EP2942595B1 - Wärmetauschervorrichtung und klimaanlage - Google Patents

Wärmetauschervorrichtung und klimaanlage Download PDF

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Publication number
EP2942595B1
EP2942595B1 EP15160937.7A EP15160937A EP2942595B1 EP 2942595 B1 EP2942595 B1 EP 2942595B1 EP 15160937 A EP15160937 A EP 15160937A EP 2942595 B1 EP2942595 B1 EP 2942595B1
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EP
European Patent Office
Prior art keywords
groove
grooves
fin
heat exchanging
width
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EP15160937.7A
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English (en)
French (fr)
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EP2942595A1 (de
Inventor
Yoshihiro Hara
Kenichi Murakami
Kenji Aoyagi
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Mitsubishi Heavy Industries Thermal Systems Ltd
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Mitsubishi Heavy Industries Thermal Systems Ltd
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Publication of EP2942595A1 publication Critical patent/EP2942595A1/de
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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
    • F28F13/18—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by applying coatings, e.g. radiation-absorbing, radiation-reflecting; by surface treatment, e.g. polishing
    • F28F13/185—Heat-exchange surfaces provided with microstructures or with porous coatings
    • F28F13/187—Heat-exchange surfaces provided with microstructures or with porous coatings especially adapted for evaporator surfaces or condenser surfaces, e.g. with nucleation sites
    • 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
    • F28F17/00—Removing ice or water from heat-exchange apparatus
    • F28F17/005—Means for draining condensates from heat exchangers, e.g. from 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2245/00—Coatings; Surface treatments
    • F28F2245/04—Coatings; Surface treatments hydrophobic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2255/00—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes
    • F28F2255/20—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes with nanostructures

Definitions

  • the present invention relates to a heat exchanging apparatus and an air conditioning apparatus.
  • a heat exchanging apparatus configuring an air conditioning apparatus includes a tube inside which a refrigerant flows and a fin thermally coupled to the tube, and performs heat exchange between the refrigerant inside the tube and air passing through between the fins.
  • a coating is performed on a surface of the fin for giving hydrophilicity or water repellency to the fin, in order to prevent decrease of efficiency with increase of ventilation resistance between the fins due to dew condensation and frost formation on the fin of the heat exchanging apparatus, or to prevent water splashes from the fin to an air conditioner space.
  • the fin is typically made of aluminum, and a surface of an aluminum material shows slight hydrophilicity, but it is desirable that the fin has higher hydrophilicity or sufficient water repellency.
  • water repellency or hydrophilicity depends on chemical properties and surface roughness of a material. It has been known that as surface roughness increases by forming small unevenness on the surface, the surface of the material shows higher hydrophilicity or water repellency (Wenzel's equation).
  • Patent Literature 1 an uneven structure is formed on a surface of an aluminum member (fin) by soaking the fin in acid, and then a water repellency coating is performed thereon using a fluorine-based resin material, so that the fin has higher water repellency than that of the fin on which the water repellency coating is only performed.
  • WO 2013/084473 A1 discloses a heat exchanging apparatus according to the preamble of claim 1.
  • a coating of a fin of a heat exchanging apparatus is performed by soaking in a coating liquid a sheet material forming the fin, or an assembly in which the fin and a tube are fit together. Therefore, in order to perform the coating, a liquid tank fit for a size of the fin for storing the coating liquid and the coating liquid that fills the liquid tank are necessary, which increases cost corresponding to the coating liquid and the liquid tank.
  • the coating step is necessary. Before the coating, acid cleaning, water washing, a conversion coating of a base and the like are necessary, and after the coating, burning is performed, which increase steps and also take time. In particular, when the coating is performed on a fin of a heat exchanger disposed outdoors, it is difficult to secure durability of the coating which can withstand long-term use.
  • the present invention has been made in view of the above problems, and an object thereof is to provide a heat exchanging apparatus that suppresses the problem of increasing ventilation resistance due to dew condensation and frost formation on the fin by giving the sufficient water repellency to the surface of the fin without performing the coating, and an air conditioning apparatus including the heat exchanging apparatus.
  • the present invention adopts the following solutions.
  • a heat exchanging apparatus includes: a plurality of fins each having a plate shape and extending in a vertical direction, the plurality of fins being arranged successively in a horizontal direction in a state that surfaces of the adjacent pair of fins are parallel to each other; and a heat transfer tube inside which a refrigerant flows, the heat transfer tube being inserted into a tube hole provided on each of the plurality of fins while adhering.
  • a plurality of grooves each extending from a upper part to a lower part is formed on the surface of each of the fins at intervals in an arrangement direction orthogonal to the extending direction of each of the grooves, and a width of each of the grooves is 5 ⁇ m or more to 200 ⁇ m or less and a distance between edges of the adjacent grooves in the arrangement direction is 5 ⁇ m or more to twice or less the width of each of the grooves.
  • the width of each of the grooves formed on the surface of each of the plate shape fins at intervals in the arrangement direction is 5 ⁇ m or more to 200 ⁇ m or less.
  • a size of a waterdrop formed on the surface of the fin is 1 mm or more to 3 mm or less, the width of the groove is sufficiently narrower than the size of the waterdrop. Therefore, a phenomenon (bridge phenomenon) occurs, the bridge phenomenon being the phenomenon in which the waterdrop formed on an upper part of the groove does not reach a bottom of the groove and is disposed to extend over the groove from one edge to the other edge.
  • the water repellency of the surface of the fin becomes higher because the bridge phenomenon occurs.
  • the distance between the edges of the adjacent grooves is 5 ⁇ m or more to twice or less the width of each of the grooves.
  • the size of the waterdrop formed on the surface of the fin is 1 mm or more to 3 mm or less in diameter, the distance between the edges of the grooves is sufficiently smaller than the size of the waterdrop. Therefore, the surface of the fin between the edges of the grooves shows the sufficient water repellency.
  • the present invention can provide the heat exchanging apparatus that suppresses a problem of increasing ventilation resistance due to dew condensation and frost formation on the fin by giving the sufficient water repellency to the surface of the fin without performing a coating.
  • a contact angle formed between the surface of each of the fins and the waterdrop is ⁇ e
  • the water repellency is sufficiently shown.
  • the ratio of the depth of the groove to the width of the groove corresponds to 1/tan ⁇ e
  • the water repellency is sufficiently shown.
  • a ratio of a depth of each of the grooves to the width of each of the grooves is 1/tan ⁇ e or more.
  • the sufficient water repellency can be given to the surface of the fin.
  • the sufficient water repellency can certainly be given to the surface of the fin.
  • a cross section shape of each of the grooves may be rectangular in a plane orthogonal to the extending direction.
  • the sufficient water repellency can be given to the surface of the fin on which the plurality of grooves each having the rectangular cross section is formed.
  • each of the plurality of grooves extends from the upper part to the lower part along a vertical direction.
  • the waterdrop formed on the surface of the fin to which the water repellency is given can certainly be dripped toward the lower part of the fin by its own weight along the groove formed from the upper part to the lower part in the vertical direction.
  • each of the plurality of grooves extends from the upper part to the lower part along a direction inclined from a vertical direction.
  • the waterdrop formed on the surface of the fin to which the water repellency is given can certainly be dripped toward the lower part of the fin by its own weight along the groove formed from the upper part to the lower part in the direction inclined from the vertical direction.
  • An air conditioning apparatus of the present invention includes the heat exchanging apparatus according to any one of the first to fifth aspects; and a fan introducing air toward the heat exchanging apparatus.
  • each of the plurality of grooves extends from the upper part to the lower part along a direction inclined from a vertical direction, and extends in a direction descending from an upstream side to a downstream side of a flowing direction of the air introduced with the fan.
  • the waterdrop formed on the surface of the fin to which the water repellency is given can be dripped by its own weight along the groove formed from the upper part to the lower part in the direction inclined from the vertical direction. Further, the waterdrop formed on the surface of the fin can be dripped along the groove by the air introduced with the fan.
  • the waterdrop formed on the surface of the fin can be certainly dripped by action of its own weight and the air introduced with the fan.
  • the present invention can provide a heat exchanging apparatus that suppresses a problem of increasing ventilation resistance due to dew condensation and frost formation on a fin by giving sufficient water repellency to a surface of the fin without performing a coating.
  • the air conditioning apparatus 100 of the first embodiment includes an indoor unit 20 and an outdoor unit 30.
  • a refrigerant flows from the indoor unit 20 into the outdoor unit 30, or from the outdoor unit 30 into the indoor unit 20 through a pair of refrigerant piping 40.
  • the indoor unit 20 and the outdoor unit 30 are electrically connected to each other with electrical wiring (not illustrated).
  • the indoor unit 20 includes a rear surface base (not illustrated) and a front surface panel 21 which are integrally configured.
  • An indoor heat exchanging apparatus 22 of a plate fin tube type, an indoor fan 23 having a substantially cylindrical shape, and a control part 24 controlling operation of the indoor unit 20 are fitted to the base.
  • the outdoor unit 30 includes a casing 31.
  • An outdoor heat exchanging apparatus 32 heat exchanging apparatus
  • a propeller fan 33 fan
  • a compressor 34 compressor
  • an outdoor unit electrical equipment box 50 are provided inside the casing 31.
  • the outdoor unit 30 is provided with a baffle plate 35 on a substantially center position, the baffle plate 35 separating the inside of the outdoor unit 30 into two spaces.
  • the propeller fan 33 is disposed on the left space and the compressor 34 is disposed on the right space when the outdoor unit 30 is viewed from the front.
  • the propeller fan 33 rotates counterclockwise when the outdoor unit 30 is viewed from the front, and generates airflow inside the casing 31 in a direction from the rear surface to the front surface (direction indicated by an arrow in Fig. 2 ).
  • the propeller fan 33 is a device that introduces outside air (air) toward the outdoor heat exchanging apparatus 32 in this manner.
  • a fin guard (not illustrated) and a fan guard 36 are provided on the rear surface of the casing 31 from which the outdoor heat exchanging apparatus 32 faces the outside, and on the front surface of the casing 31 from which the propeller fan 33 faces the outside, respectively.
  • the fin guard is provided for preventing the fins 10 being damaged by unexpected impact from the outside.
  • the fan guard 36 is provided for protecting the propeller fan 33 from impact from the outside and also preventing dust included in outside air from coming into the inside of the casing 31.
  • the compressor 34 changes a gas refrigerant having a low temperature and pressure into a gas refrigerant having a high temperature and pressure and then discharges it.
  • a refrigerant circuit includes the compressor 34, the indoor heat exchanging apparatus 22, the outdoor heat exchanging apparatus 32, the refrigerant piping 40, an expansion valve (not illustrated), a four-way valve controlling the flowing direction of the refrigerant (not illustrated) and the like.
  • the refrigerant circuit is a circuit circulating the refrigerant between the indoor unit 20 and the outdoor unit 30 through the pair of refrigerant piping 40.
  • the gas refrigerant having the high temperature and pressure in the compressor 34 is pressure-fed to the indoor heat exchanging apparatus 22 of the indoor unit 20 through the refrigerant piping 40 illustrated in Fig. 1 .
  • the refrigerant having the high temperature and pressure and flowing through the indoor heat exchanging apparatus 22 gives heat to indoor air taken with the indoor fan 23.
  • hot air that is air to which the heat is given, is blown from an air outlet 21c.
  • the gas refrigerant having the high temperature and pressure is condensed to be liquefied by the heat exchange in the indoor heat exchanging apparatus 22, and becomes a liquid refrigerant having a high temperature and pressure.
  • the liquid refrigerant having the high temperature and pressure is decompressed with the expansion valve while being fed to the outdoor heat exchanging apparatus 32 of the outdoor unit 30, and has a low temperature and pressure.
  • the liquid refrigerant having the low temperature and pressure and flowing through the outdoor heat exchanging apparatus 32 takes heat from air newly taken from the outside into the inside of the casing 31 with the propeller fan 33.
  • the liquid refrigerant having the low temperature and pressure is evaporated to be gasified, and becomes a gas refrigerant having a low temperature and pressure.
  • the gas refrigerant having the low temperature and pressure is fed to the compressor 34 to have a high temperature and pressure.
  • the air conditioning apparatus 100 performs the heating operation by repeating the above steps.
  • the refrigerant flows in the refrigerant circuit in a direction opposite to the direction during the heating operation. That is, the gas refrigerant having the high temperature and pressure in the compressor 34 is pressure-fed to the outdoor heat exchanging apparatus 32 through the refrigerant piping 40.
  • outdoor air takes heat from the gas refrigerant, so that the gas refrigerant is condensed to be liquefied.
  • the gas refrigerant having the high temperature and pressure becomes a liquid refrigerant having a high temperature and pressure.
  • the liquid refrigerant having the high temperature and pressure is decompressed with the expansion valve to have a low temperature and pressure, and is fed to the indoor heat exchanging apparatus 22 through the refrigerant piping 40 again.
  • the liquid refrigerant having the low temperature and pressure takes heat from indoor air, and then cool air is blown from the air outlet 21c and the refrigerant itself is evaporated to be gasified.
  • the liquid refrigerant having the low temperature and pressure becomes a gas refrigerant having a low temperature and pressure.
  • the gas refrigerant is fed to the compressor 34 again to have a high temperature and pressure.
  • the air conditioning apparatus 100 performs the cooling operation by repeating the above steps.
  • the outdoor heat exchanging apparatus 32 of this embodiment is a fin and tube type heat exchanging apparatus.
  • the outdoor heat exchanging apparatus 32 is provided with a plurality of fins 10 each having a plate shape extending along an axis X extending in a vertical direction.
  • the plurality of fins 10 is arranged successively in a horizontal direction in a state that surfaces of the adjacent pair of fins 10 are parallel to each other.
  • reference numeral 10 is given to the only two fins, and is not given to the other fins to omit the description thereof.
  • the plurality of fins 10 is arranged such that it does not disturb the flowing of the air introduced with the propeller fan 33 and can transfer heat efficiently to the introduced air.
  • each of the fins 10 is provided with tube holes 10B, and a heat transfer tube 40A is inserted into each of the tube holes 10B.
  • the heat transfer tube 40A is a part of the refrigerant piping 40, and is a component through which the refrigerant flows in the outdoor heat exchanging apparatus 32.
  • the heat transfer tube 40A is inserted into the tube hole 10B while adhering, and the refrigerant (liquid) flows thereinside.
  • the fin 10 is made of a metallic material having high heat transfer ability. Therefore, the fin 10 can transfer the heat having transferred from the refrigerant to air around the fin 10 efficiently.
  • the metallic material forming the fin 10 for example, an aluminum material, an aluminum material on which a conversion coating is performed, or a stainless steel material can be used.
  • arrows in Figs. 4(a) and (b) each indicate a flowing direction of the air introduced with the propeller fan 33.
  • reference numeral 12 is given to the only two grooves, and is not given to the other grooves to omit the description thereof.
  • the surface of the fin 10 is formed with the plurality of grooves 12 each extending from an upper part to a lower part along an axis X extending in a vertical direction.
  • the plurality of grooves 12 is formed at fixed intervals in an arrangement direction orthogonal to the extending direction of the groove 12 (axis x direction).
  • the grooves 12 are provided in order to prevent waterdrops attached to the surface of the fin 10 forming a large lump to cause dew condensation and frost formation. More specifically, the grooves 12 are provided for making the surface of the fin 10 show sufficient water repellency and making the waterdrops attached to the fin 10 drip toward the lower part of the fin 10.
  • Fig. 4(b) illustrates a modified example of the fin 10.
  • the surface of the fin 10 in the modified example is formed with the grooves 12 each extending from an upper part to a lower part along a direction inclined from the vertical direction.
  • the plurality of grooves 12 is formed at fixed intervals in an arrangement direction orthogonal to the extending direction of the groove 12 (direction inclined from the axis x direction).
  • an angle formed between an axis Y1 indicating the extending direction of the groove 12 and the axis x along the vertical direction is an angle Z1 in a plane where the surface of the fin 10 is disposed.
  • the reason why the axis Y1 is inclined from the axis X by the angle Z1 in this manner is to utilize power of the air introduced with the propeller fan 33 for making the waterdrops formed on the surface of the fin 10 drip toward the lower part of the fin 10.
  • the groove 12 extends in a direction descending from an upstream side to a downstream side of the air flowing direction indicated by the arrow. Therefore, the waterdrops formed on the surface of the fin 10 can be dripped along the grooves 12 by the air introduced with the propeller fan 33.
  • the angle Z1 described above is set to any value larger than 0° and smaller than 90° depending on various conditions, such as the number of rotations, or air volume of the propeller fan 33.
  • the angle Z1 becomes closer to 0°, the power of the air introduced with the propeller fan 33 becomes difficult to be utilized, and as the angle Z1 becomes closer to 90°, waterdrop's own weight becomes difficult to be utilized. Therefore, in order to utilize both the power of the air introduced with the propeller fan 33 and the waterdrop's own weight, it is desirable that the angle Z1 is set to about 40° (for example, 20° or more to 60° or less).
  • a relationship between a width 12W of the groove 12 formed on the surface of the fin 10 and a pitch 12P indicating a distance in the arrangement direction between edges of the adjacent grooves 12 satisfy conditions of the following equations (1) and (2). 5 ⁇ ⁇ m ⁇ width 12 ⁇ W ⁇ 200 ⁇ m 5 ⁇ ⁇ m ⁇ pitch 12 ⁇ P ⁇ width 12 ⁇ W ⁇ 2
  • the surface small structure 10A includes a surface 11 of a material on which a coating for giving water repellency or hydrophilicity is not performed, and the plurality of grooves 12 formed on the surface 11.
  • Each of the plurality of grooves 12 has a cross section (cross section in a plane orthogonal to the extending direction of the groove 12) of a rectangular shape, and extends linearly.
  • the plurality of grooves 12 is arranged in parallel to each other at predetermined intervals in the arrangement direction orthogonal to the extending direction of the groove 12.
  • a dimension in the arrangement direction orthogonal to the length direction of the extending groove 12A (width 12W) is sufficiently smaller than a diameter of the waterdrop.
  • the diameter of the waterdrop is about 1 mm to 3 mm.
  • the grooves 12 are arranged alternately on a surface side 101 and a back side 102 of the fin 10. That is, the groove 12 on the back side 102 is located between the adjacent grooves 12 on the surface side 101, and the groove 12 on the surface side 101 is located between the adjacent grooves 12 on the back side 102.
  • the material itself has hydrophilicity of a contact angle about 45° to 84°, but a ratio of a depth 12D to the width 12W of the groove 12 is determined on the basis of predetermined basic criteria Cr1 (see Fig. 6 ), so that water repellency can be obtained.
  • the basic criteria Cr1 depth 12D/width 12W of the groove 12
  • the basic criteria Cr1 is 1/tan ⁇ e assuming that a contact angle formed between the smooth surface (surface 11) of the material of the fin 10 and the waterdrop is ⁇ e.
  • a shape of the groove 12 is determined such that the ratio of the depth 12D to the width 12W of the groove 12 becomes larger than the basic criteria Cr1.
  • the depth 12D/width 12W of the groove 12 is one of factors influencing the contact angle ⁇ e of the surface small structure 10A, and the basic criteria Cr1 prescribing the depth 12D/width 12W of the groove 12 determines a threshold between the water repellency and the hydrophilicity of the surface small structure 10A on which the groove 12 is formed.
  • Fig. 6 illustrates a relationship between the contact angle ⁇ e formed between the smooth surface of the material and the waterdrop, and the depth 12D/width 12W of the groove 12.
  • the contact angle ⁇ e is formed between the smooth surface on which the groove 12 is not formed and the waterdrop, and is constant without depending on the size of the waterdrop, or posture of the material disposed.
  • a basic criteria zone B1 including the basic criteria Cr1 and near values of its upper and lower sides is set.
  • the depth 12D/width 12W of the groove 12 is determined such that it becomes larger than the basic criteria zone B1.
  • the upper side means an area where the value of the depth 12D/width 12W of the groove 12 is larger than the basic criteria Cr1.
  • the lower side means an area where the value of the depth 12D/width 12W of the groove 12 is smaller than the basic criteria Cr1.
  • the basic criteria zone B1 is within a range of basic criteria Cr1 1 where the contact angle ⁇ e is smaller than a measured value by 10% (in the case of 0.9 ⁇ e) to basic criteria Cr1 2 where the contact angle ⁇ e is larger than the measured value by 10% (in the case of 1.1 ⁇ e). Even if the contact angle ⁇ e includes a measurement error, the surface small structure 10A becomes water repellent in the area F1 where the depth 12D/width 12W of the groove 12 is larger than the basic criteria zone B1.
  • the surface small structure 10A becomes hydrophilic.
  • the surface small structure 10A can be water repellent because a bridge phenomenon to be described later occurs, so that the depth 12D/width 12W of the groove 12 may be set within the range.
  • the measured value of the contact angle ⁇ e is about 45° to 90° in the case where the material is aluminum.
  • the contact angle ⁇ e is about 50° to 70°.
  • the contact angle ⁇ e is about 80° to 90°.
  • the inventor focused on entanglement of air between the material and the waterdrop as one of factors influencing the contact angle ⁇ e.
  • sensitivity evaluation of shape factors to the contact angle ⁇ e was performed using Taguchi methods (quality engineering).
  • the shape factors used for the evaluation are the width 12W, the depth 12D, and the pitch 12P of the groove 12, cross section shapes of the groove 12 (rectangle, U-shape (including an arc shape), V-shape), and patterns formed by the plurality of grooves 12 (latticed pattern, striped pattern, spotted pattern).
  • Results illustrated in Fig.8 were obtained by the sensitivity evaluation.
  • a vertical axis in Fig. 8 indicates an influence degree (sensitivity) of each factors on the contact angle ⁇ e, the water repellency becomes higher as the vertical axis approaches to the upper side of Fig. 8 , and the hydrophilicity becomes higher as the vertical axis approaches to the lower side of Fig. 8 .
  • the sensitivity of the width 12W, and the depth 12D of the groove 12, and the pattern to the contact angle ⁇ e are larger than that of the other factors.
  • the water repellency becomes higher.
  • the width 12W of the groove 12 becomes wider, or as the depth 12D of the groove 12 becomes shallower, the hydrophilicity becomes higher.
  • Condition 1 the uneven structure of the surface small structure 10A (width 12W, the depth 12D, the pitch 12P of the groove 12 and the like) is sufficiently smaller than the diameter of the waterdrop.
  • Condition 3 the waterdrop behaves such that a surface area thereof becomes smaller (minimization of surface energy).
  • the waterdrop 14 is spherical before coming in contact with the surface small structure 10A ( Fig. 9(a) ), and then part of the spherical surface of the waterdrop 14 comes in contact with the surface 11 of the surface small structure 10A ( Fig. 9(b) ).
  • the waterdrop 14 also comes in contact with next surfaces 11B and 11C while extending over both side grooves 12, 12 from the contact portion (surface 11A) ( Fig. 9(c) ). While repeating the behaviors the number of times depending on a volume of the waterdrop 14, the waterdrop 14 spreads to be stable ( Fig. 9(d) ). A contact angle ⁇ actually formed between the surface small structure 10A and the waterdrop 14 is measured in the state of Fig. 9(d) .
  • the waterdrop 14 comes in contact with the surface 11A of the surface small structure 10A. Since the uneven structure of the surface small structure 10A is sufficiently smaller than the diameter of the waterdrop 14 (condition 1), the waterdrop 14 comes in contact with the surface 11A, which is a top surface of a projection portion between the grooves 12, 12, and spreads to one edge 121 of an opening of the groove 12.
  • the waterdrop 14 tends to enter toward a deeper position of the groove 12, but does not reach a bottom 124 of the groove 12 and reaches the other edge 122 (opposite side) of the groove 12.
  • a cross section shape of the waterdrop 14 inside the groove 12 at the time of reaching the opposite surface 11B after the waterdrop 14 extending over the groove 12 can be approximated by a straight line as illustrated in Fig. 10(c) from the condition 3.
  • the waterdrop 14 partitions the groove 12 into the inner side and the outer side, and thus the air 15 is entangled between the waterdrop 14 and the material.
  • the waterdrop 14 further spreads on the surface 11B as illustrated in Fig. 10(d) .
  • the waterdrop 14 behaves such that the surface area thereof becomes smaller (condition 3)
  • the waterdrop 14 does not swell downward inside the groove 12 and keeps a straight line shape.
  • the waterdrop 14 repeats the behaviors in Figs. 10(a) to (d) to be stable (see Fig. 9(d) ).
  • Figs. 10(a) to (d) only the right side of the waterdrop 14 is illustrated, but the left side of the waterdrop 14 also spreads like the right side. Further, the waterdrop 14 also spreads in the length direction of the groove 12 (direction orthogonal to the paper surface) to be stable in a state that its own weight and surface tension are balanced.
  • the waterdrop 14 comes in contact with the surface 11A of the surface small structure 10A. Since the uneven structure of the surface small structure 10A is sufficiently smaller than the diameter of the waterdrop 14 (condition 1), the waterdrop 14 comes in contact with the surface 11A, which is the top surface of the projection portion between the grooves 12, 12, and spreads to one edge 121 of the opening of the groove 12.
  • the waterdrop 14 flows out from the other edge 122 (opposite side) of the groove 12 into the surface 11B. That is, when the groove 12 is shallow, the air 15 is not entangled between the waterdrop 14 and the material. Thereafter, the waterdrop 14 repeats the behaviors in Figs. 11(a) to (d) to be stable.
  • a diagram of a model of the groove 12 configuring the surface small structure 10A was drawn ( Fig. 12(a) ). Based on this model, a geometric relationship of the width 12W and the depth 12D of the groove 12 is obtained.
  • the cross section of the groove 12 can be illustrated by a two-dimensional shape and the shape of the waterdrop entered into the inside of the groove 12 can be illustrated by a straight line for simplicity.
  • a value of the depth 12D can be expressed as A/tan ⁇ e.
  • the value of the depth 12D/width 12W of the groove 12 is 1/tan ⁇ e.
  • this 1/tan ⁇ e basic criteria Cr1
  • the basic criteria Cr1 depth 12D/width 12W
  • the basic criteria Cr1 is also determined depending on the contact angle ⁇ e.
  • the smooth surface of the aluminum alloy material of the fin 10 has the contact angle ⁇ e of about 84°, if the ratio of the depth 12D to the width 12W of the groove 12 exceeds 0.1, which is the basic criteria Cr1, the water repellency becomes higher (see an upward arrow), and if the ratio is less than 0.1, the hydrophilicity becomes higher (see a downward arrow).
  • the value of the depth 12D/width 12W of the groove 12 is set larger than 0.1.
  • the water repellency becomes higher with distance from the basic criteria Cr1 within the area F1 where the value of the depth 12D/width 12W of the groove 12 is larger than the basic criteria Cr1, and thus the necessary water repellency can be obtained by adjusting the size of the depth 12D/width 12W of the groove 12.
  • the basic criteria Cr1 as described above is set to the groove 12 having the inner wall 123 perpendicular to the surface 11 and the rectangular cross section shape ( Fig. 12(a) ).
  • Fig. 13(a) illustrates a case where the inclination angle ⁇ w is small
  • Fig. 13(b) illustrates a case where the inclination angle ⁇ w is large.
  • the inclination criteria Cr2 (depth/width) is expressed by the following equation (3).
  • Cr 2 cos ⁇ e ⁇ ⁇ w / tan ⁇ w ⁇ cos ⁇ e ⁇ ⁇ w + sin ⁇ e ⁇ ⁇ w
  • Fig. 14 illustrates the inclination criteria Cr2 in the case where the contact angle ⁇ e is 84° (aluminum material).
  • the contact angle ⁇ e is 84° (aluminum material).
  • the depth 12D of the groove 12 required to form the bridge increases.
  • the inclination angle ⁇ w increases to the predetermined angle or more (herein, about 45° or more), the bridge phenomenon does not occur.
  • an inclination criteria zone B2 including the inclination criteria Cr2 and near values of its upper and lower sides is set.
  • the inclination criteria zone B2 is within a range of inclination criteria Cr2 1 where the inclination angle ⁇ w is smaller by 10% than the measured value to inclination criteria Cr2 2 where the inclination angle ⁇ w is larger by 10% than the measured value.
  • the upper side means an area where the value of the depth 12D/width 12W of the groove 12 is larger than the inclination criteria Cr2.
  • the lower side means an area where the value of the depth 12D/width 12W of the groove 12 is smaller than the inclination criteria Cr2.
  • the water repellency can certainly be obtained in an area where the value of the depth 12D/width 12W of the groove 12 is larger than the inclination criteria zone B2.
  • the water repellency can be obtained because the bridge phenomenon occurs, so that the depth/width of the groove 12 may be set within the range.
  • a hydrophilicity area F B separated from water repellency area F A by the inclination criteria Cr2 when the ratio of the depth 12D to the width 12W of the groove 12 is increased, the hydrophilicity is enhanced (right portion in Fig. 14 ). This is because the groove 12 is deep and thus a specific surface area is increased (increase of surface roughness).
  • the cross section shape of the groove 12 of the surface small structure 10A is not limited to the rectangle ( Fig. 12(a) ) or trapezoid ( Fig. 13(a) ), but it may be the U-shape or V-shape.
  • the depth 12D/width 12W of the groove 12 can be determined using the inclination criteria Cr2 by setting the inclination angle ⁇ w along the inner wall 123.
  • the width 12W of the groove 12 can be set to about one fourth or less of the diameter of the waterdrop in order to form the bridge, and, for example, it can be set to 5 ⁇ m or more to 200 ⁇ m or less. It is preferably 30 ⁇ m or more to 100 ⁇ m or less. A condition that the width 12W is set to 5 ⁇ m or more to 200 ⁇ m or less is prescribed in the above described equation (1).
  • the pitch between the grooves 12 can be set to any value larger than 0.
  • the pitch 12P between the grooves 12 distance in the arrangement direction orthogonal to the extending direction of the groove 12
  • a condition that the pitch 12P between the grooves 12 is set to 5 ⁇ m or more to twice or less the width 12W of the groove 12 is prescribed in the above described equation (2).
  • the plurality of grooves 12 is formed at the fixed intervals in the arrangement direction orthogonal to the extending direction of the groove 12 (direction inclined from the axis x direction), but it is not necessarily be formed at the fixed intervals. Further, the pitches 12P between the grooves 12 are described as constant, but they are not necessarily be constant.
  • the intervals of the grooves 12 in the arrangement direction are any intervals which are not constant, and the pitches 12P between the grooves 12 have any lengths which are not constant, the condition of the above described equation (2) is satisfied.
  • the intervals of the grooves 12 in the arrangement direction may be any intervals which are not constant, and the pitches 12P between the grooves 12 may have any lengths which are not constant.
  • a curved (shape extending linearly while meandering like waves) pattern can be adopted in addition to the straight line pattern.
  • the latticed pattern can be adopted.
  • the waterdrop moves diagonally at a portion where a straight line intersects with a straight line from one straight line to the other straight line. Therefore, in the portion where the straight lines intersect with each other, the width of the groove 12 becomes relatively larger than the depth of the groove 12 (diagonal intersecting with the vertical line and the horizontal line).
  • the widths of the grooves 12 are made to be constant on the whole pattern, so that the intersecting portion where the width of the groove 12 becomes relatively larger than the other portions does not exist. Therefore, it is assumed that the bridge is easily formed on the whole pattern and thus the effect of the water repellency is excellent in the straight line or curved grooves 12 as compared with the latticed grooves 12.
  • Fig. 14 Each indicate data of the sample manufactured at the time of the sensitivity evaluation of the shape factors described with reference to Fig. 7 .
  • Each of the samples has the striped pattern grooves 12 formed by cutting.
  • the samples corresponding to the plots 1 to 3 (P1 to P3) each have the inclination angle ⁇ w of 0°.
  • the sample corresponding to the plot 4 (P4) has the inclination angle ⁇ w of 26°.
  • the width of the groove 12 is 200 ⁇ m, the depth of the groove 12 is 200 ⁇ m, and the depth/width is 1.
  • the pitch between the grooves 12 is 200 ⁇ m.
  • the width of the groove 12 is 100 ⁇ m, the depth of the groove 12 is 10 ⁇ m, and the depth/width is 0.1.
  • the pitch between the grooves 12 is 50 ⁇ m.
  • the width of the groove 12 is 100 ⁇ m, the depth of the groove 12 is 25 ⁇ m, and the depth/width is 0.25.
  • the pitch between the grooves 12 is 200 ⁇ m.
  • the width of the groove 12 is 100 ⁇ m, the depth of the groove 12 is 100 ⁇ m, and the depth/width is 1.
  • the pitch between the grooves 12 is 100 ⁇ m.
  • each of the plots P1 to P4 belongs to the area of the inclination criteria Cr2 or more.
  • the contact angle of the sample corresponding to the plot 1 is 147°.
  • the contact angle of the sample corresponding to the plot 2 is 128°.
  • the contact angle of the sample corresponding to the plot 3 is 116°.
  • the contact angle of the sample corresponding to the plot 4 is 123°. From the above plot data, when the ratio of the depth/width of the groove 12 is determined to be the inclination criteria Cr2 or more, the wettability decreases and the water repellency is expressed.
  • the outdoor heat exchanging apparatus 32 of this embodiment is formed with the plurality of grooves 12 formed at intervals in the arrangement direction orthogonal to the extending direction of the groove 12 on the surface of each of the plurality of plate shape fins 10.
  • the width 12W of each of the plurality of grooves 12 is preferably set to 5 ⁇ m or more to 200 ⁇ m or less.
  • the width 12W of the groove is sufficiently narrower than the size of the waterdrop. Therefore, the phenomenon (bridge phenomenon) occurs, the bridge phenomenon being the phenomenon in which the waterdrop formed on the upper part of the groove 12 does not reach the bottom 124 of the groove and is disposed to extend over the groove 12 from one edge to the other edge.
  • the water repellency of the fin 10 becomes higher because the bridge phenomenon occurs.
  • the ratio of the depth 12D of the groove 12 to the width 12W of the groove 12 is set to 1/tan ⁇ or more when the contact angle formed between the surface of the fin 10 and the waterdrop is ⁇ e.
  • ⁇ 1.1 ⁇ e
  • 1/tan ⁇ is the basic criteria Cr1 1 , which is the lower limit of the basic criteria zone B1.
  • the ratio of the depth 12D of the groove 12 to the width 12W of the groove 12 to the basic criteria Cr1 or more, the basic criteria Cr1 being larger than the basic criteria Cr1 1 which is the lower limit of the basic criteria zone B1, that is by setting the ratio to 1/tan ⁇ e or more, the more sufficient water repellency can be given to the surface of the fin 10.
  • the outdoor unit 30 of this embodiment includes the outdoor heat exchanging apparatus 32, and the propeller fan 33 introducing the air toward the outdoor heat exchanging apparatus 32. It is preferable that the plurality of grooves 12 each extend along the direction inclined from the vertical direction from the upper part to the lower part and extend in the direction descending from the upstream side to the downstream side of the flowing direction of the air introduced with the propeller fan 33.
  • the waterdrop formed on the surface of the fin 10 to which the water repellency is given can be dripped by its own weight along the groove 12 formed from the upper part to the lower part in the direction inclined from the vertical direction. Further, the waterdrop formed on the surface of the fin 10 can be dripped along the groove 12 by the air introduced with the propeller fan 33.
  • the waterdrop formed on the surface of the fin 10 can be certainly dripped by action of its own weight and the air introduced with the propeller fan 33.
  • the second embodiment is a modified example of the first embodiment, and the second embodiment is the same as the first embodiment unless description is specifically given hereinafter, and thus description thereof is omitted.
  • the outdoor heat exchanging apparatus 32 of the first embodiment is the fin and tube type heat exchanging apparatus including the heat transfer tube 40A having a circular cross section.
  • an outdoor heat exchanging apparatus 32' of the second embodiment is a fin and tube type heat exchanging apparatus including a heat transfer tube 40'A having a flat cross section.
  • the outdoor heat exchanging apparatus 32' of this embodiment includes a plurality of heat transfer tubes 40'A and a header 40'B connected to the plurality of heat transfer tubes 40'A.
  • tube holes 10'B provided on a fin 10' of this embodiment each has a shape in which an upstream side in an air flowing direction indicated by an arrow opens.
  • the heat transfer tube 40'A of this embodiment has the flat cross section, and is formed with a plurality of refrigerant passages thereinside.
  • the outdoor heat exchanging apparatus 32' of this embodiment is the flat heat transfer tube 40'A, the fin 10' and the heat transfer tubes 40'A are typically joined by furnace brazing.
  • the outdoor heat exchanging apparatus 32' in an assembled state by the furnace brazing has to be soaked in the coating liquid.
  • the outdoor heat exchanging apparatus 32' in the assembled state is large, and thus large equipment is necessary for soaking it in the coating liquid, which increases workload.
  • the outdoor heat exchanging apparatus 32' of this embodiment makes the fin 10' have the water repellency by forming grooves 12' to be described later on the surface of the fin 10', the above described problem of the soaking in the coating liquid does not occur.
  • arrows in Figs. 17(a) and (b) each indicate a flowing direction of the air introduced with the propeller fan 33.
  • reference numeral 12' is given to the only two grooves, and is not given to the other grooves 12' to omit the description thereof.
  • the surface of the fin 10' is formed with the plurality of grooves 12' each extending from an upper part to a lower part along an axis X extending in a vertical direction.
  • the plurality of grooves 12' is formed at fixed intervals in an arrangement direction orthogonal to the extending direction of the groove 12' (axis x direction).
  • Fig. 17(b) illustrates a modified example of the fin 10'.
  • the surface of the fin 10' in the modified example is formed with the grooves 12' each extending from an upper part to a lower part along a direction inclined from the vertical direction.
  • the plurality of grooves 12' is formed at fixed intervals in an arrangement direction orthogonal to the extending direction of the groove 12' (direction inclined from the axis x direction).
  • an angle formed between an axis Y2 indicating the extending direction of the groove 12' and the axis x along the vertical direction is an angle Z2 in a plane where the surface of the fin 10' is disposed.
  • the reason why the axis Y2 is inclined from the axis X by the angle Z2 in this manner is to utilize power of the air introduced with the propeller fan 33 for making the waterdrops formed on the surface of the fin 10' drip toward the lower part of the fin 10'.
  • the groove 12' extends in a direction descending from an upstream side to a downstream side of the air flowing direction indicated by the arrow. Therefore, the waterdrop formed on the surface of the fin 10' can be dripped along the groove 12' by the air introduced with the propeller fan 33.
  • the angle Z2 described above is set to any value larger than 0° and smaller than 90° depending on various conditions, such as the number of rotations, or air volume of the propeller fan 33. From the same reason as the first embodiment, it is desirable that the angle Z2 is set to about 40° (for example, 20° or more to 60°or less).
  • the outdoor heat exchanging apparatus 32' which is the fin and tube type heat exchanging apparatus including the flat heat transfer tube 40'A, it is possible to give the water repellency to the fin 10' by forming the plurality of grooves 12' on the fin 10'.
  • the fin 10' and the heat transfer tubes 40'A are typically joined by furnace brazing. Therefore, in order to make the fin 10' have the water repellency by soaking it in the coating liquid, the large equipment is necessary for soaking it in the coating liquid, which increases workload.
  • the fin 10' has the water repellency without being soaked in the coating liquid, and thus the problem of the soaking in the coating liquid can be suppressed.
  • the third embodiment is a modified example of the second embodiment, and the third embodiment is the same as the first embodiment and the second embodiment unless description is specifically given hereinafter, and thus description thereof is omitted.
  • the outdoor heat exchanging apparatus 32' which is the fin and tube type heat exchanging apparatus including the flat heat transfer tube 40'A, adopts the tube hole 10'B having the shape in which the upstream side in the air flowing direction opens.
  • an outdoor heat exchanging apparatus 32" which is a fin and tube type heat exchanging apparatus including a flat heat transfer tube 40"A, adopts a tube hole 10"B having a shape in which a downstream side in an air flowing direction opens.
  • the outdoor heat exchanging apparatus 32" of this embodiment includes the plurality of heat transfer tubes 40"A and a header 40"B connected to the plurality of heat transfer tubes 40"A.
  • tube holes 10''B provided on a fin 10" of this embodiment each has the shape in which the downstream side in the air flowing direction indicated by an arrow opens.
  • the heat transfer tube 40"A of this embodiment has the flat cross section, and is formed with a plurality of refrigerant passages thereinside.
  • the outdoor heat exchanging apparatus 32'' of this embodiment has the water repellency by forming grooves 12" to be described later on the surface of the fin 10", it is advantageous that the above described problem of the soaking in the coating liquid does not occur.
  • arrows in Figs. 19(a) and (b) each indicate a flowing direction of the air introduced with the propeller fan 33.
  • reference numeral 12" is given to the only two grooves, and is not given to the other grooves 12" to omit the description thereof.
  • the surface of the fin 10" is formed with the plurality of grooves 12" each extending from an upper part to a lower part along an axis X extending in a vertical direction.
  • the plurality of grooves 12" is formed at fixed intervals in an arrangement direction orthogonal to the extending direction of the groove 12" (axis x direction).
  • Fig. 19(b) illustrates a modified example of the fin 10".
  • the surface of the fin 10 in the modified example is formed with the grooves 12" each extending from an upper part to a lower part along a direction inclined from the vertical direction.
  • the plurality of grooves 12" is formed at fixed intervals in an arrangement direction orthogonal to the extending direction of the groove 12" (direction inclined from the axis x direction).
  • an angle formed between an axis Y3 indicating the extending direction of the groove 12" and the axis x along the vertical direction is an angle Z3 in a plane where the surface of the fin 10" is disposed.
  • the reason why the axis Y3 is inclined from the axis X by the angle Z3 in this manner is to utilize power of the air introduced with the propeller fan 33 for making the waterdrops formed on the surface of the fin 10" drip toward the lower part of the fin 10".
  • the groove 12" extends in a direction descending from an upstream side to a downstream side of the air flowing direction indicated by the arrow. Therefore, the waterdrops formed on the surface of the fin 10" can be dripped along the groove 12" by the air introduced with the propeller fan 33.
  • the angle Z3 described above may be set to any value larger than 0° and smaller than 90° depending on various conditions, such as the number of rotations, or air volume of the propeller fan 33. From the same reason as the first embodiment, it is desirable that the angle Z3 is set to about 40° (for example, 20° or more to 60°or less).
  • the outdoor heat exchanging apparatus 32'' which is the fin and tube type heat exchanging apparatus including the flat heat transfer tube 40''A, it is possible to give the water repellency to the fin 10" by forming the plurality of grooves 12" on the fin 10.
  • the fin 10" and the heat transfer tubes 40"A are typically joined by furnace brazing. Therefore, in order to make the fin 10" have the water repellency by soaking it in the coating liquid, the large equipment is necessary for soaking it in the coating liquid, which increases workload.
  • the fin 10" has the water repellency without being soaked in the coating liquid, and thus the problem of the soaking in the coating liquid can be suppressed.
  • the surface small structure 10A (10'A, 10"A) may be provided on only one surface of the fin 10 (fin 10', fin 10").
  • the shape of the fin 10 (fin 10', fin 10") is not limited to the shapes described in the above embodiments, and may be a corrugated shape.
  • the surface small structure 10A (10'A, 10"A) may be provided on the surface of the heat transfer tube 40A (40'A, 40"A) which may come in contact with water, or ice.

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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)
  • Crystallography & Structural Chemistry (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (9)

  1. Wärmeaustauschvorrichtung (32), umfassend:
    mehrere Rippen (10), die jeweils eine Plattenform aufweisen und sich in einer vertikalen Richtung erstrecken, wobei die mehreren Rippen (10) aufeinanderfolgend in einer horizontalen Richtung in einem Zustand angeordnet sind, in dem Flächen des benachbarten Paares von Rippen (10) parallel zueinander sind; und
    ein Wärmeübertragungsrohr (40A), das derart ausgestaltet ist, dass Kältemittel innerhalb des Wärmeübertragungsrohrs (40A) strömen kann, wobei das Wärmeübertragungsrohr (40A) haftend in ein Rohrloch (10B) eingesetzt wird, das auf jeder von den mehreren Rippen (10) bereitgestellt ist, wobei
    mehrere Rillen (12), die sich jeweils von einem oberen Teil zu einem unteren Teil erstrecken, auf der Oberfläche von jeder von den Rippen (10) in Intervallen in einer Anordnungsrichtung orthogonal zur Erstreckungsrichtung von jeder von den Rillen (12) gebildet sind, und
    dadurch gekennzeichnet, dass eine Breite von jeder von den Rillen (12) 5 µm oder größer bis 200 µm oder kleiner beträgt und ein Abstand zwischen Rändern der benachbarten Rillen (12) in der Anordnungsrichtung 5 µm oder größer bis das Zweifache oder kleiner der Breite von jeder von den Rillen (12) beträgt.
  2. Wärmeaustauschvorrichtung (32) nach Anspruch 1, wobei, wenn ein Kontaktwinkel, der zwischen der Fläche von jeder von den Rippen (10) und einem Wassertropfen gebildet wird, θe beträgt, ein Verhältnis einer Tiefe von jeder von den Rillen (12) zur Breite von jeder von den Rillen (12) 1/tan α oder größer beträgt, wo α = 1,1θe ist.
  3. Wärmeaustauschvorrichtung (32) nach Anspruch 1, wobei ein Verhältnis einer Tiefe von jeder von den Rillen (12) zur Breite von jeder von den Rillen (12) 1/tan θe oder größer beträgt.
  4. Wärmeaustauschvorrichtung (32) nach Anspruch 1, wobei ein Verhältnis einer Tiefe von jeder von den Rillen (32) zur Breite von jeder von den Rillen (32) 1/tan β oder größer beträgt, wobei β = 0,9θe ist.
  5. Wärmeaustauschvorrichtung (32) nach einem der Ansprüche 2 bis 4, wobei eine Querschnittsform von jeder von den Rillen (12) in einer Ebene orthogonal zu der Erstreckungsrichtung rechtwinklig ist.
  6. Wärmeaustauschvorrichtung (32) nach einem der Ansprüche 1 bis 5, wobei jede von den mehreren Rillen (12) sich von dem oberen Teil zu dem unteren Teil entlang einer vertikalen Richtung erstreckt.
  7. Wärmeaustauschvorrichtung (32) nach einem der Ansprüche 1 bis 5, wobei jede von den mehreren Rillen (12) sich von dem oberen Teil zum unteren Teil entlang einer Richtung erstreckt, die von einer vertikalen Richtung geneigt ist.
  8. Klimatisierungsvorrichtung (100), umfassend:
    die Wärmeaustauschvorrichtung (32) nach einem der Ansprüche 1 bis 5; und
    einen Lüfter (33), der ausgestaltet ist, Luft in Richtung der Wärmeaustauschvorrichtung (32) einzuführen.
  9. Klimatisierungsvorrichtung (100) nach Anspruch 8, wobei jede von den mehreren Rillen (12) sich von dem oberen Teil zum unteren Teil in einer Richtung erstreckt, die von einer vertikalen Richtung geneigt ist, und sich in eine Richtung erstreckt, die von einer stromaufwärtigen Seite zu einer stromabwärtigen Seite einer Strömungsrichtung der mit dem Gebläse (33) eingeführten Luft absteigt.
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JP2015193922A (ja) * 2014-03-24 2015-11-05 三菱重工業株式会社 撥液化する表面微細構造並びにその製造方法、熱交換器、および空気調和機の構成要素
FR3046755B1 (fr) * 2016-01-20 2019-07-19 Valeo Systemes Thermiques Systeme de gestion d'entree d'air pour face avant de vehicule automobile
JP6940270B2 (ja) * 2016-11-22 2021-09-22 東京電力ホールディングス株式会社 熱交換器
JP2019163909A (ja) * 2018-03-20 2019-09-26 東京電力ホールディングス株式会社 フィンチューブ式熱交換器
CN109442677B (zh) * 2018-09-18 2022-09-09 平安科技（深圳）有限公司 空调系统的故障控制方法、电子设备
CN216081132U (zh) * 2021-03-03 2022-03-18 郑州海尔空调器有限公司 换热器翅片及换热器

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JPH07174481A (ja) * 1993-12-17 1995-07-14 Matsushita Electric Ind Co Ltd 熱交換装置
US6764745B1 (en) * 1999-02-25 2004-07-20 Seiko Epson Corporation Structural member superior in water repellency and method for manufacturing the same
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