant supply device for supplying refrigerant to the suction type wind tunnel of (a). It is.
  • FIG. 1 shows the return bend pipe
  • Fig. 2 is a partially broken front view showing an example of a fin-and-tube heat exchanger incorporating a return bend tube.
  • Fig. 3 (a) shows the heat exchanger of Fig. 2 on the return bend tube side.
  • (B) is a perspective view of the heat exchanger as viewed from the hairpin tube side,
  • (c) is a schematic diagram schematically showing the flow of refrigerant in the heat exchanger, and
  • FIG. Fig. 5 (a) is an enlarged end view when cut in the tube axis direction showing an example of a joint with the return bend pipe, Fig.
  • Fig. 5 (a) is a pipe bend orthogonal end view of the return bend pipe, and (b) is a part of (a).
  • Fig. 6 (a) is an end view orthogonal to the axis of the hairpin tube, (b) is a partially enlarged end view of (a), and
  • Figs. 7 (a) and (b) are heat exchanges of other embodiments.
  • Fig. 8 (a) is a schematic diagram of the refrigerant flow in the exchanger.
  • Fig. 8 (a) is a schematic diagram of a suction wind tunnel used to measure the evaporation performance of the heat exchanger.
  • (B) is a schematic diagram of (a).
  • Supply refrigerant to suction type wind tunnel It is a schematic diagram of a medium supply device.
  • the return bend pipe 1 of the present invention is used in a fin-and-tube heat exchanger (hereinafter referred to as a heat exchanger) 20 and a hairpin for supplying refrigerant to the inside of the pipe. It is joined to the pipe end of the pipe 11.
  • This return bend pipe 1 is formed on a pipe body la formed in a U-shape, a pipe end lb connected to the hairpin pipe 11 at the pipe end of the pipe body la, and an inner surface of the pipe body la.
  • a number of first grooves 2 are provided (see FIG. 4; the description of the first groove is omitted in FIG. 1).
  • the return bend tube 1 is interposed between the two hairpin tubes 11 and 11 and connects the hairpin tubes 11 to each other, as shown in FIG. 2, a plurality of hairpin tubes 11 and 11 are connected in series. By connecting to, a long-distance refrigerant flow path is formed.
  • the return bend pipe 1 incorporates the return bend pipe 1 by restricting the inner groove shape of the first groove 2 formed on the inner surface of the pipe as follows.
  • the evaporation performance of the heat exchanger 20 (see Fig. 2 and Fig. 3) can be improved.
  • the return bend pipe 1 uses 3 to 10 mm as the outer diameter of the hairpin pipe 11 to be joined (second outer diameter OD2), the outer diameter of the pipe (first outer diameter OD1) is It is preferable to use a 3 to 1 Omm tube that is the same as a hairpin tube!
  • the first groove 2 of the return bend pipe 1 has the first groove pitch (P1) in the cross section perpendicular to the pipe axis,
  • the groove pitch ratio (P1 / P2) to the second groove pitch (P2) in the cross section perpendicular to the tube axis of the spiral second groove 12 formed on the inner surface of the hairpin tube 11 satisfies 0.665-2.
  • the first groove cross-sectional area (S1) per groove in the cross section perpendicular to the pipe axis of the first groove 2 and the second cross-sectional area per groove in the cross section perpendicular to the pipe axis of the second groove 12 ( The groove cross-sectional area ratio (S1 / S2) with S2) must satisfy 0.3 to 3.6.
  • the groove cross-sectional area ratio (S1 / S2) is more preferably 0.54-2.7.
  • the reason for limiting the numerical values of the groove pitch ratio (P1 / P2) and the groove cross-sectional area ratio (S1 / S2) will be described below.
  • the groove pitch ratio (P1 / P2) is less than 0.65, the number of grooves in the return bend pipe 1 that occupy one groove in the hairpin pipe 11 increases, so that the liquid refrigerant flows from the hairpin pipe 11 to the return bend pipe 1. Flows into the refrigerant liquid film inside the pipe (first groove 2) on the return bend pipe inlet side, and the refrigerant liquid film is disturbed. Then, when the liquid refrigerant flows into the hairpin tube 11 at the next stage, the refrigerant liquid film flows in a turbulent state, and a thick portion is formed in the refrigerant liquid film at the straight tube portion of the hairpin tube, and heat exchange with the outside of the tube is performed. It becomes unstable and the evaporation performance decreases.
  • the groove cross-sectional area ratio (S1 / S2) is less than 0.3, when the liquid refrigerant flows from the hairpin tube 11 into the return bend tube 1, the cross-sectional area of the first groove 2 is greatly reduced, so that the return bend The refrigerant liquid film contracts on the pipe inlet side, and the refrigerant liquid film is disturbed. Then, when the liquid refrigerant flows into the next-stage air pipe 11, the refrigerant liquid film flows in a turbulent state, resulting in a thick portion of the refrigerant liquid film in the straight tube portion of the hairpin tube 11, and the outside of the tube. Heat exchange becomes unstable and evaporation performance decreases.
  • the first groove 2 of the return bend tube 1 has a first groove lead angle ( ⁇ 1) formed by the first groove 2 and the tube axis, and a hairpin tube 11
  • the angle difference ( ⁇ : ⁇ _ ⁇ 2) between the second groove 12 formed on the inner surface of the tube and the second groove lead angle ( ⁇ 2) formed by the tube axis satisfies ⁇ 15 to + 15 °, and Groove depth ratio (hl / h2) between the first groove depth (hi) in the cross section perpendicular to the pipe axis of the first groove 2 and the second groove depth (h2) in the cross section perpendicular to the pipe axis of the second groove 12 ) Is preferably between 0.47 and 1.5;
  • the first groove 2 includes the case where the first groove lead angle ( ⁇ 1) is 0 °, that is, the first groove 2 is parallel to the tube axis. The reason for limiting the numerical values of the angle difference ( ⁇ 1- ⁇ 2) and the groove depth ratio (hl / h
  • the angle difference ( ⁇ 1- ⁇ 2) is less than -15 °, that is, the first groove lead angle ( ⁇ 1) is smaller than (second groove lead angle ( ⁇ 2) -15 °)
  • the return bend pipe inlet side the coolant liquid film splashes from the peak of the first fin 3 formed between the first grooves 2, and turbulence (separation flow) occurs in the coolant liquid film.
  • the refrigerant liquid film flows in a turbulent state, resulting in a thick portion of the refrigerant liquid film in the straight tube portion of the hairpin tube 11, and heat exchange with the outside of the tube becomes unstable and the evaporation performance tends to decrease.
  • the direction of the first groove lead angle ( ⁇ 1) formed by the first groove 2 and the tube axis is the second groove formed by the second groove 12 formed on the tube inner surface of the hairpin tube 11 and the tube axis. It is preferably formed in the same direction as the direction of the groove lead angle ( ⁇ 2). If the direction of the first groove lead angle ( ⁇ 1) and the direction of the second groove lead angle ( ⁇ 2) are different, the pressure loss of the refrigerant in the return bend pipe 1 becomes large, and the evaporation performance tends to deteriorate.
  • the groove depth ratio (hl / h2) is smaller than 0.47, the refrigerant liquid film in the first groove 2 is released immediately on the return bend pipe inlet side, and the liquid droplet of the refrigerant liquid film is formed immediately. Disturbance (separated flow) occurs. Then, when the liquid refrigerant flows into the hairpin tube 11 in the next stage, the refrigerant liquid film flows in a turbulent state, and a thick portion is formed in the refrigerant liquid film in the straight tube portion of the hairpin tube 11, and heat exchange with the outside of the tube becomes unstable and the evaporation performance tends to decrease.
  • the first groove 2 of the return bend pipe 1 includes the first fin peak angle ( ⁇ 1) and the first fin root radius (rl) force of the first fin 3 formed between the first grooves 2.
  • S more preferably formed so as to be the same as the second fin peak angle ( ⁇ 2) and the second fin root radius (r2) of the second fin 13 formed between the second grooves 12 of the hairpin tube 11.
  • the first fin peak angle ( ⁇ 1) is 4.5 to 45 °
  • the first fin root radius (rl) is 1/12 to 1/2 of the first groove depth (hi).
  • the first fin peak angle ( ⁇ ⁇ ) is 4.5 to 28.5 °
  • the first fin root radius (rl) is 1/12 to the first groove depth (hi); 1/4 is optimal. It is. This further maintains the formation of the “annular flow” of the refrigerant liquid film in the return bend pipe 1.
  • the resistance decreases due to the increase in the cross-sectional area of the first groove 2 when the liquid refrigerant flows into the return bend pipe 1 from the hairpin pipe 11.
  • the groove bottom width of the first groove 2 is widened, the retention of the refrigerant liquid film is deteriorated, and the formation of the “annular flow” is easily broken, and the refrigerant liquid film is disturbed.
  • the refrigerant liquid film flows in a turbulent state, and a thick portion is generated in the cooling liquid film in the straight tube portion of the hairpin tube 11, and the outside of the tube is disconnected. Heat exchange becomes unstable and evaporation performance tends to decrease.
  • the cross-sectional area of the first groove 2 decreases when the liquid refrigerant flows from the hairpin tube 11 into the return bend tube 1.
  • the refrigerant liquid film contracts immediately on the return bend pipe inlet side, and the refrigerant liquid film is disturbed immediately.
  • the refrigerant liquid film is likely to flow in a turbulent state, and a thick portion is formed in the refrigerant liquid film in the straight tube portion of the hairpin tube 11, and the outside of the tube is Heat exchange becomes unstable, and evaporation performance tends to decrease.
  • the cross-sectional area of the first groove 2 increases when the liquid refrigerant flows from the hairpin tube 11 into the return bend tube 1.
  • the resistance is reduced by the above, conversely, because the groove bottom width of the first groove 2 widens, the retention of the refrigerant liquid film decreases, and the formation of the "annular flow” tends to collapse, and the refrigerant liquid film is disturbed. .
  • the refrigerant liquid film flows in a turbulent state, resulting in a thick portion of the refrigerant liquid film in the straight tube portion of the hairpin tube 11, and the outside of the tube. Heat exchange becomes unstable and evaporation performance tends to decrease.
  • the return bend pipe 1 (pipe body la) preferably has a foot length (U is 1 ⁇ 0 to; 5 times the pitch (P). Note that the foot length (U is U-shaped) In the pipe-shaped main part la, the distance between the pipe end 1 b and the outer surface of the bent tip part, and the pitch (P) is the distance between the center of both pipe ends in the U-shaped pipe main part 1 a. Distance.
  • the material of the return bend tube 1 (tube body portion la) is preferably made of a material having a lower thermal conductivity than the material of the hairpin tube.
  • the return bend pipe 1 is used in the heat exchanger 20 (see Figs. 2 and 3), especially in the air heat exchanger, the return bend pipe 1 is used outside the heat exchange section. Therefore, when the material of the return bend pipe 1 has higher thermal conductivity than the material of the hairpin pipe, heat loss occurs in the return bend pipe 1 portion.
  • the refrigerant evaporates in the return bend pipe 1, and the formation of the "annular flow" of the refrigerant liquid film breaks down. Disturbance (separated flow) of the refrigerant liquid film due to the occurrence occurs.
  • the refrigerant liquid film flows in a turbulent state, and a thick portion of the refrigerant liquid film in the straight tube portion of the hairpin tube is generated, and the outside of the tube
  • the heat exchange becomes unstable and the evaporation performance tends to decrease.
  • phosphorous deoxidized copper is often used as the material for the hairpin tube and the return bend tube 1 (tube body la). Then, when splicing, the ends of both pipes are heated to about 800-900 ° C with a gas burner or the like. At this time, if phosphorus deoxidized copper is used for the return bend pipe 1 (pipe main body la), the strength of the return bend pipe 1 (heat affected zone) is reduced by this heating, and the pressure inside the pipe during use is reduced. This makes it easier to break the tube. In order to avoid this point, it is necessary to increase the first pipe wall thickness (T1) (see Fig. 4) of the return bend pipe 1 (the pipe body la).
  • T1 first pipe wall thickness
  • the return bend tube 1 (pipe main body la) can be reduced in weight.
  • the heat-resistant copper alloy for example, Cu-Sn-P and Cu-Sn-Zn-P based copper alloys having a pressure strength of 10 MPa or more at room temperature even after heating at 850 ° C are preferable.
  • the hairpin tube a heat-resistant copper alloy tube made of the same material as the return bend tube 1 may be used.
  • the first maximum inner diameter (ID1) of the return bend tube 1 (tube main body la) is (ID1) ⁇ () in relation to the second maximum inner diameter (ID2) of the hairpin tube 11. ID2) is preferred. If (ID1) ⁇ (ID2), the force of the "annular flow" of the refrigerant liquid film formed in the pipe of the return bend pipe 1 is expanded when the liquid refrigerant flows into the hairpin pipe 11, and the lower part in the pipe As a result, the refrigerant liquid film accumulates, and the thickness of the refrigerant liquid film becomes non-uniform, thereby disturbing the refrigerant liquid film.
  • the refrigerant liquid film near the inlet of the next-stage hairpin tube flows in a turbulent state, resulting in a thick portion of the refrigerant liquid film, which makes the heat exchange with the outside of the tube unstable and reduces the evaporation performance.
  • the refrigerant liquid film near the inlet of the next-stage hairpin tube flows in a turbulent state, resulting in a thick portion of the refrigerant liquid film, which makes the heat exchange with the outside of the tube unstable and reduces the evaporation performance.
  • the hairpin tube 11 constituting a heat exchanger 20 together with the return bend tube 1 of the present invention
  • the hairpin tube 11 has a plurality of spiral second grooves 12 formed on the inner surface of the tube, and the inner surface groove shape of the second groove 12 is regulated as follows. Power to control S is preferable.
  • the hairpin tube 11 is mainly a 3 to 10 mm tube as a heat transfer tube for air conditioning equipment, the outer diameter of the tube (second tube outer diameter OD2) is the same as that of the hairpin tube 3 to; It is preferable to use a 10 mm tube.
  • a heat-resistant copper alloy having higher heat resistance than phosphorus-deoxidized copper which is preferably phosphorous-deoxidized copper having excellent forming processability, may be used.
  • Second groove pitch (P2) (p 0.37-0.42mm, second cross section (S2) (p 0.04—0.06mm 2 ).
  • Second groove pitch (P2) Is less than 0.37 mm and the second groove cross-sectional area (S2) is less than 0.04 mm 2 when forming the second groove 12 on the inner surface of the pipe (eg, grooved plug)
  • the groove forming tool breaks and immediately forms the second groove 12 on the tube inner surface stably.
  • the refrigerant liquid is inserted between the second grooves 12 inside the pipe. Since the film is hard to be formed thinly, the refrigerant liquid film inside the pipe becomes a thermal resistance, and the evaporation performance is likely to deteriorate.
  • the second groove lead angle ( ⁇ 2) is preferably 15 ° or more.
  • the second groove lead angle ( ⁇ 2) is less than 15 °, the formation of the “swirl flow” of the refrigerant liquid film in the pipe is insufficient, and the evaporation performance tends to be lowered.
  • the formation of a uniform “annular flow” of the refrigerant liquid film in the second groove 12 decreases, and the straight pipe portion of the hairpin pipe 11 As a result, the liquid film of the refrigerant becomes uneven, heat exchange with the outside of the tube becomes unstable, and evaporation performance tends to deteriorate.
  • the second groove lead angle ( ⁇ 2) force exceeds 5 °, the speed when forming the second groove 12 on the inner surface of the tube by rolling will become extremely slow and will soon stabilize and become long. Since the hairpin tube 11 is difficult to manufacture, the second groove lead angle ( ⁇ 2) is more preferably 45 ° or less.
  • the second groove depth (h2) is preferably 0.10-0.28 mm. If the second groove depth (h2) is less than 0.10 mm, the second fin 13 formed between the second grooves 12 on the inner surface of the pipe It becomes lower than the liquid level of the refrigerant and is buried in the refrigerant liquid film. For this reason, the effective heat transfer area inside the pipe is remarkably reduced, and the evaporation performance tends to be lowered. Also, if the second groove depth (h2) exceeds 0.28 mm, the groove forming tool (for example, grooved plug) will be damaged immediately when forming the second groove 12 on the pipe inner surface. It is difficult to form the second groove 12 stably on the inner surface of the tube.
  • the groove forming tool for example, grooved plug
  • the second fin peak angle ( ⁇ 2) is preferably 5 to 45 °! /. If the peak angle ( ⁇ 2) of the second fin is less than 5 °, the second fin 13 may fall over when the hairpin tube 11 is expanded (not shown) when the hairpin tube 11 is installed in the heat exchanger 20 for an air conditioner. Crushing tends to occur. Further, when forming the second groove 12 on the inner surface of the tube for forming the second fin 13, the groove forming tool is easily damaged, and it is difficult to stably form the second groove 12 on the inner surface of the tube. In addition, when the peak angle ( ⁇ 2) of the second fin exceeds 45 °, the cross-sectional area of the second groove 12 is remarkably reduced, and the heat transfer performance is likely to deteriorate. In addition, the cross-sectional area of the second fin 13 (the second tube thickness ( ⁇ 2) of the hairpin tube 11) is increased, the mass of the hairpin tube 11 is increased, and the weight reduction of the heat exchanger 20 is difficult.
  • the second fin root radius (r2) is preferably 1/10 to 1/3 of the second groove depth (h2).
  • the second fin root radius (r2) is less than 1/10 of the groove depth (h2), the formability of the second fin 13 (second groove 12) is increased when the second fin 13 becomes higher. It becomes difficult to obtain the second fin 13 having a predetermined shape, and the groove forming tool that comes into contact with the root of the second groove 12 on the inner surface of the pipe is easily damaged. If the ratio exceeds 1/3, the cross-sectional area of the second fin 13 increases, the second tube thickness (T2) of the hairpin tube 11 increases, and the mass of the hairpin tube 11 increases.
  • the second maximum inner diameter (ID2) of the hairpin tube 11 is 0.80 to 0.96 of the outer diameter (OD2) of the hairpin tube 11. If the second maximum inner diameter (ID2) is less than 0.80 of the outer diameter (OD2) of the hairpin tube 11, the thickness of the second tube (T2) is increased, the mass of the hairpin tube 11 is increased, and heat exchange is performed. It becomes difficult to reduce the weight of the vessel 20 (see Fig. 2 and Fig. 3). In addition, when the second maximum inner diameter (ID2) exceeds 0.96 of the outer diameter (OD2) of the hairpin tube 11, the second tube wall thickness (T2) is reduced and the tube strength of the hairpin tube 11 is reduced. Tube breakage is likely to occur during use of the low heat exchanger 20. [0067] (3) Manufacturing method of return bend tube and hairpin tube
  • Both the return bend tube and the hairpin tube are manufactured, for example, by the following known manufacturing method.
  • a soft material is used for the raw tube to which the following first step is applied.
  • the first to third steps described below are continuously performed using a rolling device provided with a diameter reducing device at the former stage and the latter stage.
  • the inner grooved tube is usually rolled up on a level wound coil and annealed in an annealing furnace to form a soft material, and the fourth step is applied.
  • the raw pipe made of a material such as phosphorous deoxidized copper or heat-resistant copper alloy is pulled out so as to pass between the reduced diameter die and the reduced diameter plug, so that the first reduced diameter processing is performed on the raw pipe. .
  • the grooved plug Inserting a grooved plug into the element pipe reduced in diameter in the first step and pressing the grooved plug inserted into the element pipe with a plurality of rolling balls or rolling rolls.
  • the second diameter reduction process is applied to the base tube.
  • the groove shape of the grooved plug is transferred to the inner surface of the reduced diameter pipe, and the first groove 2 or the second groove 12 (see FIG. 4) is formed.
  • the grooved plug has a groove shape corresponding to the above-described inner surface groove shape (see FIGS. 5 and 6).
  • the third diameter reduction processing is performed, and the first tube outer diameter (OD1) Alternatively, a heat transfer tube with an inner groove with the second tube outer diameter (OD 2) is manufactured.
  • the inner grooved tube manufactured in the third step is bent with a predetermined jig to manufacture a return bend tube 1 and a hairpin tube 11 (see FIGS. 1 and 2) having a predetermined shape.
  • the heat exchanger 20 is supplied with a refrigerant inside the tube, and a large number of hairpin tubes 11, 11,...
  • the hairpin portions 23 arranged in parallel, and the hairpin tubes 11 of each of the hairpin portions 23, 11 '''' Tube end 1, lb (see Fig. 1) joined to many return bend pipes 1, 1 ...
  • a fin portion 21 composed of a large number of fins 21a, 21a '... Arranged in parallel at a constant interval (fin pitch Pb).
  • the hairpin tubes 11 may be arranged in a plurality of rows at a predetermined row direction pitch Pc.
  • the refrigerant supplied into the pipe of the heat exchanger 20 is in the same direction when the refrigerant is condensed with respect to the air flow blown to the heat exchanger 20, and when the refrigerant is evaporated. Flowed in the opposite direction.
  • At least a partial force of the return bend portion 22 is constituted by a return bend pipe 1 in which a large number of first grooves 2 (see Fig. 5) are formed on the inner surface of the pipe.
  • a return bend pipe 1 in which a large number of first grooves 2 (see Fig. 5) are formed on the inner surface of the pipe.
  • the inner surface groove shape of the return bend pipe 1, for example, groove pitch ratio (Pl / P2), groove cross-sectional area ratio (S1 / S 2), groove depth ratio (hl / h2) (see Fig. 5 and Fig. 6)
  • the difference in groove lead angle ( ⁇ 1- ⁇ 2) see Fig.
  • a return bend section 22 may be used as a return bend section 22 made of a smooth pipe.
  • the heat exchanger of the present invention may be one in which at least a part of the refrigerant flow path constituted by the hairpin tube and the return bend pipe is branched to form a plurality of refrigerant flow paths.
  • a two-pass heat exchanger 20A in which the entire refrigerant flow path is branched
  • a partial two-pass heat exchanger 20B in which a part of the refrigerant flow path is branched.
  • the refrigerant flow path is branched into two flow paths (refrigerant flow path A and refrigerant flow path B).
  • the branched refrigerant flow paths may be further branched into a plurality of refrigerant flow paths.
  • the number of branches is one, but it may be two or more, that is, the refrigerant flow path shown in FIG. 3 (c). Is not branched 1-pass heat exchanger 20 is connected to multiple 2-pass heat exchangers 20A It may be a combination.
  • the one-pass heat exchanger 20 (see FIG. 3 (c)) is used.
  • the evaporation performance is improved by maintaining the swirling flow of the refrigerant.
  • the refrigerant mass velocity per branch is lowered, particularly the refrigerant velocity at the return bend pipe inlet side is lowered, and the refrigerant liquid film formed inside the pipe is reduced. The “annular flow” becomes more stable.
  • the refrigerant used in the heat exchanger 20 of the present invention is a hydrated fluorocarbon (HFC) -based refrigerant, which is a non-azeotropic refrigerant mixture, for example, difluoromethane (R410) which is preferred.
  • R410A in which 50% of R32) and pentafluoroethane (R125) are mixed is more preferable.
  • HFC non-azeotropic refrigerant mixture By using an HFC non-azeotropic refrigerant mixture, the evaporation performance of the heat exchanger 20 is improved, and the pressure loss of the refrigerant is also reduced.
  • the R410 system has excellent heat transfer performance, but the compressor tends to be large due to the high operating pressure. Therefore, the R407 system in which the evaporation performance is slightly lower than the R410 system and the operating pressure force is lower than the 410 system may be used as the refrigerant of the present invention.
  • Examples 8 to 20 are phosphorus deoxidized copper of alloy number C1220 or oxygen-free copper of alloy number C1020 specified in JISH3300
  • Example 7 is Cu-Sn-P (0.65 (Mass%, 0.03 mass%, Cu balance heat-resistant copper alloy) is melted, forged, hot extruded, cold pressure It was extended and cold drawn to give a blank tube.
  • the first diameter reduction processing is performed, and the inner diameter groove-shaped spiral grooves or parallel grooves shown in Tables 1 and 2 are formed on the diameter-reduced element pipe.
  • test tube for return bend pipe
  • a first pipe outer diameter (OD 1) of 7 mm was prepared by subjecting the grooved tube to the third diameter reduction and annealing.
  • a test tube (for hairpin tube) with a second tube outer diameter (OD2) of 7 mm was prepared in the same manner using phosphorous deoxidized copper with alloy number C 1220 specified in JISH3300.
  • a fin-and-tube heat exchanger (one-pass heat exchanger) 20 shown in FIG. 2, FIG. 3 (a), (b) was produced using each of the test tubes.
  • a plurality of hairpin tubes 11 were prepared by bending a test tube (for hairpin tubes) into a hairpin shape at a predetermined bending pitch (Pa) at the center thereof.
  • a plurality of hairpin tubes 11 were passed through a plurality of fins 21a arranged in parallel with each other at a predetermined interval (fin pitch (Pb)).
  • a bullet having a tube expansion rate of 105.5% based on the outer diameter standard of the copper tube (hairpin tube 11) is inserted into the heavy tube 11 and a contraction type tube expander (tube expander), and fin 2 la and hepin tube 1 1 were joined.
  • a plurality of return bend pipes 1 were produced by bending a test pipe (for return bend pipes) with a predetermined foot length and pitch (P) (see Fig. 1). Then, as shown in Fig.
  • Heat exchanger 20 was produced by flowing both tubes with a burner while heating them with nitrogen gas to prevent oxidation (850 ° C, 1 minute).
  • the specifications of the heat exchanger 20 are as follows. (Heat exchanger 20)
  • the opening $ is 500mm long x 250mm high x 25.4mm wide.
  • Foot length (U 20. Omm, 21.2 mm, 22.5 mm, 31.4 mm,
  • the thickness of the fin 21a was l lO ⁇ m.
  • 4 10 fins 21a were arranged in parallel with a fin pitch (Pb) of 1.25 mm.
  • Example 9 the same test tube (hairpin tube, return bend tube) as in Example 1 was used, and in the same manner as in Example 1, the fin-and-tube type thermal tube shown in Fig. 7 (a) was used. Exchanger (2-pass heat exchanger) 20A was produced. The number of stages of the hairpin tubes 11 in the refrigerant flow paths A and B is 6 in 2 rows.
  • Comparative Example 1 was the same as Example 1 except that a smooth tube with no grooves formed on the inner surface was used as the test tube (return bend tube).
  • Comparative Examples 2 to 5 except that at least one of the groove pitch ratio (P1 / P2) and the groove cross-sectional area ratio (S 1 / S2) uses an internally grooved tube that is outside the scope of the claims of the present invention, Same as Example 1. Then, a heat exchanger (one-pass heat exchanger) 20 was produced in the same manner as in Example 1.
  • Fig. 8 (a) shows a schematic diagram of a measuring apparatus for measuring the evaporation performance.
  • the measuring device includes a suction type wind tunnel 100 having a constant temperature and humidity function, a refrigerant supply device 110 (see FIG. 8 (b)), and an air conditioner (not shown).
  • the heat exchanger 20 (20A) is arranged in the flow path of the air flowing in from the air inlet 108 and discharged from the air outlet 109, and upstream of the heat exchanger 20 (20A).
  • Air samplers 101 and 102 are arranged on the side and downstream, respectively.
  • the air samplers 101 and 102 are connected to temperature and humidity measuring boxes 103 and 104, respectively.
  • the temperature and humidity measuring boxes 103 and 104 measure the temperature and humidity of the air by measuring the dry bulb temperature and wet bulb temperature of the air sampled by the air samplers 101 and 102, respectively.
  • An induction fan 105 is provided downstream of the air sampler 102 and discharges air to the air discharge port 109. Also, between the heat exchanger 20 (20A) and the air sampler 102, and the air Rectifiers 106 and 106 for rectifying the air that has passed through the heat exchanger 20 (20A) are provided between the sambra 102 and the induction fan 105.
  • FIG. 8 (b) shows a schematic diagram of the refrigerant supply device 110.
  • 107 is a refrigerant pipe
  • 111 is a sight glass
  • 112 is a liquid (refrigerant) heating and cooling heat exchanger
  • 113 is a dryer
  • 114 is a liquid receiver (refrigerant)
  • 115 is a solution.
  • Plug, 116 is a condenser
  • 117 is an oil separator
  • 118 is a compressor
  • 119 is an accumulator
  • 120 is an evaporator
  • 121 is an expansion valve
  • 122 is a flow meter.
  • the refrigerant whose pressure and temperature are adjusted is supplied through the refrigerant pipe 107 into the hairpin pipe 11 (see FIG. 2) of the heat exchanger 20 (20A) provided in the suction type wind tunnel 100.
  • pressure gauges 123 (the temperature is a saturation temperature corresponding to the measurement pressure) for measuring the temperature and pressure of the refrigerant are provided at the inlet and outlet of the heat exchanger 20 (20A).
  • the air conditioner (not shown) supplies air having a controlled temperature and humidity to the air inlet 108 of the suction type wind tunnel 100.
  • the heat exchanger of Comparative Example 2 has a groove cross-sectional area ratio (S 1 / S2) that is less than the lower limit
  • the heat exchanger of Comparative Example 3 has a groove pitch ratio (P1 / P2) and a groove cross-sectional area ratio (S1 / S2).
  • S 1 / S2 the heat exchanger of Comparative Example 2
  • P1 / P2 the heat exchanger of Comparative Example 4
  • S1 / S2 a groove cross-sectional area ratio
  • Example 21 uses the material Cu-S as the test tube (return bend tube).
  • Example 1 except that a pipe with a first tube thickness (T1) 0.20mm made of nP (0.65% by mass, 0.03% by mass ?, the balance being Cu heat-resistant copper alloy) is used. And the same.
  • Example 22 was the same as Example 1 except that an inner grooved tube having a first tube thickness (T1) of 0.34 mm was used as the test tube (return bend tube). Then, a heat exchanger (1-pass heat exchanger) was produced in the same manner as in Example 1. Next, using the heat exchangers of Example 1, Example 21, and Example 22, a pressure resistance test by water pressure was performed. The pressure when breakage occurred in the return bend section (return bend pipe) of the heat exchanger was measured with a Bourdon tube pressure gauge to determine the pressure resistance. The results are shown in Table 4.
  • the heat exchanger of Example 21 has a small decrease in strength due to brazing even if the first pipe wall thickness (T1) of the return bend pipe is thinner than Example 1. It was confirmed that the pressure strength was higher than Further, in the heat exchanger of Example 22 in which the material of the return bend pipe is the same as that of Example 1, the pressure strength is the same as that of Example 21.
  • the first pipe thickness (T1) of the return bend pipe is It was 1.7 times that of Example 1 and it was confirmed that the amount of material used increased.

Landscapes

  • 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 de chaleur de type à ailettes et tubes utilisant un tube de retour coudé capable de maximiser la performance d'évaporation de l'échangeur de chaleur. Ledit échangeur de chaleur comprend une unité en épingle à cheveux doté d'une multiplicité de tubes en épingle à cheveux disposés en parallèle, une unité de retour coudée dotée d'une multiplicité de tels tubes de retour coudés disposés en parallèle et articulés aux parties d'extrémité des tubes en épingle à cheveux individuelles des parties en épingle à cheveux, et une partie à ailettes ayant une multiplicité d'ailettes disposées en parallèle à un espacement constant sur les surfaces externes des tubes en épingle à cheveux. Les intérieurs de tubes sont alimentés par un agent de refroidissement. L'échangeur de chaleur comporte des premières rainures formées sur les faces internes des tubes de retour coudés. Le rapport de pas de rainure (P1/P2) entre un premier pas de rainure (P1) des premières rainures, pris dans la section normale à l'axe de tube, et un second pas de rainure (P2) de secondes rainures, pris dans la section normale à l'axe de tube, d'une forme hélicoïdale formées dans les faces internes de tube des tubes en épingle à cheveux est de 0,65 à 2,2. En même temps, le rapport de surface de section de rainure (S1/S2) entre une première surface de section de rainure (S1) par rainure, prise dans la section normale à l'axe de tube, des premières rainures et une seconde surface de section de rainure (S2) par rainure, prise dans la section normale à l'axe de tube des secondes rainures est de 0,3 à 3,6.
PCT/JP2007/063807 2006-07-14 2007-07-11 Échangeur de chaleur de type à ailettes et tubes, et son tube de retour coudé WO2008007694A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP07790611.3A EP2042825B1 (fr) 2006-07-14 2007-07-11 Échangeur de chaleur de type à ailettes et tubes, et son tube de retour coudé
CN2007800213773A CN101466992B (zh) 2006-07-14 2007-07-11 翅片管型换热器及其u形弯头管

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2006193721A JP4728897B2 (ja) 2006-07-14 2006-07-14 リターンベンド管およびフィンアンドチューブ型熱交換器
JP2006-193721 2006-07-14

Publications (1)

Publication Number Publication Date
WO2008007694A1 true WO2008007694A1 (fr) 2008-01-17

Family

ID=38923250

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2007/063807 WO2008007694A1 (fr) 2006-07-14 2007-07-11 Échangeur de chaleur de type à ailettes et tubes, et son tube de retour coudé

Country Status (6)

Country Link
EP (1) EP2042825B1 (fr)
JP (1) JP4728897B2 (fr)
KR (1) KR20080108620A (fr)
CN (1) CN101466992B (fr)
MY (1) MY144548A (fr)
WO (1) WO2008007694A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2123998A2 (fr) * 2008-05-21 2009-11-25 STIEBEL ELTRON GmbH & Co. KG Dispositif de pompe à chaleur doté d'un caloporteur doté d'une tubulure à lamelles en tant qu'évaporateur

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101829827B (zh) * 2010-06-12 2012-02-01 西安交通大学 内翅片管高温真空钎焊夹具
CN102235779B (zh) * 2011-07-19 2013-07-24 海信科龙电器股份有限公司 空调换热器
KR20140106552A (ko) * 2011-12-07 2014-09-03 파나소닉 주식회사 핀 튜브형 열교환기
JP2013134024A (ja) * 2011-12-27 2013-07-08 Panasonic Corp 冷凍サイクル装置
DE102012005513A1 (de) * 2012-03-19 2013-09-19 Bundy Refrigeration Gmbh Wärmetauscher, Verfahren zu seiner Herstellung sowie verschiedene Anlagen mit einem derartigen Wärmetauscher
CN105026869B (zh) * 2013-02-21 2017-09-12 开利公司 用于热交换器的管道结构
CN103307919A (zh) * 2013-06-24 2013-09-18 苏州市金翔钛设备有限公司 一种钛盘管
CN104279910A (zh) * 2013-07-11 2015-01-14 上海林内有限公司 用于热交换器的管接头
ITMI20131684A1 (it) * 2013-10-11 2015-04-12 Frimont Spa Condensatore per macchina di fabbricazione del ghiaccio, metodo per la sua realizzazione, e macchina di fabbricazione del ghiaccio che incorpora tale condensatore
WO2016009565A1 (fr) * 2014-07-18 2016-01-21 三菱電機株式会社 Dispositif à cycle de réfrigération
US9777967B2 (en) 2014-08-25 2017-10-03 J R Thermal LLC Temperature glide thermosyphon and heat pipe
JP6357178B2 (ja) 2015-07-30 2018-07-11 株式会社デンソーエアクール 熱交換器およびその製造方法
US10520255B2 (en) 2016-11-11 2019-12-31 Johnson Controls Technology Company Finned heat exchanger U-bends, manifolds, and distributor tubes
CN109751750A (zh) * 2017-11-08 2019-05-14 开利公司 用于空调系统的末端产品的换热管及其制造方法
KR102097462B1 (ko) 2019-05-09 2020-04-06 (주)에프원공조 열교환기용 리턴벤드 및 그 제조방법
KR102186154B1 (ko) * 2019-07-09 2020-12-03 엘지전자 주식회사 열교환기 및 열교환기의 제조방법

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63154986A (ja) 1986-12-18 1988-06-28 Seiko Instr & Electronics Ltd 時計用外装部品の固定方法
JPH04122986A (ja) 1990-09-13 1992-04-23 Fujitsu Ltd 画像データｄｍａ転送制御方式
JPH10292992A (ja) * 1997-04-18 1998-11-04 Toshiba Corp 熱交換器の製造方法
JPH11190597A (ja) 1997-12-26 1999-07-13 Hitachi Cable Ltd 熱交換器の伝熱管接続方法
JP2006098033A (ja) 2004-09-02 2006-04-13 Kobelco & Materials Copper Tube Inc リターンベンド管およびフィンアンドチューブ型熱交換器

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0926280A (ja) * 1995-07-12 1997-01-28 Sanyo Electric Co Ltd 内面溝付冷媒配管
JP4300013B2 (ja) * 2001-10-22 2009-07-22 昭和電工株式会社 熱交換器用フィン付き管、熱交換器、熱交換器用フィン付き管の製造方法および熱交換器の製造方法
JP4119836B2 (ja) * 2003-12-26 2008-07-16 株式会社コベルコ マテリアル銅管 内面溝付伝熱管

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63154986A (ja) 1986-12-18 1988-06-28 Seiko Instr & Electronics Ltd 時計用外装部品の固定方法
JPH04122986A (ja) 1990-09-13 1992-04-23 Fujitsu Ltd 画像データｄｍａ転送制御方式
JPH10292992A (ja) * 1997-04-18 1998-11-04 Toshiba Corp 熱交換器の製造方法
JPH11190597A (ja) 1997-12-26 1999-07-13 Hitachi Cable Ltd 熱交換器の伝熱管接続方法
JP2006098033A (ja) 2004-09-02 2006-04-13 Kobelco & Materials Copper Tube Inc リターンベンド管およびフィンアンドチューブ型熱交換器

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP2042825A4 *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2123998A2 (fr) * 2008-05-21 2009-11-25 STIEBEL ELTRON GmbH & Co. KG Dispositif de pompe à chaleur doté d'un caloporteur doté d'une tubulure à lamelles en tant qu'évaporateur
EP2123998A3 (fr) * 2008-05-21 2014-12-03 STIEBEL ELTRON GmbH & Co. KG Dispositif de pompe à chaleur doté d'un caloporteur doté d'une tubulure à lamelles en tant qu'évaporateur

Also Published As

Publication number Publication date
CN101466992B (zh) 2010-12-22
CN101466992A (zh) 2009-06-24
EP2042825A4 (fr) 2010-06-16
JP2008020150A (ja) 2008-01-31
JP4728897B2 (ja) 2011-07-20
EP2042825A1 (fr) 2009-04-01
EP2042825B1 (fr) 2018-10-03
KR20080108620A (ko) 2008-12-15
MY144548A (en) 2011-09-30

Similar Documents

Publication Publication Date Title
WO2008007694A1 (fr) Échangeur de chaleur de type à ailettes et tubes, et son tube de retour coudé
JP4759226B2 (ja) 拡管用工具およびそれを使用した拡管方法
JP2008215733A (ja) フィンアンドチューブ型熱交換器
EP2312254B1 (fr) Echangeur de chaleur et climatiseur équipé de l'échangeur de chaleur
JP5649715B2 (ja) 熱交換器及びこの熱交換器を備えた冷蔵庫、空気調和機
JP2008164245A (ja) 熱交換器
JP2007271123A (ja) 内面溝付伝熱管
JP4119836B2 (ja) 内面溝付伝熱管
JPWO2013084508A1 (ja) フィンチューブ型熱交換器
KR101200597B1 (ko) 복합 전열관, 이를 이용한 열교환기 및 열교환 시스템
JP4422590B2 (ja) リターンベンド管およびフィンアンドチューブ型熱交換器
JP6053693B2 (ja) 空気調和機
JP2006194476A (ja) 室外熱交換器
WO2017208419A1 (fr) Échangeur de chaleur de type à tubes et ailettes, appareil de type pompe à chaleur équipé de l'échangeur de chaleur de type à tubes et ailettes et procédé de fabrication de l'échangeur de chaleur de type à tubes et ailettes
JP2011021844A (ja) 内面溝付伝熱管及び蒸発器用のクロスフィンチューブ型熱交換器
JP6802697B2 (ja) 内面溝付管
JP2007271238A (ja) 熱交換器
JP2013096651A (ja) 内面溝付伝熱管及び内面溝付伝熱管を備えた熱交換器及びその製造方法
JP2012093053A (ja) 熱交換器、熱交換器の製造方法、冷蔵庫、および空気調和機
JP2010019489A (ja) 蒸発器用の内面溝付伝熱管
JP4119765B2 (ja) 内面溝付伝熱管
JP7290396B2 (ja) 熱交換器
JP2011033239A (ja) 伝熱管、空気調和機、及び伝熱管の製造方法
JP2010139233A (ja) 蒸発器用のクロスフィンチューブ型熱交換器
JP2003287383A (ja) 内面溝付管

Legal Events

Date Code Title Description
WWE Wipo information: entry into national phase

Ref document number: 200780021377.3

Country of ref document: CN

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

Ref document number: 07790611

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 1020087027945

Country of ref document: KR

WWE Wipo information: entry into national phase

Ref document number: 2007790611

Country of ref document: EP

NENP Non-entry into the national phase

Ref country code: DE

NENP Non-entry into the national phase

Ref country code: RU