WO2018145253A1 - 鳍片式热交换器 - Google Patents

鳍片式热交换器 Download PDF

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Publication number
WO2018145253A1
WO2018145253A1 PCT/CN2017/073074 CN2017073074W WO2018145253A1 WO 2018145253 A1 WO2018145253 A1 WO 2018145253A1 CN 2017073074 W CN2017073074 W CN 2017073074W WO 2018145253 A1 WO2018145253 A1 WO 2018145253A1
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WIPO (PCT)
Prior art keywords
heat
fin
heat exchanger
heat dissipation
powder
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PCT/CN2017/073074
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English (en)
French (fr)
Inventor
姜文兴
Original Assignee
玖鼎材料股份有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 玖鼎材料股份有限公司 filed Critical 玖鼎材料股份有限公司
Priority to CN201780000429.2A priority Critical patent/CN109041577B/zh
Priority to US16/484,111 priority patent/US20200025464A1/en
Priority to PCT/CN2017/073074 priority patent/WO2018145253A1/zh
Publication of WO2018145253A1 publication Critical patent/WO2018145253A1/zh

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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
    • 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
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • 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
    • F28F13/182—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by applying coatings, e.g. radiation-absorbing, radiation-reflecting; by surface treatment, e.g. polishing especially adapted for evaporator or condenser surfaces
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
    • F28F21/081—Heat exchange elements made from metals or metal alloys
    • F28F21/087—Heat exchange elements made from metals or metal alloys from nickel or nickel alloys
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • 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
    • F28F2245/02—Coatings; Surface treatments hydrophilic
    • 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

Definitions

  • the present disclosure relates to a finned heat exchanger, and more particularly to a finned heat exchanger for use in a refrigeration or air conditioning system.
  • a finned heat exchanger having a large heat exchange area is usually used in order to improve the heat dissipation of the unit.
  • various improvements have been proposed:
  • a blue wave treatment can form an epoxy resin isolation film on the heat dissipation fins, which can theoretically prevent the chloride ions from contacting the aluminum fins to prevent corrosion.
  • the coating operation since the blue wave treatment is a pre-treatment, the coating operation must be completed in a factory that supplies aluminum.
  • the machined surface will produce many cuts and breaks. These cuts and breaks will cause corrosion factors to enter, causing corrosion of the heat sink fins.
  • the oxide layer on the surface of the aluminum fins does not prevent corrosion from continuing, especially in humid environments. Therefore, once corrosion occurs, it will continue.
  • the corrosion resistance of various aluminum alloys is different, and because of the different crystal phases, the corrosion results Also different.
  • 1100 aluminum alloy In the case of the commonly used 1100 aluminum alloy, it is easy to exhibit local deep corrosion in the salt spray test, and in the case of testing with 8006 aluminum alloy, it shows a uniform shallow corrosion. Therefore, in terms of structural damage, 1100 aluminum alloy will be more serious.
  • the separator composed of the epoxy resin has poor thermal conductivity, and although it has considerable protective force, it does not have the ability to resist UV.
  • a fin type heat exchanger applied in a refrigeration or air conditioning system.
  • a heat dissipation layer containing nanomaterials on the fins of the heat exchanger, and by setting appropriate proportions of heat dissipation powders of different particle size sizes and adding a bonding agent, the heat exchange area of the fins and the heat radiation enhancement can be increased.
  • conductivity achieving control of the hydrophobicity and hydrophilicity of the fins, and reducing the surface friction coefficient to improve the efficiency of heat convection, and the heat dissipation layer has excellent UV and corrosion resistance.
  • the present disclosure provides a fin heat exchanger, comprising: a plurality of fins; and a plurality of refrigerant tubes disposed transversely between the plurality of fins, wherein the refrigerant is passed through Introducing the plurality of refrigerant tubes such that air exchanges heat between the plurality of refrigerant tubes and the air passages between the plurality of fins; wherein a surface of the fins includes a heat dissipation layer, and a material of the heat dissipation layer A first heat dissipating powder having a first particle size and a second heat dissipating powder having a second particle size; and wherein the material of the heat dissipating layer comprises nanographite, carbon nanotube, boron nitride, or nanodiamond .
  • the material of the first heat dissipating powder is selected from the group consisting of nano graphite, carbon nanotubes, titanium dioxide, boron nitride, carbon black, carbon fiber, metal powder, silicon carbide, and aluminum oxide.
  • the material of the second heat dissipating powder is selected from the group consisting of nano graphite, carbon nanotubes, boron nitride, carbon black, carbon fiber, metal powder, silicon carbide, aluminum nitride, And a group of nano-diamonds.
  • the first particle size of the first heat dissipating powder ranges from 300 nanometers to 500 nanometers.
  • the second particle size of the second heat dissipating powder ranges from 25 nanometers to 35 nanometers.
  • the first heat dissipating powder accounts for more than 0% to 35% of the heat dissipating layer.
  • the second heat dissipating powder accounts for 5% to 40% of the content of the heat dissipating layer.
  • the material of the heat dissipation layer includes a bonding agent covering the first heat dissipation powder and the second heat dissipation powder to reduce the surface friction coefficient of the heat dissipation layer.
  • a material in which the bonding agent is selected from the group consisting of a polyacrylate type, a polyvinyl alcohol type resin, and a siloxane.
  • the ratio of the first particle size to the second particle size is 10: Between 1 and 30:1 to form the heat dissipation layer having hydrophobicity.
  • the ratio of the first particle size to the second particle size is greater than 500:1. the above, To form the heat dissipation layer having hydrophilicity.
  • the present disclosure forms a heat dissipation layer containing nano materials on a fin of a heat exchanger, wherein the heat dissipation layer contains heat dissipation powders of different particle sizes, thereby increasing the heat exchange area and strengthening of the fins. Thermal radiation and conductivity. Moreover, by setting the proportion of the heat dissipating powders of different particle size sizes, the hydrophobicity and hydrophilicity of the fins can be controlled to control the fins to have excellent humidity and self-cleaning ability. Furthermore, by adding a bonding agent to the heat dissipation layer, it is possible to reduce the surface friction coefficient to improve the efficiency of heat convection, and to provide the heat dissipation layer with excellent UV and corrosion resistance.
  • Figure 1 shows a schematic view of a refrigeration system in accordance with a preferred embodiment of the present disclosure
  • Figure 2 shows a pressure-enthalpy diagram of a refrigeration cycle in an ideal environment
  • Figure 3 shows the pressure-enthalpy diagram of the refrigeration cycle in an ideal environment and in the actual environment
  • FIG. 4 shows a partial schematic view of a fin heat exchanger in accordance with a preferred embodiment of the present disclosure
  • Figure 5 shows a partial enlarged view of the fin of Figure 4.
  • the refrigeration system comprises four main units: a compressor, a condenser, a refrigerant controller and an evaporator.
  • the refrigeration system utilizes the state change characteristics of the cold coal to perform an exothermic and endothermic action with its latent heat to achieve the transfer of thermal energy.
  • the common principle of air conditioning is to pass heat from a low-temperature heat source through a heat pump. It is sent to another higher temperature heat sink, and the natural heat will flow in the opposite direction.
  • the refrigerant is the main cause of cooling the air.
  • the refrigerant is a volatile gas that circulates in the piping of the refrigeration system, like blood in a blood vessel of a human body, which functions as a heat absorption in the evaporator and acts as a heat release in the condenser. effect. Therefore, in reality, the refrigeration system is not a device for manufacturing cold air, but a device for carrying heat, and carries heat from the room to the outside.
  • Commercially available refrigerants are classified into different types depending on pressure and usage requirements, such as R-123, RR-134, R-404A, R-407C, R-410A, R-600, and the like.
  • FIG. 2 there is shown a pressure-enthalpy diagram of a refrigeration cycle in an ideal environment.
  • a cycle consisting of the compressor, the condenser, the refrigerant controller, and the evaporator is as follows: (1) using the compressor to compress a low-pressure low-temperature gaseous refrigerant into a high pressure High temperature gaseous refrigerant, which is also the source of power for the refrigerant to circulate in the refrigeration system. (2) Using the condenser, the high-pressure high-temperature gaseous refrigerant is cooled to a high-pressure medium-temperature liquid refrigerant through a cooling medium, thereby forming an exothermic effect at this end.
  • the refrigerant controller (or the choke) is used to depressurize the high-pressure medium-temperature liquid refrigerant into a low-pressure medium-temperature liquid refrigerant, and the purpose of the pressure reduction is to match the evaporation temperature of the evaporator. Therefore, the lower the temperature requirement, the lower the pressure needs to be reduced. That is to say, high-temperature evaporation occurs in the case of high pressure, and low-temperature evaporation occurs in the case of low pressure.
  • Figure 3 shows the pressure-enthalpy diagram of the refrigeration cycle in an ideal environment and the actual environment, where A graph represents the pressure-enthalpy diagram of the refrigeration cycle in an ideal environment, and B-pattern Represents the pressure-enthalpy diagram of the refrigeration cycle in a real environment.
  • a graph represents the pressure-enthalpy diagram of the refrigeration cycle in an ideal environment
  • B-pattern represents the pressure-enthalpy diagram of the refrigeration cycle in a real environment.
  • the process from point 1 to point 2 is entropy compression, in which no heat energy is lost or obtained.
  • the process from point 2 to point 3 or point 4 to point 1 is condensation or evaporation. This process is a change in isobaric pressure, and heat energy is not lost or obtained due to the influence of the pipeline.
  • the process from point 3 to point 4 is a thermal expansion process, which is a step-down change along the isobaric line, does not exchange heat with the outside, and the refrigerant entering the compressor is saturated gas during this process, and The refrigerant leaving the condenser is a saturated liquid.
  • the pressure-defective B-pattern of the refrigeration cycle in the actual environment that the refrigeration cycle in the actual environment is inevitably subject to heat loss due to the influence of ambient temperature and humidity.
  • the refrigeration cycle benefit can be approximated to the pressure-enthalpy A pattern of the refrigeration cycle in an ideal environment, in the present disclosure, by strengthening the described in the refrigeration system
  • the condenser and the heat exchanger of the evaporator are used to increase the radiation, conduction, and convection equivalent energy of the heat exchanger, and further extend the service life of the refrigeration system.
  • a heat dissipation layer containing a nano material is formed on fins of the condenser and the heat exchanger of the evaporator, and a proportion of the heat dissipation powder of an appropriate different particle size is set and a bonding agent is added.
  • the heat dissipation layer (The specific structure and characteristics of the heat dissipation layer will be detailed later), thereby increasing the heat exchange area of the fins, enhancing heat radiation and conductivity, controlling the hydrophobicity and hydrophilicity of the fins, and reducing surface friction.
  • the coefficient improves the efficiency of heat convection and gives the heat dissipation layer excellent UV and corrosion resistance.
  • the greater the pressure differential between condensation and evaporation the greater the labor required for the compressor. That is to say, as long as the temperature of condensation and evaporation can be lowered, the compression energy consumption can be reduced, the current can be reduced, and the compressor running time can be reduced. Therefore, the present disclosure can also achieve the effects of improving cooling efficiency and reducing the use time to achieve energy saving. It has been confirmed by experiments that in addition to achieving energy-savings of 25 to 40 percent, it can achieve the best environmental protection effect with up to five years of unrelenting performance.
  • FIG. 4 a partial schematic view of a finned heat exchanger 10 in accordance with a preferred embodiment of the present disclosure is shown.
  • the fin heat exchanger 10 is used in a condenser and an evaporator in a refrigeration system.
  • the fin heat exchanger 10 includes a plurality of fins 20 and a plurality of refrigerant tubes 30.
  • the plurality of refrigerant tubes 30 are transversely disposed between the plurality of fins 20, wherein the arrows in FIG. 4 indicate the circulation direction of the refrigerant.
  • the air is introduced into the plurality of refrigerant tubes 30 to exchange heat between the plurality of refrigerant tubes 30 and the air passages between the plurality of fins 20.
  • the fin 20 is a heat sink having a composite structure made by using advanced technology, and has high heat conduction, high heat capacity and heat radiation characteristics.
  • the fin 20 includes a substrate 21 and a heat dissipation layer 22, wherein the heat dissipation layer 22 may be formed on the substrate 21 by spraying, impregnation, coating, or electrochemical, but is not limited thereto.
  • the material of the substrate 21 may be aluminum or copper, but is not limited thereto.
  • the heat dissipation layer 22 includes a base layer 221 , a first heat dissipation powder 222 , and a second heat dissipation powder 223 .
  • the base layer 221 is made of a material that enhances heat transfer efficiency, and the first heat-dissipating powder 222 and the second heat-dissipating powder 223 are used for enhancing heat radiation.
  • the material of the first heat dissipating powder is selected from the group consisting of nano graphite, carbon nanotubes, titanium dioxide, boron nitride, carbon black, carbon fiber, metal powder, silicon carbide, aluminum oxide, aluminum nitride, aluminum oxide, A group of silica and nanodiamonds.
  • the material of the second heat dissipating powder is selected from the group consisting of nano graphite, carbon nanotubes, boron nitride, carbon black, carbon fiber, metal powder, silicon carbide, aluminum nitride, and nano diamonds.
  • the first heat dissipating powder 222 accounts for more than 0% to 35% of the heat dissipating layer 22, and the second heat dissipating powder 223 occupies 5% to 40% of the heat dissipating layer content 22. .
  • the first heat-dissipating powder 222 has a first particle size and the second heat-dissipating powder 223 has a second particle size.
  • the first particle size of the first heat dissipating powder 222 ranges from 300 nanometers to 750 nanometers, preferably between 300 nanometers and 500 nanometers.
  • the first The second particle size of the two heat dissipating powders 223 ranges between 1 nm and 35 nm, preferably between 25 nm and 35 nm.
  • the first heat dissipating powder 222 and the second heat dissipating powder 223 of different particle size sizes are disposed on the heat dissipation layer 22 to form a height difference on the surface, thereby increasing the heat exchange surface area of the fins 20 . To enhance the heat dissipation effect.
  • Thermal load refers to sensible heat (warming) or latent heat (increased humidity) obtained by air in space.
  • the heat gain in the room does not necessarily pass to the air immediately (when the temperature of the surface of the object is lower than the temperature of the air dew point, the moisture will condense on the surface of the object as dew, a process called condensation).
  • condensation a process called condensation
  • the ratio of the first particle size size 222 to the second particle size size 223 Preferably, between 10:1 and 30:1, the first heat dissipating powder 222 and the second heat dissipating powder 223 are constructed on a specific surface to form a nano-sized geometrically complementary structure to form The heat dissipation layer 22 is hydrophobic.
  • the nano-sized concave and convex surface can stabilize the gas atoms adsorbed thereon, thereby forming a stable gas film on the surface of the material.
  • the water droplet will form a solid-gas-liquid tri-state interface on the contact surface with the surface of the object, so that the water droplet and There is an air interface between the surfaces of the objects, so that a rough surface structure can be used to create a hydrophobic phenomenon.
  • the air is sealed in the pores of the surface structure due to the large depth of the surface rough pores, so that the liquid is not completely adsorbed by the wetting action.
  • the liquid is only partially in contact with the solid, and the layer of air formed by the solid surface roughness causes the liquid to float above the air layer without wetting the solid. Also, the more the air stored on the surface, the larger the contact angle of the surface, even approaching 180 degrees.
  • the ratio of the first particle size size 222 to the second particle size size 223 Preferably, more than 500:1 or more is selected to form the heat dissipation layer 22 having hydrophilicity.
  • the heat dissipation layer 22 exhibits a hydrophilic property, a water film can be created on the surface of the heat dissipation layer 22, whereby the moisture can be taken away together with heat (heat of vaporization) while evaporating. Therefore, when an additional sprinkling device is used to cool the outdoor unit, it is possible to achieve a cooling effect with only a small amount of water.
  • the outdoor unit has a good cooling effect by the hydrophilic layer 22 having hydrophilicity, thereby improving the performance of the refrigeration system and effectively reducing the indoor temperature by 2 to 4 °C.
  • about 10 to 20% of power consumption can be reduced to achieve energy saving.
  • the heat dissipation layer 22 further includes a bonding agent (not shown) that covers the first heat dissipation powder 222 and the second heat dissipation powder 223 to reduce the heat dissipation layer 22 .
  • a bonding agent (not shown) that covers the first heat dissipation powder 222 and the second heat dissipation powder 223 to reduce the heat dissipation layer 22 .
  • Surface friction coefficient Since Thermal Convection mainly relies on Eddying motion, and Convective heat transfer refers to the eddy current motion in the boundary layer to achieve heat transfer. That is to say, the fluid flowing in the heat exchange will generate friction with the surrounding fins 20, and the phenomenon of this friction becomes a resistance force. The frictional resistance of the surface of the fin 20 affects the effect of heat conduction.
  • the surface of the fin 20 has low friction by covering the first heat dissipating powder 222 and the second heat dissipating powder 223 with the bonding agent.
  • the coefficient which in turn increases the efficiency of the heat convection.
  • the material of the bonding agent is preferably selected from the group consisting of a polyacrylate type and a polyvinyl alcohol-based resin. So that the surface of the heat dissipation layer 22 can exhibit hydrophilic properties.
  • the material of the bonding agent preferably contains siloxane such that the surface of the heat dissipation layer 22 can exhibit hydrophobic characteristics.
  • the component of the bonding agent preferably further comprises an anti-UV The agent is such that the heat dissipation layer 22 has an excellent anti-UV function.
  • the disclosure can provide excellent heat conduction, heat diffusion, heat exchange and hydrophobic effect, wherein in the embodiment, the first heat dissipation powder and the second heat dissipation powder
  • the body accounts for 10% to 20% of the content of the heat dissipation layer, and the results are as shown in the table:
  • the fin heat exchanger 10 of the present disclosure is applied to an indoor unit of a 2.8 KW to 2.8 KW air conditioning system. Tested in a normal R-410, 2.8 KW fixed-frequency air conditioner for three months, for a heat exchanger in which the heat dissipation layer 22 of the present disclosure is not provided, the air is usually from 8 to 12 degrees from the expansion section to the evaporation section.
  • the compression section through the evaporator is typically 8 to 18 degrees.
  • the temperature entering the condenser through the compressor will be 20 to 25 degrees higher depending on the temperature and humidity of the environment, and the condenser will be about 4 to 8 degrees above room temperature.
  • the air is reduced from the expansion section into the evaporation section to about 4 to 12 degrees, the temperature drop into the compressor is reduced to 0 to 8 degrees, and condensation is introduced from the compressor.
  • the device is 16 to 22 degrees above room temperature and the condenser is about 2 to 4 degrees above room temperature.
  • the dehumidification rate is more than 25% higher.
  • the fin heat exchanger 10 of the present disclosure is applied to an indoor unit of a 2.8 KW propelling 4.1 kW air conditioning system. Replace the 4.1KW indoor unit with the same R-410, 2.8KW fixed-frequency air conditioner. After the heat dissipation layer 22 of the present disclosure is disposed on the fin, the air is reduced from the expansion section into the evaporation section and lowered to 4 to 12 degrees. The temperature drop of the compressor is 4 to 8 degrees, the compressor is fed into the condenser 16 to 20 degrees above room temperature, and the condenser is about 2 to 3 degrees above room temperature. In addition, the dehumidification rate is more than 35 percent higher.
  • the present disclosure forms a heat dissipation layer comprising a nano material on a fin of a heat exchanger, wherein the heat dissipation layer comprises heat dissipation powders of different particle sizes, thereby increasing heat exchange area and heat enhancement of the fins. Radiation and conductivity. Moreover, by setting the proportion of the heat dissipating powders of different particle size sizes, the hydrophobicity and hydrophilicity of the fins can be controlled to control the fins to have excellent humidity and self-cleaning ability. Furthermore, by adding a bonding agent to the heat dissipation layer, it is possible to reduce the surface friction coefficient to improve the efficiency of heat convection, and to provide the heat dissipation layer with excellent UV and corrosion resistance.

Abstract

一种鳍片式热交换器（10），包含多个鳍片（20）；以及多个冷媒管（30），横向穿设于所述多个鳍片（20）间，其中通过将冷媒引入所述多个冷媒管（30），使得空气在所述多个冷媒管（30）及所述多个鳍片（20）间的空气通道进行热交换；其中所述鳍片（20）的表面包含散热层（22），并且所述散热层（22）的材料包含具有第一粒径尺寸的第一散热粉体（222）和具有第二粒径尺寸的第二散热粉体（223）；以及其中所述散热层（22）的材料包含纳米石墨、纳米碳管、氮化硼、或纳米钻石。通过所述散热层（22）的设置可增加鳍片（20）的热交换面积和强化热辐射与传导率、控制鳍片（20）的疏水性和亲水性、降低表面摩擦系数以提高热对流的效率，并使散热层（22）具有优异的抗UV与耐腐蚀功能。

Description

鳍片式热交换器 技术领域
本揭示涉及一种鳍片式热交换器，特别是涉及一种应用在冷冻或空调系统中的鳍片式热交换器。
背景技术
在冷冻或空调系统中，为了提升机组的散热效果通常会采用具有较大热交换面积的鳍片式热交换器。为了增强鳍片式热交换器的热交换效果以及使用寿命，现今已提出多种改善方法：
1.使用铝作为散热鳍片的材料，并且通过蓝波处理在散热鳍片上形成一层蓝色薄膜，接着在蓝色薄膜的外层包覆具有防锈功能的压克力树脂，以有效防止酸雨和盐蚀，最后在最外层包覆亲水膜，使得水滴可均匀包覆在散热鳍片上，更能避免生锈腐蚀，有效延长使用寿命，对抗湿热高盐份的气候。一般而言，铝会与空气中的氧结合形成氧化铝，此氧化层有助于防蚀，但是如果环境中还有其他腐蚀性物质，如氯离子等，就会破坏此氧化层，继续腐蚀。因此通过蓝波处理可在散热鳍片上形成一层环氧树脂的隔离膜，理论上可以杜绝氯离子接触到铝鳍片而达到防止腐蚀的问题。然而，实际上，由于蓝波处理是属于前置处理，必须在提供铝材的工厂内完成涂层作业。当将蓝波处理后的铝材送到热交换器的制造厂加工时，加工表面会产生许多切口与破口,这些切口与破口会让腐蚀因子进入，使得散热鳍片产生腐蚀。并且，铝鳍片表面的氧化层无法阻止腐蚀的继续发生，特别是在潮湿的环境中。因此，一旦腐蚀发生就会继续进行。再者，各种铝合金的防蚀效果不同，并且因为晶相不同的关系，腐蚀结果 也各异。以常用的1100铝合金来说，在盐雾试验时容易呈现局部深层腐蚀情形，而以8006铝合金进行测试时则呈现均匀的浅层腐蚀情形。因此以结构破坏来说，1100铝合金会比较严重。另一方面，由所述环氧树脂构成的隔离膜，其导热性差，虽然具有相当的防护力,但不具备抗UV的能力。
2.通过加大机组的管径、回路或改进内螺纹的角度和螺纹数，增加鳍片式热交换器的散热面积，以提高散热性能。然而，此方法存在了整机体积大、重量重、制造成本高等缺点。
有鉴于此，有必要提出一种鳍片式热交换器，用以解决现有技术中存在的问题。
发明内容
为解决上述现有技术的问题，本揭示的目的在于提供一种应用在冷冻或空调系统中的鳍片式热交换器。通过在热交换器的鳍片上形成包含纳米材料的散热层，并且通过设定适当的不同粒径尺寸的散热粉体的比例以及添加连结剂，进而可增加鳍片的热交换面积和强化热辐射与传导率、达到控制鳍片的疏水性和亲水性、以及降低表面摩擦系数以提高热对流的效率，并且使散热层具有优异的抗UV与耐腐蚀功能。
为达成上述目的，本揭示提供一种鳍片式热交换器，其特征在于，包含：多个鳍片；以及多个冷媒管，横向穿设于所述多个鳍片间，其中通过将冷媒引入所述多个冷媒管，使得空气在所述多个冷媒管及所述多个鳍片间的空气通道进行热交换；其中所述鳍片的表面包含散热层，并且所述散热层的材料包含具有第一粒径尺寸的第一散热粉体和具有第二粒径尺寸的第二散热粉体；以及其中所述散热层的材料包含纳米石墨、纳米碳管、氮化硼、或纳米钻石。
于本揭示其中之一优选实施例当中，所述第一散热粉体的材料选自于由纳米石墨、纳米碳管、二氧化钛、氮化硼、碳黑、碳纤维、金属粉末、碳化硅、氧化铝、氮化铝、氧化铝、二氧化硅以及纳米钻石所组成的群组。
于本揭示其中之一优选实施例当中，所述第二散热粉体的材料选自于由纳米石墨、纳米碳管、氮化硼、碳黑、碳纤维、金属粉末、碳化硅、氮化铝、以及纳米钻石所组成的群组。
于本揭示其中之一优选实施例当中，所述第一散热粉体的所述第一粒径尺寸的范围在300纳米至500纳米之间。
于本揭示其中之一优选实施例当中，所述第二散热粉体的所述第二粒径尺寸的范围在25纳米至35纳米之间。
于本揭示其中之一优选实施例当中，所述第一散热粉体占所述散热层含量为大于0％至35％。
于本揭示其中之一优选实施例当中，所述第二散热粉体占所述散热层含量的5％至40％。
于本揭示其中之一优选实施例当中，所述散热层的材料含包含连结剂，包覆住所述第一散热粉体和所述第二散热粉体，以降低所述散热层的表面摩擦系数，以及其中所述连结剂的材料选自于由聚丙烯酸盐系、聚乙烯醇系树脂以及硅氧烷所组成的群组。
于本揭示其中之一优选实施例当中，当所述鳍片式热交换器设置在冷冻系统的室内机时，所述第一粒径尺寸与所述第二粒径尺寸的比例介于10:1至30:1之间，以形成具有疏水性的所述散热层。
于本揭示其中之一优选实施例当中，当所述鳍片式热交换器设置在冷冻系统的室外机时，所述第一粒径尺寸与所述第二粒径尺寸的比例大于500:1以上， 以形成具有亲水性的所述散热层。
相较于先前技术，本揭示通过在热交换器的鳍片上形成包含纳米材料的散热层，其中所述散热层包含不同粒径尺寸的散热粉体，进而可增加鳍片的热交换面积和强化热辐射与传导率。并且通过设定适当的不同粒径尺寸的散热粉体的比例，进而可达到控制鳍片的疏水性和亲水性，以控制所述鳍片具有优异的含湿度与自洁能力。再者，通过在散热层添加连结剂，可达到降低表面摩擦系数以提高热对流的效率，并且使散热层具有优异的抗UV与耐腐蚀功能。
附图说明
图1显示一种根据本揭示优选实施例的冷冻系统的示意图；
图2显示一种在理想环境中的冷冻循环的压力-焓图；
图3显示分别在理想环境中与实际环境中的冷冻循环的压力-焓图；
图4显示一种根据本揭示优选实施例的鳍片式热交换器的局部示意图；以及
图5显示图4的鳍片的局部放大图。
具体实施方式
为了让本揭示的上述及其他目的、特征、优点能更明显易懂，下文将特举本揭示优选实施例，并配合所附图式，作详细说明如下。
请参照图1，其显示一种根据本揭示优选实施例的冷冻系统。所述冷冻系统包含压缩机、冷凝器、冷媒控制器及蒸发器四个主要机组。所述冷冻系统根据冷冻循环，利用冷煤的态变特性，以其潜热进行放热、吸热动作以达到热能的传递。详言之，常见的空气调节原理为，通过热泵把热力由一个低温热源传 送到另一个较高温的散热装置，自然地热会以相反方向流动。此循环使用了普通气体定律(universal gas law)PV＝nRT，其中P代表气压，V代表体积，R代表普通气体常数，T代表温度，n则是气体的莫尔数量。
在所述冷冻系统中，冷媒是让空气降温的主因。冷媒是一种容易挥发的气体，在冷冻系统管路中循环，就像是人体血管中的血液一样，在所述蒸发器中起到吸热作用，并在所述冷凝器中起到放热作用。因此，实际上冷冻系统不是制造冷气的装置，而是搬运热量的装置，将热量从室内搬运到室外。市售的冷媒依压力及使用需求而分成不同的种類，例如R-123、RR-134、R-404A、R-407C、R-410A、R-600等等。
请参照图2，其显示一种在理想环境中的冷冻循环的压力-焓图。在所述冷冻系统中，由所述压缩机、所述冷凝器、所述冷媒控制器及所述蒸发器构成的循环如下：(1)使用所述压缩机将低压低温的气态冷媒压缩成高压高温的气态冷媒，这也是冷媒在冷冻系统中循环的动力来源。(2)使用所述冷凝器将高压高温的气态冷媒经冷却介质冷却成高压中温的液态冷媒，因而在此端形成放热作用。(3)利用所述冷媒控制器(或称阻流器)将高压中温的液态冷媒降压成低压中温的液态冷媒，降压的目的是为了配合所述蒸发器的蒸发温度。因此，当温度要求越低表示需要将压力降至越低。也就是说，在高压的情况下会进行高温蒸发，以及在低压的情况下会进行低温蒸发。(4)利用所述蒸发器将低压中温的液态冷媒蒸发吸热成为低压低温的气态冷媒。因此，所述蒸发器适合装设在室内冷房或冷冻库内。通过冷媒蒸发时向内吸收热量，造成室内冷房或冷冻库温度下降，降而起到降温和冷冻的功效。
请参照图2和图3，图3显示分别在理想环境中与实际环境中的冷冻循环的压力-焓图，其中A图形表示在理想环境中的冷冻循环的压力-焓图，以及B图形 表示在实际环境中的冷冻循环的压力-焓图。先从在理想环境中的冷冻循环的压力-焓图的A图形来看，从点1到点2的过程为等熵(entropy)压缩，在此过程不会有热能的损失或获得。从点2到点3或点4到点1的过程为冷凝或蒸发，此过程为等压的变化，不会因为管路影响而造成热能的损失或获得。从点3到点4的过程为断热膨胀过程，此过程为沿着等焓线的降压变化，不会与外界进行热交换，并且此过程中进入所述压缩机的冷媒为饱和气体，以及离开所述冷凝器的冷媒为饱和液体。然而，从在实际环境中的冷冻循环的压力-焓图的B图形可以看到，实际环境中的冷冻循环会受周围环境温、湿度的影响必然会有热损失的情况发生。
因此，为了提高热交换率以及减少热损失，使得冷冻循环效益能趋近于理想环境中的冷冻循环的压力-焓图的A图形，在本揭示中，通过强化所述冷冻系统中的所述冷凝器及所述蒸发器的热交换器，以提高热交换器的辐射、传导、对流等效能，并且进一步延长冷冻系统的使用寿命。具体来说，通过在所述冷凝器及所述蒸发器的热交换器的鳍片上形成包含纳米材料的散热层，并且通过设定适当的不同粒径尺寸的散热粉体的比例以及添加连结剂(所述散热层的具体结构跟特征将详述于后)，进而可增加鳍片的热交换面积和强化热辐射与传导率、达到控制鳍片的疏水性和亲水性、以及降低表面摩擦系数以提高热对流的效率，并且使散热层具有优异的抗UV与耐腐蚀功能。进一步来说，当冷凝与蒸发的压差越大，所述压缩机所需的作工能量就越大。也就是说，只要能降低冷凝与蒸发的温度，即可以降低压缩能耗，达到降低电流及减少所述压缩机运转时间。因此，本揭示还可达到提高冷却效率和减少使用时间进而达到节能省电的效果。经实验证实，除了可达到节能百分之二十五至四十外，还可达到长达五年效能不减的最佳环保功效。
请参照图4，其显示一种根据本揭示优选实施例的鳍片式热交换器10的局部示意图。优选地，所述鳍片式热交换器10是应用在冷冻系统中的冷凝器及蒸发器内。所述鳍片式热交换器10包含多个鳍片20以及多个冷媒管30。所述多个冷媒管30横向穿设于所述多个鳍片20间，其中图4中的箭头表示冷媒的循环方向。通过将冷媒引入所述多个冷媒管30内，使得空气在所述多个冷媒管30及所述多个鳍片20间的空气通道进行热交换。
请参照图5，其显示图4的鳍片20的局部放大图。所述鳍片20是利用先进技术做出的具有复合结构的散热片，兼具有高热传导、高热容与热辐射特性。具体来说，所述鳍片20包含基板21和散热层22，其中所述散热层22可通过喷涂、含浸、淋膜或电化学的方式形成在所述基板21上，但不局限于此。优选地，所述基板21的材料可选用铝或铜，但不局限于此。所述散热层22包含一基底层221、第一散热粉体222、和第二散热粉体223。所述基底层221是采用能增进热传导效能的材料，以及所述第一散热粉体222和第二散热粉体223是用于增进热辐射的效能。优选地，所述第一散热粉体的材料选自于由纳米石墨、纳米碳管、二氧化钛、氮化硼、碳黑、碳纤维、金属粉末、碳化硅、氧化铝、氮化铝、氧化铝、二氧化硅以及纳米钻石所组成的群组。优选地，所述第二散热粉体的材料选自于由纳米石墨、纳米碳管、氮化硼、碳黑、碳纤维、金属粉末、碳化硅、氮化铝、以及纳米钻石所组成的群组。并且，优选的，所述第一散热粉体222占所述散热层22含量为大于0％至35％，以及所述第二散热粉体223占所述散热层含量22的5％至40％。
如图5所示，所述第一散热粉体222具有第一粒径尺寸以及所述第二散热粉体223具有第二粒径尺寸。具体来说，所述第一散热粉体222的所述第一粒径尺寸的范围在300纳米至750纳米之间，优选地在300纳米至500纳米之间。所述第 二散热粉体223的所述第二粒径尺寸的范围在1纳米至35纳米之间，优选地在25纳米至35纳米之间。通过在所述散热层22上设置不同粒径尺寸的所述第一散热粉体222和所述第二散热粉体223，以在表面形成高低差，进而增加所述鳍片20的热交换表面积，以增强散热效果。
由于当空间中的湿度越低时，冷冻系统的热负荷(cooling load)越低。热负荷指的是空间内空气所获得的显热(升温)或潜热(湿度增加)。室内的热获得不一定立即传予空气(当物体表面的温度低于空气露点温度，水分会在物体表面凝结为露，此过程叫结露)。也就是说，降低露点温度(即湿度)即可提高热交换的效益。因此，当本揭示的所述鳍片式热交换器10设置在冷冻系统的室内机(例如所述蒸发器)时，所述第一粒径尺寸222与所述第二粒径尺寸223的比例优选地选用介于10:1至30:1之间，使得所述第一散热粉体222和所述第二散热粉体223在特定的表面上建造纳米尺寸几何形狀互补的结构，以形成具有疏水性的所述散热层22。由于纳米尺寸的凹凸表面可使吸附在其上的气体原子稳定存在，进而在材料表面上形成一层稳定的气体薄膜。因此，对于半径约等于700μm的水滴来说，若物体表面具有次微米或纳米尺度的粗糙表面构造，则水滴会在与物体表面的接触面形成固-气-液三态的介面，使水滴和物体表面之间存在空气介面，故可藉此粗糙表面构造产生疏水现象。进一步详细说明，对于展现在異质复合的固体表面的疏水特性，由于表面粗糙孔隙的深度较大，空气被封住在表面结构的孔隙内，因此在润湿作用下，液体并未完全的吸附或附着于固体表面，而是悬浮坐立于固体表面及其粗糙度形成的空气层之上。也就是说，液体只有部分地与固体接触，并且因固体表面粗糙度而形成的空气层，会使得液体悬浮于所述空气层上方而不会使固体湿润。并且，当表面上储存的空气越多时，表面的接触角越大，甚至趋近于180度。
反之，当本揭示的所述鳍片式热交换器10设置在冷冻系统的室外机(例如所述冷凝器)时，所述第一粒径尺寸222与所述第二粒径尺寸223的比例优选地选用大于500:1以上，以形成具有亲水性的所述散热层22。当所述散热层22展现亲水特性时，可在所述散热层22的表面创造出水薄膜，藉此可让水气在蒸发的时候一起将热(气化热)带走。因此，当使用额外的洒水设备来使所述室外机冷却降温时，可起到只需使用少许水的情况下，即达到冷却效果。经实验证实，通过具有亲水性的所述散热层22使得所述室外机具有良好的冷却效果，进而能提升冷冻系统的效能，并有效地使室内温度下降2至4℃。经试算，大约可减少10至20％的耗电，达到节能效果。
在本揭示中，所述散热层22还包含连结剂(未出示于图中)，其包覆住所述第一散热粉体222和所述第二散热粉体223，以降低所述散热层22的表面摩擦系数。由于热对流(Thermal Convection)主要是透过涡流运动(Eddying motion)，以及对流热传递(Convective heat transfer)指的是在边界层(boundary layer)以涡流运动进行扰动，达到传热的目的。也就是说，在热交换中流动的流体会与周围所述鳍片20产生摩擦，此摩擦的现象变成一种阻抗力。所述鳍片20表面的摩擦阻抗会影响到热传导的效果。因此，在本揭示的所述鳍片20中，通过将所述连结剂包覆住所述第一散热粉体222和所述第二散热粉体223，使得所述鳍片20的表面具有低摩擦系数，进而可增加热对流效率。应当注意的是，当所述鳍片式热交换器10设置在冷冻系统的室外机，所述连结剂的材料优选地选自于由聚丙烯酸盐系和聚乙烯醇系树脂所组成的群组，以使得所述散热层22的表面能展现出亲水特性。当所述鳍片式热交换器10设置在冷冻系统的室内机时，所述连结剂的材料优选地包含硅氧烷，以使得所述散热层22的表面能展现出疏水特性。另一方面，所述连结剂的成分优选地还包含抗UV 剂，以使所述散热层22具有优异的抗UV功能。
另一方面，以下列举多个实验结果，以证实通过将本揭示的所述热交换器10应用在冷冻系统中的冷凝器和/或蒸发器内可起到优异的热交换效率：
(一)在冷冻或空调系统的室内机内，相较于使用具有本揭示的散热层的鳍片与使用现有技术中的通过蓝波处理的鳍片或使用未通过表面处理的纯铝或纯铜材料作为热交换器的鳍片，本揭示可起到优异的热传导、热扩散、热交换以及疏水效果，其中在本实施例中，所述第一散热粉体和所述第二散热粉体占所述散热层含量的10％至20％，结果如表格所示：
Figure PCTCN2017073074-appb-000001
(二)将本揭示的鳍片式热交换器10应用在2.8KW对2.8KW空调系统的室内机内。以一般R-410、2.8KW的定频空调做测试三个月，对于未设置本揭示的所述散热层22的热交换器表现为：空气从膨胀段进入蒸发段通常为8至12度，通过蒸发器进入压缩段通常为8至18度。通过压缩机进冷凝器的温度会随着环境温湿度的不同会高出20至25度，出冷凝器约高于室温4至8度。反观，通过在鳍片上设置本揭示的所述散热层22后，空气从膨胀段进入蒸发段降低到约4至12度，进入压缩机的温度降降低到0至8度，从压缩机进冷凝器高出室温16至22度，出冷凝器约高于室温2至4度。此外，除湿率则高出百分之二十五以上。
(三)将本揭示的鳍片式热交换器10应用在2.8KW推动4.1KW空调系统的室内机内。以同样的R-410、2.8KW定频空调更换4.1KW的室内机，通过在鳍片上设置本揭示的所述散热层22后，空气自膨胀段进入蒸发段降降低到4至12度，进入压缩机的温度降为4至8度，压缩机进冷凝器高出室温16至20度，出冷凝器约高于室温2至3度。此外，除湿率则高出百分之三十五以上。
综上所述，本揭示通过在热交换器的鳍片上形成包含纳米材料的散热层，其中所述散热层包含不同粒径尺寸的散热粉体，进而可增加鳍片的热交换面积和强化热辐射与传导率。并且通过设定适当的不同粒径尺寸的散热粉体的比例，进而可达到控制鳍片的疏水性和亲水性，以控制所述鳍片具有优异的含湿度与自洁能力。再者，通过在散热层添加连结剂，可达到降低表面摩擦系数以提高热对流的效率，并且使散热层具有优异的抗UV与耐腐蚀功能。
以上仅是本揭示的优选实施方式，应当指出，对于本领域具有通常知识者，在不脱离本揭示原理的前提下，还可以做出若干改进和润饰，这些改进和润饰也应视为本揭示的保护范围。

Claims (10)

  1. 一种鳍片式热交换器，其特征在于，包含：多个鳍片；以及多个冷媒管，横向穿设于所述多个鳍片间，其中通过将冷媒引入所述多个冷媒管，使得空气在所述多个冷媒管及所述多个鳍片间的空气通道进行热交换；
    其中所述鳍片的表面包含散热层，并且所述散热层的材料包含具有第一粒径尺寸的第一散热粉体和具有第二粒径尺寸的第二散热粉体；以及
    其中所述散热层的材料包含纳米石墨、纳米碳管、氮化硼、或纳米钻石。
  2. 如权利要求1所述的鳍片式热交换器，其特征在于，所述第一散热粉体的材料选自于由纳米石墨、纳米碳管、二氧化钛、氮化硼、碳黑、碳纤维、金属粉末、碳化硅、氧化铝、氮化铝、氧化铝、二氧化硅以及纳米钻石所组成的群组。
  3. 如权利要求1所述的鳍片式热交换器，其特征在于，所述第二散热粉体的材料选自于由纳米石墨、纳米碳管、氮化硼、碳黑、碳纤维、金属粉末、碳化硅、氮化铝、以及纳米钻石所组成的群组。
  4. 如权利要求1所述的鳍片式热交换器，其特征在于，所述第一散热粉体的所述第一粒径尺寸的范围在300纳米至500纳米之间。
  5. 如权利要求1所述的鳍片式热交换器，其特征在于，所述第二散热粉体的所述第二粒径尺寸的范围在25纳米至35纳米之间。
  6. 如权利要求1所述的鳍片式热交换器，其特征在于，所述第一散热粉体占所述散热层含量为大于0％至35％。
  7. 如权利要求1所述的鳍片式热交换器，其特征在于，所述第二散热粉体占所述散热层含量的5％至40％。
  8. 如权利要求1所述的鳍片式热交换器，其特征在于，所述散热层的材料含包含连结剂，包覆住所述第一散热粉体和所述第二散热粉体，以降低所述散 热层的表面摩擦系数，以及其中所述连结剂的材料选自于由聚丙烯酸盐系、聚乙烯醇系树脂以及硅氧烷所组成的群组。
  9. 如权利要求1所述的鳍片式热交换器，其特征在于，当所述鳍片式热交换器设置在冷冻系统的室内机时，所述第一粒径尺寸与所述第二粒径尺寸的比例介于10:1至30:1之间，以形成具有疏水性的所述散热层。
  10. 如权利要求1所述的鳍片式热交换器，其特征在于，当所述鳍片式热交换器设置在冷冻系统的室外机时，所述第一粒径尺寸与所述第二粒径尺寸的比例大于500:1以上，以形成具有亲水性的所述散热层。
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