WO2005100898A1 - Ailette de transfert thermique pour échangeur de chaleur - Google Patents

Ailette de transfert thermique pour échangeur de chaleur Download PDF

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Publication number
WO2005100898A1
WO2005100898A1 PCT/JP2005/007383 JP2005007383W WO2005100898A1 WO 2005100898 A1 WO2005100898 A1 WO 2005100898A1 JP 2005007383 W JP2005007383 W JP 2005007383W WO 2005100898 A1 WO2005100898 A1 WO 2005100898A1
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WO
WIPO (PCT)
Prior art keywords
heat transfer
fin
heat
fins
heat exchanger
Prior art date
Application number
PCT/JP2005/007383
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English (en)
Japanese (ja)
Inventor
Hyunyoung Kim
Original Assignee
Daikin Industries, 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 Daikin Industries, Ltd. filed Critical Daikin Industries, Ltd.
Priority to EP05730153A priority Critical patent/EP1739377A4/fr
Priority to US11/578,046 priority patent/US20080296008A1/en
Publication of WO2005100898A1 publication Critical patent/WO2005100898A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/003—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by using permeable mass, perforated or porous materials
    • 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
    • F28D1/03—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 plate-like or laminated conduits
    • F28D1/0308—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other
    • F28D1/0325—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another
    • 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
    • F28D1/0478—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 the conduits having a non-circular cross-section
    • 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
    • F28D1/0535—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 the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators

Definitions

  • the present invention relates to a heat exchanger used for an air conditioner and a heat transfer fin suitable for various other heat exchangers.
  • a cross fin type heat exchanger including slit fins and louver fins has been proposed.
  • Japanese Patent Application Laid-Open Nos. 493595 and 926279 disclose these heat exchangers. If slits and louvers are provided for the heat transfer fins made of a thin plate with good heat conductivity such as an aluminum plate, the heat transfer performance with air (heat transfer coefficient) can be improved by the leading edge effect.
  • Japanese Patent Application Laid-Open No. 2002-195774 proposes using a laminated heat exchanger including a flat heat transfer tube and a corrugated fin for an air conditioner.
  • Figures 31 and 32 show the overall structure of each heat exchanger equipped with such flat heat transfer tubes and corrugated fins, as well as the components.
  • the heat exchanger 10 includes a plurality of flat heat transfer tubes 1 extending in parallel to a direction orthogonal to the headers 12A, 12B between pipe-shaped upper and lower headers 12A, 12B through which the refrigerant is introduced and discharged. It is formed so as to communicate with the headers 12A and 12B.
  • a corrugated fin 11 formed by continuously bending a flat aluminum plate or the like is joined between the heat transfer tubes 1 to the adjacent heat transfer tubes 1.
  • the heat pipe 1 has a plurality of refrigerant flow passages 2 each having a rectangular cross section defined by partition walls.
  • the refrigerant introduced from the external refrigerant pipes 7 and 8 through the headers 12A and 12B flows evenly into the respective refrigerant flow passages 2, and is transmitted as widely as possible through the flat surface of the heat transfer tube 1 and the corrugated fins 11. Efficient heat exchange between the internal refrigerant and external air in the heat area Exchange.
  • a plurality of louvers l la and l ib for improving heat transfer efficiency with air are formed on the flat surface from the upstream side to the downstream side of the air flow,
  • the heat exchange performance between the refrigerant and the air is made as high as possible by the leading edge effect.
  • An object of the present invention is to provide a heat exchanger in which an air-side heat transfer fin of a heat exchanger is formed of a foamed metal produced by foaming copper, aluminum, or the like having a high heat transfer coefficient, thereby greatly improving heat transfer performance.
  • the present invention is configured as follows to achieve the above object.
  • a heat transfer tube through which a fluid to be heat-exchanged with air flows, and a heat transfer fin provided in the heat transfer tube and exchanging heat by contact with air. Consists of foamed metal with a pore density of 20PPI or more.
  • the foamed metal has a porous structure of an open cell type in which a fluid can flow inside due to thin linear grooves connected to each other, and therefore has a large surface area per unit volume. Therefore, the heat transfer area of the foam metal is large. In addition, since the foam metal has a complicated flow path, heat transfer is promoted by turbulence of the fluid.
  • the foam metal can easily renew the temperature boundary layer by the linear grooves, and can obtain a high heat transfer coefficient. Therefore, the heat transfer performance of the heat transfer fins becomes extremely high. Therefore, when the heat transfer fins formed of the foamed metal are employed, the heat exchange performance of the heat exchanger can be greatly improved.
  • the flow path structure of the foamed metal is complicated and the pressure loss is large. Les ,. Therefore, when adopting foam metal as the material of the heat transfer fins, it is important to determine the optimum pore density. According to the results of various studies and experiments, it has been found that the pore density for maximizing the heat conductivity of the foam metal is preferably at least 20 PPI or more.
  • a plurality of heat transfer tubes through which a fluid to be exchanged with air flows are provided, and an interval between the plurality of heat transfer tubes is set to 12 mm or less.
  • the heat transfer fins made of foamed metal have a large surface area per unit volume and a large heat transfer area, and thus have excellent heat transfer performance.
  • foamed metal has drawbacks in that the linear grooves are thin and the fin efficiency is lower than that of loop fins. Therefore, it is necessary to optimize the interval between multiple heat transfer tubes. Therefore, as a result of various investigations, it was effective to set the interval between the multiple heat transfer tubes to 12 mm or less, and the heat transfer performance was sufficiently improved especially when the pore density was 20 PPI or more.
  • a third solution of the present invention is characterized in that the heat exchanger is a stacked heat exchanger.
  • the heat transfer tubes are flat and extend in the air flow direction, and the heat transfer fins provided therebetween can be configured to be sufficiently long in the air flow direction. Therefore, the stacked heat exchanger itself has high heat transfer performance.
  • a fourth solution of the present invention is characterized in that the pore density is 20 PPI or more and 60 PPI or less.
  • the fifth solution of the present invention is characterized in that the interval between the plurality of heat transfer tubes 1 is 4 mm or more and 12 mm or less.
  • the foamed metal has a large surface area per unit volume and a large heat transfer area, and thus has excellent heat transfer performance.
  • the fin efficiency is low. Therefore, it is necessary to optimize the interval between multiple heat transfer tubes.
  • the heat transfer performance was improved when the distance between the heat transfer tubes was 4 mm or more and 12 mm or less.
  • FIG. 1 is a perspective view showing a configuration of a heat exchanger according to a first embodiment of the present invention.
  • FIG. 2 is an enlarged view showing a configuration of a material structure of a heat transfer fin made of a foamed metal.
  • FIG. 3 Samples of (A) No. 1 (Nol), (B) No. 2 (No. 2), (C) No. 3 (No. 3) (pore ratio) 10PPI, 20PPI, 40PPI).
  • FIG. 4 is a graph showing the relationship between the wind velocity Vf on the front side of the heat transfer fin and the heat transfer performance QN per unit volume.
  • FIG. 5 is a graph showing the relationship between heat transfer performance per unit volume of a heat transfer fin and pump power.
  • FIG. 6 is a graph showing a relationship between a front-side wind speed Vf and a pressure loss ⁇ P in a heat transfer fin.
  • FIG. 7 is a graph showing pressure loss characteristics during heating of foam metal in heat transfer fins.
  • FIG. 8 is a graph showing a change in a friction loss coefficient f of the heat transfer fin during heating.
  • FIG. 9 is a graph showing the relationship between the heat transfer coefficient of the heat transfer fin during heating and the surface area ⁇ per unit volume.
  • FIG. 10 is a graph showing the relationship between ho during heating of a heat transfer fin and the wind speed Vf on the front side.
  • FIG. 11 is a graph showing the correspondence between the calculation results by equation (10) and the experimental results in explaining the action of the heat transfer fins.
  • Garden 12] is a graph showing the relationship between the pressure loss ( ⁇ / D) and the wind speed (Vf) on the front side during cooling and drying in the heat transfer fins.
  • FIG. 13 is a graph showing a relationship between a pressure loss ( ⁇ P / D) and a frontal wind speed Vf (m / s) of a heat transfer fin during cooling wet (water temperature 5 ° C.).
  • FIG. 6 is a graph showing a ratio ⁇ ⁇ / ⁇ ⁇ ⁇ ⁇ ⁇ to a pressure loss ⁇ ⁇ during a lie (5 ° C.).
  • Vf speed
  • FIG. 27 is a graph showing the relationship between the heat transfer performance h ⁇ of the heat transfer fin per unit volume during cooling wet and the required power E ⁇ per unit product wet product.
  • FIG. 29 is a perspective view showing a configuration of a heat exchanger according to a second embodiment of the present invention.
  • FIG. 30 is a perspective view showing a configuration of a heat exchanger according to a third embodiment of the present invention.
  • FIG. 31 is a perspective view showing a configuration of an air heat exchanger according to a conventional example.
  • FIG. 32 is a partially cutaway perspective view showing a configuration of a main part of a conventional air heat exchanger.
  • FIGS. 1 and 2 show the entire heat exchanger and the configuration of main parts according to a first preferred embodiment of the present invention.
  • a heat exchanger 10 is composed of a plurality of pipes, which extend in parallel with each other in a direction orthogonal to the headers 12A, 12B, between pipe-shaped upper and lower headers 12A, 12B through which a refrigerant is introduced and discharged.
  • the flat heat transfer tube 1 is formed so as to communicate with the headers 12A and 12B.
  • a Korgut fin 11 formed by continuously bending a flat aluminum plate or the like is joined to the adjacent heat transfer tubes 1.
  • the heat transfer fins 13 are formed of an open-cell type foamed metal having a porous structure as shown in FIG. 2 through which a fluid, which cannot be a conventional corrugated fin, can flow inside. ing.
  • the heat transfer tube 1 has a plurality of refrigerant flow grooves having a rectangular cross section defined by partition walls, similarly to the conventional product shown in FIG. Then, the refrigerant introduced and distributed from the external refrigerant pipes 7 or 8 via the upper header 12A or the lower header 12B flows uniformly in each refrigerant flow groove from above to below or from below to above. Heat is exchanged with the external air as efficiently as possible through the heat transfer surface of the coolant flowing through each coolant flow passage and the porous fin surface of the heat transfer fins 13 made of foamed metal. [0024]
  • the foam metal forming the heat transfer fins 13 is a porous substance.
  • foamed metal has a large surface area per unit volume and a complicated flow path, the heat transfer area is large, and an effective heat transfer promoting action due to turbulence of the fluid can be expected.
  • foamed metal has a large number of interconnected thin linear grooves (see microstructure in Fig. 2), which makes it possible to easily update the temperature boundary layer and obtain a very high heat transfer coefficient. be able to.
  • the heat exchanger 10 having such a configuration is used as, for example, a condenser
  • the refrigerant introduced from the external refrigerant pipe 7 via the upper header 12A is evenly distributed from above the heat transfer tube 1 to below. It is distributed and flows, and is led out of the external refrigerant pipe 8 via the lower header 12B.
  • the heat exchanger 10 is used as an evaporator, the refrigerant flows in the opposite direction.
  • the heat transfer tubes 1 are flattened and elongated in the air flow direction, and the heat transfer fins 13 disposed therebetween extend in the air flow direction, and the heat transfer performance is improved. large. Further, the heat transfer fins 13 can be easily formed by foaming a metal having a high heat transfer coefficient, such as aluminum or copper, and shaping the metal into a shape that can be brazed.
  • a heat exchanger suitable for an air conditioner can be formed with high heat exchange performance at low cost and compactly.
  • the foamed metal forming the heat transfer fins 13 of the present embodiment is a porous substance, and as shown in FIGS. 3A, 3B, and 3C, the pore density PPI is represented by (A).
  • the surface area per unit volume is increased as higher as 10PPI, (B) 20PPI, (C) 40PPI.
  • the pressure loss increases. Therefore, it is important to determine the optimum range of the pore density PPI when adopting the heat transfer fins 13 of the air heat exchanger as described above.
  • PPI pore 'par' inch indicates the density of bubbles per inch cubic inch.
  • the pore density PPI of the foamed metal is generally preferably 20 PPI or more ((B), (C) in Fig. 3) and 60 PPI or less. .
  • the diameter of the linear grooves connected to each other is small, so that there is a problem that the fin efficiency is lower than that of a conventional loop fin or the like. Therefore, it is necessary to set the interval (fin width) H of the heat transfer tubes 1 to an optimum value. Therefore, as a result of various studies and experiments, it was found that the interval H between the heat transfer tubes 1 was in the range of 4 mm or more and 12 mm or less. It turned out to be optimal.
  • the interval H between the heat transfer tubes 1 is 4 mm or more and 12 mm or less.
  • the gap H between the heat transfer tubes 1 is 4 mm or more and 12 mm or less when the pore density of the heat transfer fins 13 made of foamed metal is 20 PPI or more and 60 PPI or less, as shown in the graph of FIG. 4, the unit for the front wind speed Vf
  • the heat transfer performance per volume QN (W / m 3 ) was greatly improved compared to the case of louver fins.
  • the distance H between the heat transfer tubes 1 and the bore density of the heat transfer fins are as described above, as shown in the graph of Fig. 5, the amount of heat transfer per unit volume with the same power is about 25% compared to the case of the louver fins. Increased Effective heat transfer performance was improved.
  • the dimensions 5 mm, 8 mm, and 12 mm in the legends of FIGS. 4 and 5 are determined by considering the distance H between the heat transfer tubes 1 (hereinafter, referred to as the width of the heat transfer fins 13). The three sets of dimensional data that were adopted when performing this are shown.
  • aluminum foam metal (aluminum alloy 6101) is used as a heat transfer fin, and its pore density PPI is, for example, No. 1: Figure 3 (8) No. 10 shown, No. 2: Three types of 20PPI shown in Fig. 3 (B) and No. 3: 40PPI shown in Fig. 3 (C) were prepared.
  • three types with different widths of the heat transfer fins that is, the distance between the heat transfer tubes 1) H of 5 mm, 8 mm, and 12 mm were prepared, and a total of 9 types of samples were prepared. Then, the heat exchange between the refrigerant (hot water as an example) on the heat transfer tube 1 side and the air flowing outside in the configuration of FIG. 1 was performed.
  • the experimental conditions were an air temperature of 20 ° C and a relative humidity of 50%.
  • the measurement of pressure loss was performed under no-load conditions without supplying hot water into the heat transfer tube 1, while the measurement of heat transfer coefficient was performed as a heat source. This was performed by supplying warm water at 50 ° C.
  • the wind speed range was about 0.5 to 2.3 m / s as the wind speed Vf on the front side (upstream side) of the heat transfer fins 13.
  • the specific material of the aluminum foam metal used in this experiment is aluminum alloy 6101 as described above.
  • the following [Table 1] shows the detailed specifications.
  • the three types of foamed metal No. 1 to No. 3 (10, 20, and 40 PPI) with a pore density of PPI, to see the effect of the spacing H between the wall surfaces Nine types of samples were prepared with three widths of 5 mm, 8 mm, and 12 mm. The height L of these foamed metals was 89 mm, the depth D was 13 mm, and the surface area per unit volume was 3.
  • the graph in Fig. 6 shows the relationship between the frontal wind speed Vf (m / s) and the pressure loss P (Pa).
  • the pressure loss ⁇ ⁇ increases as the pore density PPI increases, that is, as the pore size d decreases.
  • the pressure drop characteristics of the foamed metal are calculated by using the water permeability ( ⁇ ) and the Ergun coefficient (C) as follows.
  • FIG. 8 shows the change in the friction loss coefficient f with respect to Re.
  • the graph in Figure 9 shows the product of the measured heat transfer coefficient ha and the surface area per unit volume.
  • the heat transfer coefficient ha is defined by the following equation.
  • the heat transfer performance increases as the pore density ⁇ increases and the fin width ⁇ decreases.
  • the heat transfer performance is higher than in the case of the conventional louver fins, suggesting that the heat exchanger can be made more compact. Let's do it.
  • the heat transfer coefficient ha needs to find the force S including the fin efficiency, and the heat transfer coefficient h not including the fin efficiency needs to be determined for the optimal design.
  • the heat transfer coefficient h cannot be easily obtained due to the complicated flow path shape. Therefore, Here, h. Ask for.
  • the characteristic length of the porous material can be d and ⁇ .
  • N3 ⁇ 4 i2 h. ⁇ "/ k (8)
  • FIG. 11 shows a comparison between the correlation equation of Equation (10) and the actual experimental results. As a result, the two agree well, and it can be seen that 90% of the data is within an error of ⁇ 6%.
  • the experimental conditions were an air temperature of 20 ° C and a relative humidity of 50%.
  • the pressure loss was measured under no-load conditions without supplying cold water into the flat heat transfer tube 1, while the heat transfer coefficient was measured by supplying cold water at 5 ° C and 10 ° C as a cold heat source.
  • the wind speed range was about 0.5 to 2.3 m / s as the wind speed Vf on the front side (upstream side) of the heat transfer fins 13.
  • the specific specifications of the aluminum foam metal (aluminum alloy 6101) used in this experiment were as follows. This is also shown in [Table 1] above. Then, as in the case of the first experimental example, the foam metal No. 1 to No. 3 (10, 20, 40 PPI) with three types of pore density PPI (pores per inch) In order to see the effect of the interval H, the fin width H was set to 3 types of 5 mm, 8 mm, and 12 mm, and a total of 9 types of test samples were prepared. The height L in the upward and downward direction is 89 mm, the depth D is 13 mm, and the surface area per unit volume is j3.
  • the graph of FIG. 12 shows the pressure loss ⁇ / D (Pa / m) with respect to the front wind speed Vf (m / s) in a dry state.
  • the length D (m) of the fin portion in the direction of air flow was considered in order to consider the difference between dry and wet states.
  • ⁇ P / D the pressure loss
  • Fig. 13 shows the relationship between the front wind speed Vf (m / s) in each wet state when the temperature of water as the refrigerant is 5 ° C
  • Fig. 14 when the temperature of water as the refrigerant is 10 ° C.
  • the pressure loss ⁇ P (Pa) is shown.
  • the ratio ⁇ ⁇ ⁇ / ⁇ ⁇ wet dry of the pressure loss ⁇ ⁇ between dry and wet increases as the pore density PPI increases.
  • the ratio is larger than in the case of louver fins. That is, the foamed metal fins have lower drainage properties than the louver fins.
  • the foamed metal fins used in this experiment are of an experimental level only, and the fin surfaces are in an untreated state. The problem can be improved sufficiently.
  • the fin surface must be considered separately in two cases: a dry state and a wet state.
  • Fig. 17 shows the relationship between the heat transfer coefficient h and the front wind speed Vf (mZs) under dry conditions.
  • the heat transfer coefficient h is such that the smaller the pore density PPI, the larger the fin width H
  • FIG. 19 shows the ratio of the heat transfer performance of the foam metal fin to the louver fin.
  • Figs. 20 and 21 show the relationship between the front wind velocity Vf (mZs) and the heat transfer coefficient h in the wet state when the temperature of the cold water is 5 ° C and 10 ° C.
  • FIG. 22 (water temperature 5 ° C.) and FIG. 23 (water temperature 10 ° C.) show the heat transfer performance h ⁇ per unit volume in a wet state. Looking at this, it can be seen that the foam metal fins
  • the wettability increases with the increase of the overall air velocity and the fin width H and the decrease of the pore density PPI.
  • the foamed metal fin of the present embodiment is the same as the existing louver fin. It can be seen that it has a higher pressure loss and a higher heat transfer coefficient per volume as compared with. However, in order to construct a heat exchanger for an air conditioner, it is necessary to comprehensively study these pressure loss and heat transfer coefficient.
  • the required pump power per unit volume is expressed by the following equation.
  • V volume and A is flow cross section.
  • FIGS. 26 and 27 show the heat transfer coefficients h ⁇ and h ⁇ per unit volume in each of the dry state and the wet state in relation to the pump power ⁇ required per unit volume. .
  • FIG. 29 shows the configuration of the air heat exchanger according to the second embodiment of the present invention.
  • the present embodiment relates to a serpentine heat exchanger formed by bending a flat heat transfer tube 21 in a meandering shape as a single continuous structure.
  • FIG. 30 shows the configuration of the heat exchanger according to the third embodiment of the present invention.
  • a plurality of plate-shaped heat transfer tubes 31 extending in the horizontal direction are connected in a stacked manner by left and right connection members 22 connecting the heat transfer tubes 31, and a transfer made of foamed metal is provided between the connection members 22 of each layer.
  • Heat fins 13 are arranged.
  • Each heat transfer tube 31 has a refrigerant inlet and outlet 23 This hole 23 is connected through the connecting member 22 to form a refrigerant flow passage.
  • the through connection member 22 shows a configuration in the case of being formed as a laminated plate type air heat exchanger having the same configuration as that of the above-described best embodiment 1.
  • heat transfer fins of the present invention are not limited to the configuration of the heat exchanger according to each embodiment, but may be applied to heat transfer fins that exchange heat with air, such as a cross fin type. Needless to say.

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

Abstract

Une ailette de transfert thermique (13) équipe un tube de transfert de chaleur (1) dans lequel s’écoule un fluide pour échanger de la chaleur avec l’air. L’ailette de transfert thermique, qui transfert de la chaleur en ayant un contact avec l’air, est constituée d’une mousse de métal ayant une densité de pore de 20 PPI ou plus.
PCT/JP2005/007383 2004-04-16 2005-04-18 Ailette de transfert thermique pour échangeur de chaleur WO2005100898A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP05730153A EP1739377A4 (fr) 2004-04-16 2005-04-18 Ailette de transfert thermique pour échangeur de chaleur
US11/578,046 US20080296008A1 (en) 2004-04-16 2005-04-18 Heat Transfer Fin for Heat Exchanger

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2004-122141 2004-04-16
JP2004122141 2004-04-16
JP2005-053087 2005-02-28
JP2005053087A JP2005326136A (ja) 2004-04-16 2005-02-28 空気熱交換器用伝熱フィン

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EP (1) EP1739377A4 (fr)
JP (1) JP2005326136A (fr)
WO (1) WO2005100898A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006059908A1 (fr) * 2004-12-03 2006-06-08 Andries Meuzelaar Echangeur de chaleur pour moyen de transport motorise, et moyen de transport motorise pourvu de cet echangeur de chaleur
CN113473762A (zh) * 2020-03-30 2021-10-01 华为技术有限公司 设备外壳、设备和激光雷达

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CN103954080A (zh) * 2014-05-15 2014-07-30 广东志高空调有限公司 一种换热器结构
CN103968613A (zh) * 2014-05-27 2014-08-06 广东志高空调有限公司 一种微通道换热器
CN104896968A (zh) * 2015-06-16 2015-09-09 中国石油大学(华东) 一种金属泡沫翅片管换热器
US11535086B2 (en) * 2016-12-20 2022-12-27 Lg Innotek Co., Ltd. Heating rod, heating module including same, and heating device including same
CN108317774A (zh) * 2018-01-31 2018-07-24 天津商业大学 一种基于泡沫金属的co2冷却蒸发器
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WO2006059908A1 (fr) * 2004-12-03 2006-06-08 Andries Meuzelaar Echangeur de chaleur pour moyen de transport motorise, et moyen de transport motorise pourvu de cet echangeur de chaleur
CN113473762A (zh) * 2020-03-30 2021-10-01 华为技术有限公司 设备外壳、设备和激光雷达

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JP2005326136A (ja) 2005-11-24
EP1739377A1 (fr) 2007-01-03
US20080296008A1 (en) 2008-12-04
EP1739377A4 (fr) 2009-12-02

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