EP1739377A1 - 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
EP1739377A1
EP1739377A1 EP05730153A EP05730153A EP1739377A1 EP 1739377 A1 EP1739377 A1 EP 1739377A1 EP 05730153 A EP05730153 A EP 05730153A EP 05730153 A EP05730153 A EP 05730153A EP 1739377 A1 EP1739377 A1 EP 1739377A1
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EP
European Patent Office
Prior art keywords
heat transfer
fin
heat
foam metal
heat exchanger
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP05730153A
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German (de)
English (en)
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EP1739377A4 (fr
Inventor
Hyunyoung c/o DAIKIN INDUSTRIES LTD. KIM
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Daikin Industries Ltd
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Daikin Industries Ltd
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Publication date
Application filed by Daikin Industries Ltd filed Critical Daikin Industries Ltd
Publication of EP1739377A1 publication Critical patent/EP1739377A1/fr
Publication of EP1739377A4 publication Critical patent/EP1739377A4/fr
Withdrawn legal-status Critical Current

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    • 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 transfer fin appropriate for use in a heat exchanger for air conditioners and other types of heat exchangers.
  • Improvement in the heat transfer performance of an air side heat transfer fin for a heat exchanger or the like used in an air conditioner is an essential factor when miniaturizing the heat exchanger for saving energy in the system itself.
  • a cross fin type heat exchanger including slit fins or louver fins has been proposed.
  • Japanese Laid-Open Patent Publication No. 4-93595 and Japanese Laid-Open Patent Publication No. 9-26279 disclose such heat exchangers.
  • slits or louvers are arranged for heat transfer fins made of thin plates having satisfactory heat transmittance such as aluminum plates, their front edges function to improve the heat transfer performance (heat transfer coefficient) with air.
  • Japanese Laid-Open Patent Publication No. 2002-195774 proposes the use of a stacked type heat exchanger including flat heat transfer tubes and corrugated fins in an air conditioner.
  • the entire heat exchanger including the flat heat transfer tubes and the corrugated fins as well as each part of the heat exchanger is shown in Figs. 31 and 32.
  • a heat exchanger 10 includes pipe-shaped upper and lower headers 12A and 12B through which a refrigerant is flows in and out.
  • the heat transfer tube 1 includes a plurality of refrigerant passages 2 having a square cross-section partitioned by partitions.
  • the refrigerant flowing through the headers 12A and 12B from external refrigerant pipes 7 and 8 flows uniformly into each refrigerant passage 2 so that efficient heat exchange is immediately performed between the inside refrigerant and the outside air by the wide heat transfer area of the flat surface of the heat transfer tubes 1 and the corrugated fin 11.
  • a plurality of louvers 11a and 11b for increasing the heat transfer efficiency with air are formed in the corrugated fins 11 along a plane from the upstream side to the downstream side and configured so that the front edges function to immediately improve the heat exchange performance between the refrigerant and the air.
  • the present invention is configured as below to achieve the above object.
  • a first solution according to the present invention is a heat transfer fin arranged on a heat transfer tube through which fluid flows for exchanging heat with air.
  • the heat transfer fin contacts air to exchange heat.
  • the heat transfer fin is made of foam metal having a pore density of 20 PIP or greater.
  • the foam metal has an open cell type porous structure with fine linear grooves continuously connected to one another enabling fluid to flow therethrough.
  • the surface area per unit volume is large. Therefore, the heat transfer area of the foam metal is large. The heat transfer is enhanced by disturbance in the fluid since the foam metal has a complex passage.
  • the foam metal includes linear grooves, a temperature boundary layer can be easily renewed, and a high heat transfer coefficient can be obtained.
  • the heat transfer performance of the heat transfer fin thus becomes extremely high.
  • the heat exchange performance of a heat exchanger is greatly improved when employing the heat transfer fin made of foam metal.
  • the passage configuration is complex in the foam metal and the pressure loss is large.
  • an optimal pore density must be determined when employing foam metal as the material for the heat transfer fin. According to the results of various analyses and experiments, the more preferable pore density for maximizing the heat transfer property of the foam metal is 20 PIP or greater.
  • the heat transfer tube through which fluid flows for exchanging heat with air is provided as a plurality, and the plurality of heat transfer tubes are set at an interval of 12 mm or less.
  • the heat transfer fin made of foam metal has a superior heat transfer performance since the surface area per unit volume is large and the heat transfer area is large.
  • the fin efficiency is low compared to a louver fin or the like because the foam metal has fine linear grooves. Therefore, the interval of the plurality of heat transfer tubes must be optimized. According to the results of various analyses, the interval of the plurality of heat transfer tubes is effective when it is 12 mm or less, and the heat transfer performance is sufficiently improved especially when the pore density is 20 PIP or greater.
  • a heat exchanger is a stacked type heat exchanger.
  • the stacked type heat exchanger is configured so that the heat transfer tube is flat and extends in the air flowing direction, and so that the heat transfer fin arranged in between is sufficiently long in the air flowing direction. Therefore, the stacked type heat exchanger itself has high heat transfer performance.
  • the heat transfer performance further improves when employing the heat transfer fin made of foam metal in the stacked air-heat exchanger.
  • a heat exchanger having a high heat exchange capability and appropriate for use in an air conditioner is formed with low cost, and miniaturization of the heat exchanger is achieved.
  • the pore density is 20 PIP or greater and 60 PIP or less.
  • the optimal upper limit value of the bore density is obtained through various analyses and experiments.
  • an interval H between the plurality of heat transfer tubes is set at 4 mm or greater and 12 mm or less.
  • the foam metal has superior heat transfer performance since the surface area per unit volume is large and the heat transfer area is large.
  • the fin efficiency is low. Therefore, the interval for the plurality of heat transfer tubes must be optimized. From the results of various experiments, the heat transfer performance improved when the interval of the heat transfer tubes was 4 mm or greater and 12 mm or less.
  • Figs. 1 and 2 show the configuration for an entire heat exchanger and the main part thereof according to preferred embodiment 1 of the present invention.
  • the heat exchanger 10 is configured so that a plurality of parallel flat heat transfer tubes 1 extend between pipe shaped upper and lower headers 12A and 12b through which refrigerant flows in and out.
  • the heat transfer tubes 1 are connected to the headers 12A and 12B and extend in a direction orthogonal to the headers 12A and 12B.
  • the heat transfer fin 13 is not the corrugated fin of the prior art and is made of foam metal of open cell type having a porous structure, as shown in Fig. 2, that allows fluid to flow therethrough.
  • the heat transfer tube 1 has a plurality of refrigerant passage grooves with square cross-sections partitioned by partitions in the same manner as the prior art shown in Fig. 32.
  • Refrigerant which is drawn into and distributed by the external refrigerant piping 7 or 8, flows uniformly through each refrigerant passage groove from the upper side toward the lower side or from the lower side toward the upper side via the upper header 12A or the lower header 12B.
  • Heat exchange is immediately and efficiently performed with the ambient air through the heat transfer surface of the refrigerant flowing through each refrigerant passage and the fin surface with the porous structure in the heat transfer fin 13 made of foam metal.
  • the foam metal forming the heat transfer fin 13 is a porous substance. Therefore, the foam metal has a large heat transfer area since the surface area per unit volume is large and complex passages are formed therein. Thus, effective heat transfer promotion may be expected due to the disturbance of the fluid. Since foam metal has many fine linear groves connected to each other (see structure Fig. 2), a temperature boundary layer may easily be renewed, and an extremely high heat transfer coefficient can be obtained.
  • the heat exchanger 10 having such a configuration is used, for example, as a condenser, the refrigerant introduced from the external refrigerant piping 7 via the upper header 12A is uniformly distributed to flowed from the upper side to the lower side of the heat transfer tube 1, and discharged from the outer refrigerant pipe 8 through the lower header 12B. If the heat exchanger 10 is used as an evaporator, the refrigerant flows in the opposite direction.
  • the heat transfer tubes 1 are flat and elongated in the air flow direction, and the heat transfer fins 13 arranged in between also extend in the air flowing direction.
  • the heat transfer fins 13 are easily formed by foaming and molding a metal having a high heat transfer coefficient, such as aluminum or copper, into a shape that can be brazed.
  • the heat exchanger suitable for use in an air conditioner may be formed with a reduced size at a lower cost and with a high heat exchange performance.
  • the foam metal forming the heat transfer fin 13 of the present embodiment is a porous substance, in which the surface area per unit area expands as the pore density PPI becomes higher as in (A) 10 PPI, (B) 20 PPI and (C) 40 PPI shown in Figs. 3(A), (B) and (C).
  • the PPI pore per inch
  • the PPI represents the density of gas bubbles per cubic inch.
  • the pore density PPI of the foam metal was found to be generally preferable at 20 PPI (Figs. 3(B), (C)) or greater and 60 PPI or less.
  • the interval (fin width) H of the heat transfer tube 1 must have an optimal value. According to the results of various analyses and experiments, the interval H of the heat transfer tube 1 was found to be optimal in the range of 4 mm or greater and 12 mm or less.
  • the interval H of the heat transfer tube 1 is effective when it is 4 mm or greater and 12 mm or less, as described below.
  • the heat transfer performance QN (W/m 3 ) per unit volume with respect to the front surface wind velocity V f greatly improves compared to that for the louver fin, as shown in the graph of Fig. 4, if the interval H of the heat transfer tube 1 is 4 mm or greater and 12 mm or less when the pore density of the heat transfer fin 13 made of foam metal is greater than or equal to 20 PPI and less than or equal to 60 PPI.
  • the dimensions 5 mm, 8 mm, 12 mm in the examples of Figs. 4 and 5 are three sets of dimensional data used to analyze the interval (hereinafter considered as width of heat transfer fin 13) H of the heat transfer tube 1.
  • a foam metal made of aluminum (aluminum alloy 6010) was used for the heat transfer fin as the open cell type tested foam metal.
  • Three types of the foam metal having a pore density PPI of, for example, No. 1, 10 PPI shown in Fig. 3(A); No. 2, 20 PPI shown in Fig. 3(B); and No. 3, 40 PPI shown in Fig. 3(C) were prepared.
  • three heat transfer tubes having different width dimensions (i.e., interval of heat transfer tube 1) H of 5 mm, 8 mm, and 12 mm were prepared for each of the three types of bore density PPI.
  • heat exchange was performed between the refrigerant (warm water as one example) at the heat transfer tube side 1 in the configuration of Fig. 1 and the air flowing outside.
  • the pressure loss and the heat transfer coefficient of the heat transfer fin for each case were experimentally obtained, and analysis was performed to clarify the basic heat transfer property and the influence of the wall surface of the heat transfer tube 1 serving as the heat source.
  • the experiments were conducted under the conditions of 20°C for air temperature and 50% for relative humidity.
  • the measurement of the pressure loss was performed in a non-load condition in which no warm water was supplied to the heat transfer tube 1, and the measurement of the heat transfer coefficient was performed by supplying warm water of 50°C as a warm heat source.
  • the wind velocity range was 0.5 to 2.3 m/s in terms of the wind velocity V f at the front surface side (upstream side) of the heat transfer fin 13.
  • the specific material of the aluminum foam metal used in this experiment was aluminum alloy 6101, as mentioned above.
  • the detailed specification is shown in [Table 1].
  • fins of the three widths H of 5 mm, 8 mm, and 12 mm were prepared.
  • the height L of the foam metal was 89 mm
  • the depth D was 13 mm
  • the surface area per unit volume was ⁇ .
  • the graph of Fig. 6 shows the relationship of the pressure loss P(Pa) with respect to the front surface wind velocity V f (m/s).
  • the pressure loss ⁇ P increases as the pore density PIP increases, or as the pore size d pore decreases. Further, the pressure loss ⁇ P increases as the fin width H decreases. This is because the surface area (including wall surface) per unit volume increases as the pore size d pore decreases and the fin width H decreases.
  • the pressure loss property of the foam metal is expressed as follows using the permeability (K) and the Ergun coefficient (C E ).
  • K permeability
  • C E Ergun coefficient
  • the graph of Fig. 7 is obtained, for example, when K and CE obtained through the least-square method using equation (1) are shown in relation with the pore size d pore .
  • K increases as the pore size d pore increase
  • the fin width H increases as the friction caused by the wall surface decreases.
  • C E slightly decreases as the pore size d pore increases.
  • a definite tendency cannot be found in the influence of the fin width H.
  • Fig. 8 shows change in the friction loss coefficient f with respect to Re K .
  • the graph of Fig. 9 shows the product of the measured heat transfer coefficient ha and the surface area ⁇ per unit area.
  • Qa is the heat transfer amount
  • At is the total heat transfer area combining the surface area of the foam metal and the area of the wall surface
  • ⁇ T LMTD is the logarithmic mean temperature difference.
  • ha ⁇ represents the heat transfer performance per unit volume. It is apparent here that the heat transfer performance increases as the pore density PPI increases and the smaller the fin width H decreases. In particular, the heat transfer performance becomes higher than the conventional louver fin in the 20 PIP No. 2 fin sample and the 40 PIP No. 3 fin sample. This suggesting the possibility of sufficient miniaturization of the heat exchanger.
  • the heat transfer coefficient h o should not include the fin efficiency for optimal designing.
  • the heat transfer coefficient h o cannot be easily obtained due to the complex passage shape resulting from foam metal. Accordingly, h o is obtained through the following approximation method.
  • the pressure loss and the heat transfer coefficient in this case were experimentally obtained and analyzed to clarify the basic heat transfer property and the influence of the wall surface of the heat transfer tube 1 serving as the heat source.
  • the experiments were conducted under the conditions of 20°C for air temperature and 50% for relative humidity.
  • the measurement of the pressure loss was performed in a non-load condition in which no cold water was supplied to the heat transfer tube 1, and the measurement of the heat transfer coefficient was performed by supplying cold water of 50°C as a cold heat source.
  • the wind velocity range was 0.5 to 2.3 m/s in terms of the wind velocity V f at the front surface side (upstream side) of the heat transfer fin 13.
  • the specific material for the aluminum foam metal used in this experiment is aluminum alloy 6101, as mentioned above.
  • fins of the three widths H of 5 mm, 8 mm, and 12 mm were prepared.
  • the height L of the foam metal in the vertical direction was 89 mm
  • the depth D was 13 mm
  • the surface area per unit volume was ⁇ .
  • the graph of Fig. 12 shows the pressure loss ⁇ P/D(Pa/m) with respect to the front surface wind velocity V f (m/s) in the dry state.
  • the pressure loss is calculated by including the air flow direction length D (m) of at the fins ( ⁇ P/D). In the following description, this is simply referred to as ⁇ P.
  • Fig. 13 shows the pressure loss ⁇ P (Pa) with respect to the front surface wind velocity V f (m/s) in the wet state in when the temperature of the water serving as the refrigerant is 5°C
  • Fig. 14 shows the same state when the temperature of the water serving as the refrigerant is 10°C.
  • the influence of the pore density PPI and the fin width H is substantially the same as the tendency in the dry state.
  • the value of the pressure loss ⁇ P greatly increases compared to that in the dry state (see Fig. 12).
  • the pressure loss ⁇ P greatly increases because the condensed water accumulated on the fin surface becomes a ventilation resistance, and thus can be predicted that water drainage becomes an essential factor in comparison to the dry state.
  • the ratio of the pressure loss ⁇ P between the wet state and the dry state is shown in Fig. 15 (for a water temperature of 5°C) and Fig. 16 (for a water temperature of 10°C). In the case of water temperature of 5°C in Fig. 15, the ratio of the pressure loss gradually increases as a whole when the air flow rate increases but the pressure loss decreases when the air flow rate increases in the cases of 8 mm, 12 mm at 10°C (Fig. 16).
  • the ratio ⁇ P wet / ⁇ P dry of the pressure loss ⁇ P in a dry state and in a wet state increases as the pore density PPI increases.
  • the ratio is greater for the foam metal fin than for the louver fin. That is, the water drainage is poorer in the foam metal fin than the louver fin.
  • the foam metal fin used in the present test is in an experimental level in which the fin surface is not processed.
  • the problem of water drainage is sufficiently improved, for example, by applying a hydrophilic agent.
  • Fig. 17 shows the relationship of the heat transfer coefficient h dry with respect to the front surface wind velocity V f (m/s) in a dry state.
  • the heat transfer coefficient h dry increases as the pore density PIP decreases, and the heat transfer coefficient dry decreases as the fin width H increases.
  • Fig. 18 shows the relationship between h dry ⁇ and the front surface wind velocity V f (m/s) in the dry state. It is apparent that the heat transfer performance increases as the pore density PIP increases and the fin width H decreases.
  • Figs. 20 and 21 show the relationship of the heat transfer coefficient h wet in the wet state with respect to the front surface wind velocity V f (m/s) in the wet state when the temperature of cold water is 5°C and 10°C.
  • V f m/s
  • h wet is slightly smaller than h dry .
  • this is because the fin efficiency decreases in a dry state due to the heat transfer of latent heat resulting from condensation of the moisture in air.
  • Fig. 22 water temperature 5°C
  • Fig. 23 water temperature 10°C
  • Fig. 24 water temperature 5°C
  • Fig. 25 water temperature 10°C
  • the substance transfer coefficient h mass of Fig. 24 increases as the entire air flow rate and fin width H increase and as the pore density PIP decreases.
  • the foam metal fin of the present embodiment has higher pressure loss and higher heat transfer coefficient per volume compared to the existing louver fin.
  • the pressure loss and the heat transfer coefficient must be comprehensively analyzed.
  • V is the volume
  • a c is the flow cross-sectional area
  • Figs. 26 and 27 show the heat transfer coefficients h dry ⁇ , h wet ⁇ per unit volume for the dry state and the wet state in relation to the pump power EBA necessary per unit volume.
  • the wet state of Fig. 27, for 40 PPI, H 5 mm, 8 mm, and 12 mm, the heat transfer performance improvement effect is higher by about 28%.
  • Fig. 29 shows the structure for an air-heat exchanger according to a second embodiment of the present invention.
  • the present embodiment relates to a serpentine heat exchanger in which a flat heat transfer tube 21 is bent into a serpentine shape as a single continuous structure.
  • the high heat transfer performance is also achieved in the heat exchanger of such configuration in the same manner as the heat exchanger of the first embodiment described above.
  • Fig. 30 shows the structure for a heat exchanger according to a third embodiment of the present invention.
  • a plurality of plate shaped heat transfer tubes 31 extending in the horizontal direction are connected in a stack form by left and right connecting members 22, and the heat transfer fin 13 made of foam metal is arranged between the connecting members 22 of each layer.
  • Each heat transfer tube 31 includes refrigerant inlet and outlet holes 23.
  • the holes 23 connected through the connecting members 22 form a refrigerant passage.
  • the connecting members 22 are used for a structure similar to that of the first embodiment in a stacked plate type air-heat exchanger.
  • the heat transfer fin of the present invention is not limited to the structure of the heat exchanger in each embodiment and may obviously be applied to a heat transfer fin for performing heat exchange with air, such as a cross fin type or the like.

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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)
EP05730153A 2004-04-16 2005-04-18 Ailette de transfert thermique pour échangeur de chaleur Withdrawn EP1739377A4 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2004122141 2004-04-16
JP2005053087A JP2005326136A (ja) 2004-04-16 2005-02-28 空気熱交換器用伝熱フィン
PCT/JP2005/007383 WO2005100898A1 (fr) 2004-04-16 2005-04-18 Ailette de transfert thermique pour échangeur de chaleur

Publications (2)

Publication Number Publication Date
EP1739377A1 true EP1739377A1 (fr) 2007-01-03
EP1739377A4 EP1739377A4 (fr) 2009-12-02

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EP05730153A Withdrawn EP1739377A4 (fr) 2004-04-16 2005-04-18 Ailette de transfert thermique pour échangeur de chaleur

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US (1) US20080296008A1 (fr)
EP (1) EP1739377A4 (fr)
JP (1) JP2005326136A (fr)
WO (1) WO2005100898A1 (fr)

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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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EP1831633A1 (fr) * 2004-12-03 2007-09-12 Andries Meuzelaar Echangeur de chaleur pour moyen de transport motorise, et moyen de transport motorise pourvu de cet echangeur de chaleur
CN101806550B (zh) * 2010-03-24 2014-02-19 三花控股集团有限公司 微通道换热器
CN102331195A (zh) * 2010-07-12 2012-01-25 上海德朗汽车零部件制造有限公司 一种b型管铝质管带式水箱散热器
EP2671039B1 (fr) * 2011-02-04 2019-07-31 Lockheed Martin Corporation Échangeur de chaleur à ailettes en mousse
US9279626B2 (en) * 2012-01-23 2016-03-08 Honeywell International Inc. Plate-fin heat exchanger with a porous blocker bar
EP2843348B1 (fr) * 2013-08-29 2016-05-04 Linde Aktiengesellschaft Échangeur de chaleur à plaques doté de blocs d'échangeur de chaleur reliés par une mousse métallique
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
WO2018117484A1 (fr) * 2016-12-20 2018-06-28 엘지이노텍 주식회사 Tige chauffante, module de chauffage comprenant celle-ci et dispositif de chauffage comprenant celle-ci
DE102018214912A1 (de) * 2018-09-03 2020-03-05 Hanon Systems Kühler für ein Fahrzeug
US11066970B2 (en) * 2019-04-08 2021-07-20 Hyundai Motor Company Tube-pin assembly for heat exchanger of vehicle
CN112179976A (zh) * 2019-07-04 2021-01-05 霍尼韦尔国际公司 气体湿度降低设备以及其使用方法
US11828501B2 (en) * 2019-07-30 2023-11-28 Ut-Battelle, Llc Metal foam heat exchangers for air and gas cooling and heating applications
CN113473762B (zh) * 2020-03-30 2022-12-13 华为技术有限公司 设备外壳、设备和激光雷达

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS52134153A (en) * 1976-05-04 1977-11-10 Nippon Denso Co Ltd Layer-built heat exchanger
JPS56155391A (en) * 1980-04-30 1981-12-01 Nippon Denso Co Ltd Corrugated fin type heat exchanger
JPS60294A (ja) * 1983-06-16 1985-01-05 Matsushita Seiko Co Ltd 発泡金属を用いた熱交換器
KR19990085965A (ko) * 1998-05-23 1999-12-15 박호군 다공핀 평판관형 열교환기
NL1016713C2 (nl) * 2000-11-27 2002-05-29 Stork Screens Bv Warmtewisselaar en een dergelijke warmtewisselaar omvattende thermo-akoestische omvorminrichting.

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
No further relevant documents disclosed *
See also references of WO2005100898A1 *

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014029465A1 (fr) * 2012-08-18 2014-02-27 Audi Ag Échangeur thermique
US9664459B2 (en) 2012-08-18 2017-05-30 Audi Ag Heat exchanger with a porous metal structure having manifolds and tubes
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
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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EP1739377A4 (fr) 2009-12-02
US20080296008A1 (en) 2008-12-04
WO2005100898A1 (fr) 2005-10-27
JP2005326136A (ja) 2005-11-24

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