EP4345407A1 - Wärmetauscher - Google Patents

Wärmetauscher Download PDF

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Publication number
EP4345407A1
EP4345407A1 EP23199837.8A EP23199837A EP4345407A1 EP 4345407 A1 EP4345407 A1 EP 4345407A1 EP 23199837 A EP23199837 A EP 23199837A EP 4345407 A1 EP4345407 A1 EP 4345407A1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
heat exchanger
fin
refrigerant tube
region
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP23199837.8A
Other languages
English (en)
French (fr)
Inventor
Minjae PARK
Minsu Park
Hyungbum KIM
Juhyok Kim
Sungsub Lee
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
LG Electronics Inc
Original Assignee
LG Electronics Inc
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 LG Electronics Inc filed Critical LG Electronics Inc
Publication of EP4345407A1 publication Critical patent/EP4345407A1/de
Pending legal-status Critical Current

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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
    • 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
    • F28F1/126—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 consisting of zig-zag shaped fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
    • F28F19/004—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers by using protective electric currents, voltages, cathodes, anodes, electric short-circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • 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
    • 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
    • F28F21/084—Heat exchange elements made from metals or metal alloys from aluminium or aluminium alloys
    • 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
    • F28F21/085—Heat exchange elements made from metals or metal alloys from copper or copper 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
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2260/00—Heat exchangers or heat exchange elements having special size, e.g. microstructures
    • F28F2260/02—Heat exchangers or heat exchange elements having special size, e.g. microstructures having microchannels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/04—Fastening; Joining by brazing

Definitions

  • the present disclosure relates to a heat exchanger with strong corrosion resistance.
  • a heat exchanger may be used as a condenser or an evaporator in a refrigerating cycle device including a compressor, a condenser, an expansion mechanism, and an evaporator.
  • the heat exchanger is installed in a vehicle, a refrigerator or the like to exchange heat between refrigerant and air.
  • the heat exchanger may be classified into a fin tube type heat exchanger, a micro channel type heat exchanger, and the like, according to the structure.
  • the aluminum material for the heat exchanger mainly use pure aluminum (A1XXX) that is advantageous in extrusion, has high thermal conductivity, and is inexpensive, and aluminum-manganese (A3XXX) that is slightly lower in extrudability than the pure aluminum but has relatively high strength and corrosion resistance.
  • Table 1 shows the compositions of A1070 and A3003, which are mainly used as a conventional aluminum material for a heat exchanger.
  • A1070 is pure aluminum material, while A3003 is aluminum- manganese material.
  • Table 1 Material name Cu Si Fe Zn Mg Mn Ti Al A1070 0.03 0.20 0.25 0.04 0.03 0.03 0.03 Rem.
  • A3003 0.158 0.084 0.421 0.034 0.001 1.021 0.014 Rem.
  • the A1070 material is low in material cost and extrusion cost, so that it is used as a tube and fin material of a condenser for a home appliance, such as an air conditioner and a refrigerator, which does not require high strength but is important in economic efficiency.
  • the A3003 material is superior to the A1070 in strength and corrosion resistance but is slightly high in extrusion cost, so that it is used as an extruded tube and fin material for a heat exchanger such as an intercooler and a radiator for a vehicle.
  • aluminum is a metal that is easily activated but has high corrosion resistance by forming an oxide film on a surface in the atmosphere.
  • pitting corrosion occurs in which corrosion occurs only in a local region where the oxide film is damaged when aluminum is corroded.
  • corrosion is intensively propagated to a portion by electrochemical action with various impurities contained in aluminum alloy. Due to the corrosion mechanism of aluminum, the aluminum heat exchanger may be locally penetrated, thus causing the leakage of refrigerant or high-temperature fluid therefrom.
  • Patent Document 1 has attempted to adjust the contents of copper, silicon, iron, and zirconium and use properties of zirconium elements that control a corrosion product and induce uniform corrosion.
  • Patent Document 1 is problematic in that zirconium is a very expensive rare metal, so that manufacturing cost is expensive, and the material loses corresponding characteristics during the recrystallization of elements in the material when fins and tubes are subjected to brazing welding at high temperature, so that it is difficult to use this technology in mass production.
  • FIG. 7 in order to prevent corrosion, there has been used a method of applying zinc particles 203 onto a tube 204 and brazing it with a fin 201.
  • the fin 201 is usually coated with cladding 202.
  • the fin 201 and the tube 204 may be separated from each other in the section where the zinc concentration is excessive, and corrosion may start in the section where the zinc concentration is low.
  • Patent Document 1 KR Patent Publication No. 20150035416
  • An objective of the present disclosure provides a heat exchanger that uses a sacrificial sheet having a potential difference, thus preventing the corrosion of a fin and a tube and preventing the fin from being separated from the tube.
  • Another objective of the present disclosure provides a heat exchanger that uses a sacrificial sheet on an outer surface of a tube, thus enabling easy manufacture and reducing manufacturing cost.
  • a further objective of the present disclosure provides a heat exchanger, in which a sacrificial sheet can be easily aligned and coupled to an outer surface of a tube.
  • a heat exchanger according to the present disclosure is characterized in that a corrosion potential of a sacrificial sheet between a fin and a refrigerant tube is lower than that of the refrigerant tube.
  • a heat exchanger according to the present disclosure is characterized in that the sacrificial sheet between the fin and the refrigerant tube is zinc.
  • the present disclosure provides a heat exchanger including a plurality of refrigerant tubes through which refrigerant flows, a fin disposed between adjacent refrigerant tubes to conduct heat, and a sacrificial sheet configured such that a first surface thereof contacts the refrigerant tube and a second surface thereof contacts the fin.
  • a corrosion potential of the sacrificial sheet is lower than a corrosion potential of the refrigerant tube.
  • the corrosion potential of the sacrificial sheet may be lower than a corrosion potential of the fin.
  • the corrosion potential of the fin may be lower than the corrosion potential of the refrigerant tube.
  • the sacrificial sheet may include zinc or alloy of zinc and aluminum.
  • the fin may include at least one of aluminum, copper and aluminum alloy.
  • the refrigerant tube may include at least one of aluminum, copper and aluminum alloy.
  • the sacrificial sheet may be positioned on each of upper and lower surfaces of the refrigerant tube.
  • the sacrificial sheet may include a first region, and a second region with a step between the first region and the second region.
  • the second region may be formed by drawing a portion of the first region.
  • the second region may protrude toward the refrigerant tube contacting the sacrificial sheet.
  • the second region may be formed by recessing a portion of the first region.
  • the refrigerant tube may include a matching portion corresponding to the second region.
  • a width of the first region may be greater than a width of the second region.
  • a thickness of the sacrificial sheet may be thicker than a thickness of the fin.
  • a thickness of the refrigerant tube may be thicker than a thickness of the sacrificial sheet.
  • Each of the refrigerant tubes may include a plurality of micro channels therein.
  • the heat exchanger may further include a header coupled to first ends of the plurality of refrigerant tubes to supply the refrigerant into the plurality of refrigerant tubes.
  • the material of the sacrificial sheet may be different from that of the fin and the refrigerant tube.
  • the spatially relative terms “below”, “beneath”, “lower”, “above”, “upper”, etc. may be used to easily describe a relationship between one component and another component as shown in the drawings.
  • the spatially relative terms should be understood as encompassing different directions of components in use or operation in addition to directions shown in the drawings. For example, when reversing components shown in the drawings, components described as being “below” or “beneath” other components may be placed “above” the other components. Thus, the exemplary term “below” may include directions of both below and above.
  • the components may also be oriented in other directions, and thus the spatially relative terms may be interpreted according to an orientation.
  • FIG. 1 is a diagram illustrating a refrigerating cycle device according to an embodiment of the present disclosure
  • FIG. 2 is a perspective view illustrating the outside of an outdoor unit shown in FIG. 1 .
  • the refrigerating cycle device may include a compressor 10 that compresses a refrigerant, an outdoor heat exchanger 11 that exchanges heat between the refrigerant and outdoor air, an expansion mechanism 12 that expands the refrigerant, and an indoor heat exchanger 13 that exchanges heat between the refrigerant and indoor air.
  • the refrigerant compressed by the compressor 10 may be condensed by exchanging heat with outdoor air while passing through the outdoor heat exchanger 11.
  • the outdoor heat exchanger 11 may be used as a condenser.
  • the refrigerant condensed in the outdoor heat exchanger 11 may flow to the expansion mechanism 12 and then be expanded.
  • the refrigerant expanded by the expansion mechanism 12 may be evaporated by exchanging heat with indoor air while passing through the indoor heat exchanger 13.
  • the indoor heat exchanger 12 may be used as an evaporator that evaporates the refrigerant.
  • the refrigerant evaporated by the indoor heat exchanger 12 may be recovered to the compressor 10.
  • the heat exchanger may include the indoor heat exchanger 12 and the outdoor heat exchanger 11.
  • the refrigerant is operated in a refrigerating cycle while circulating through the compressor 10, the outdoor heat exchanger 11, the expansion mechanism 12, and the indoor heat exchanger 13.
  • An intake path of the compressor 10 that guides the refrigerant passing through the indoor heat exchanger 13 to the compressor 10 may be connected to the compressor 10.
  • An accumulator 14 in which a liquid refrigerant is accumulated may be installed in the intake path of the compressor 10.
  • the indoor heat exchanger 13 may form a refrigerant path through which the refrigerant passes.
  • the refrigerating cycle device may be a separable type air conditioner in which an indoor unit I and an outdoor unit O are separated.
  • the compressor 10 and the outdoor heat exchanger 11 may be installed in the outdoor unit I.
  • the refrigerating cycle device may be a refrigerator, and the indoor heat exchanger 13 may be disposed to exchange heat with air inside a food storage, and the outdoor heat exchanger 11 may exchange heat with air outside the food storage.
  • the indoor unit I and the outdoor unit O may be disposed together in a main body.
  • the expansion mechanism 12 may be installed in either of the indoor unit I or the outdoor unit O.
  • the indoor heat exchanger 13 may be installed in the indoor unit I.
  • An outdoor fan 15 may be installed in the outdoor unit O to blow outdoor air to the outdoor heat exchanger 11.
  • the compressor 10 may be installed in a machine room of the outdoor unit O.
  • An indoor fan 16 may be installed in the indoor unit I to blow indoor air to the indoor heat exchanger 13.
  • a liquid phase and a gas phase of the refrigerant are mixed.
  • the gas phase and the liquid phase may be unevenly introduced.
  • FIG. 3 is a perspective view illustrating a heat exchanger according to an embodiment of the present disclosure
  • FIG. 4 is a longitudinal sectional view of the heat exchanger shown in FIG. 3
  • FIG. 5 is a sectional view taken along line 5-5' of FIG. 4 .
  • the heat exchanger 100 is a device that exchanges heat between the refrigerant of a refrigerating cycle and outside air.
  • the heat exchanger 100 evenly distributes the refrigerant therein, and has a large heat transfer area.
  • the heat exchanger 100 may be arranged with a plurality of rows, and the flow direction of the refrigerant in one row may be alternately changed.
  • the heat exchanger 100 includes a plurality of refrigerant tubes 50 through which the refrigerant flows, a fin 60 disposed between adjacent refrigerant tubes 50 to conduct heat, and a sacrificial sheet 90 configured such that one surface thereof contacts the refrigerant tube 50 and the other surface contacts the fin 60.
  • the heat exchanger 100 further includes a header 70 to which one end of each of the plurality of refrigerant tubes 50 is coupled to supply the refrigerant into the refrigerant tubes 50, an outer pipe 110 provided inside the header 70, and an inner pipe 120 provided inside the outer pipe 110.
  • the refrigerant tube 50 has a fine inner diameter so that the refrigerant flows therein to maximize a contact area with the air.
  • the plurality of refrigerant tubes 50 are connected to the header 70.
  • the refrigerant tubes 50 extend in a direction transverse to the header 70.
  • the refrigerant tubes 50 may be arranged long in a horizontal (front-rear) direction (LeRi), and the plurality of refrigerant tubes 50 may be stacked in a vertical (longitudinal) direction (UD). While air passes through a space between the plurality of refrigerant tubes 50 stacked in the vertical direction, the air exchanges heat with the refrigerant in the refrigerant tubes 50.
  • the refrigerant tube 50 may include a plurality of micro channels 50a therein.
  • the plurality of micro channels 50a defines a space through which the refrigerant passes.
  • the plurality of micro channels 50a may extend in parallel with the refrigerant tube 50.
  • the sectional shape of the refrigerant tube 50 may be a rectangular shape whose horizontal length is greater than a vertical length, and the sectional shape of the micro channel 50a may be a rectangular shape.
  • the micro channels 50a are usually stacked in one row in a direction (front-rear direction) FR crossing the longitudinal direction of the refrigerant tube 50.
  • the fin 60 transfers heat from the refrigerant tube 50.
  • the fin 60 increases the contact area with air to improve heat dissipation performance.
  • the fin 60 is disposed between adjacent refrigerant tubes 50.
  • the fin 60 may have various shapes, but may be formed by bending a plate that has the same width as the refrigerant tube 50.
  • the fin 60 may be coated by cladding 601.
  • the fin 60 may connect two refrigerant tubes 50 stacked in the vertical direction to conduct heat.
  • the fin 60 may directly contact the refrigerant tube 50, and may be connected to the refrigerant tube 50 by the sacrificial sheet 90.
  • a contact portion between the fin 60 and the sacrificial sheet 90 is formed in a U- or V-shape.
  • the fins 60 and the refrigerant tubes 50 are alternatively stacked in the vertical direction, and the refrigerant tubes 50 are positioned at the lowermost end and the uppermost end of the fin 60.
  • the refrigerant tubes 50 are connected to the upper end of the fin 60 and the lower end of the fin 60.
  • the fin 60 between the first refrigerant tube 50 or 51 and the second refrigerant tube 50 or 52 may be defined as a first fin 60 or 61.
  • an nth refrigerant tube and an nth fin may be defined.
  • the header 70 may be coupled to one end of each of the plurality of refrigerant tubes 50 to supply the refrigerant into the plurality of refrigerant tubes 50. Further, the header 70 may be coupled to one end of the refrigerant tube 50 to collect the refrigerant discharged from the refrigerant tube 50 and supply the collected refrigerant to another device.
  • the header 70 has a diameter, inner diameter, or size larger than that of the refrigerant tubes 50, and extends in the vertical direction.
  • the header 70 may include a left header 71 connected to one end of the refrigerant tube 50, and a lower header 70 or 81 connected to the other end of the refrigerant tube 50.
  • the right header 81 communicates with right sides of the plurality of refrigerant tubes 50.
  • the right header 81 extends long in the vertical direction, and is connected to an inlet pipe 22.
  • the interior of the right header 81 is formed as one space, so that the refrigerant introduced through the inlet pipe 22 is distributed and supplied to the plurality of refrigerant tubes 50.
  • the inlet pipe 22 is an example of a refrigerant supply unit.
  • the inlet pipe 22 is connected to a region adjacent to the lower end of the right header 81.
  • the left header 71 communicates with the left sides of the plurality of refrigerant tubes 50.
  • the left header 71 extends long in the vertical direction, and is connected to an outlet pipe 24.
  • the interior of the left header 71 is formed as one space to guide the refrigerant, discharged to the upper side of the plurality of refrigerant tubes 50, to the outlet pipe 24.
  • the refrigerant discharged from the left header 71 may be supplied to the header 70 of another heat exchanger 100.
  • the outer pipe 110 and the inner pipe 120 may be positioned to prevent the refrigerant from being biased inside the header 70.
  • the refrigerant is uniformly distributed through holes of the outer pipe 110 and the inner pipe 120.
  • FIG. 6A is a sectional perspective view of FIG. 5
  • FIG. 6B is an enlarged view of a portion of FIG. 6A .
  • one surface of the sacrificial sheet 90 contacts the refrigerant tube 50, and the other surface contacts the fin 60, so that the sacrificial sheet is corroded instead of the fin 60 and the refrigerant tube 50, thus suppressing the corrosion of the fin 60 and the refrigerant tube 50 and preventing the separation of the fin 60 from the refrigerant tube 50.
  • the corrosion potential of the sacrificial sheet 90 may be lower than the corrosion potential of the refrigerant tube 50. If corrosion occurs while two metals contact each other, the metal with the lower corrosion potential is corroded first, so that the sacrificial sheet 90 is corroded instead of the refrigerant tube 50, thus preventing the refrigerant tube 50 from corroding and preventing the refrigerant from leaking out.
  • the corrosion potential of the sacrificial sheet 90 may be lower than the corrosion potential of the fin 60. Even if only the refrigerant tube 50 is not corroded, the leakage of the refrigerant is prevented. However, when the fin 60 is corroded, the flow of air is hindered and the efficiency of the refrigerant is lowered. Thus, the corrosion potential of the sacrificial sheet 90 is preferably lower than the corrosion potential of the fin 60.
  • the corrosion potential of the sacrificial sheet 90 is lower than the corrosion potential of the fin 60, the sacrificial sheet 90 is corroded first instead of the fin 60, thus preventing the fin 60 from being corroded.
  • the corrosion potential of the fin 60 may be lower than the corrosion potential of the refrigerant tube 50.
  • a dangerous part when corrosion occurs is the refrigerant tube 50.
  • efficiency may be slightly lowered.
  • the refrigerant tube 50 is corroded, the refrigerant leaks out and the air conditioner is not operated, causing a major problem.
  • the corrosion potential of the fin 60 is set to be lower than the corrosion potential of the refrigerant tube 50, so that the fin 60 is corroded prior to the refrigerant tube 50, thus preventing the corrosion of the refrigerant tube 50.
  • the corrosion potential of the sacrificial sheet 90 may be lower than the corrosion potential of the refrigerant tube 50, the corrosion potential of the sacrificial sheet 90 may be lower than the corrosion potential of the fin 60, and the corrosion potential of the fin 60 may be lower than the corrosion potential of the refrigerant tube 50.
  • the corrosion potential of the sacrificial sheet 90 may range from - 0.97V to - 1.1V
  • the corrosion potential of the fin 60 may range from -0.75V to - 0.95V
  • the corrosion potential of the refrigerant tube 50 may range from -0.6V to - 0.7V
  • the corrosion potential of the sacrificial sheet 90 may be lower than the corrosion potential of the fin 60, or may be lower than the corrosion potential of the refrigerant tube 50.
  • the material of the sacrificial sheet 90 may be different from the material of the fin 60 and the material of the refrigerant tube 50.
  • the material of the sacrificial sheet 90 may include metal or alloy that satisfies the corrosion potential. Considering cost, the ease of manufacture, thermal conductivity, etc., the sacrificial sheet 90 preferably includes zinc or an alloy of zinc and aluminum. However, the material of the sacrificial sheet 90 is not limited thereto.
  • the material of the fin 60 may include metal or alloy that satisfies the corrosion potential. Considering cost, the ease of manufacture, thermal conductivity, etc., the fin 60 preferably includes at least one of aluminum, copper, and aluminum alloy. However, the material of the fin 60 is not limited thereto.
  • the material of the refrigerant tube 50 may include metal or alloy that satisfies the corrosion potential. Considering cost, the ease of manufacture, thermal conductivity, etc., the refrigerant tube 50 preferably includes at least one of aluminum, copper, and aluminum alloy. However, the material of the refrigerant tube 50 is not limited thereto.
  • the sacrificial sheet 90 is positioned on the upper surface and/or lower surface of the refrigerant tube 50.
  • the sacrificial sheet 90 is in surface contact with the upper surface and/or lower surface of the refrigerant tube 50.
  • the sacrificial sheet 90 may cover the entire upper surface and/or lower surface of the refrigerant tube 50.
  • the width of the sacrificial sheet 90 in the front-rear direction may be at least equal to the width of the fin 60 and the refrigerant tube 50 or larger than the width of the fin 60 and the refrigerant tube 50. This is because when the width of the sacrificial sheet 90 is reduced, corrosion first occurs in a portion where the sacrificial sheet 90 is not present.
  • the sacrificial sheet 90 may have a structure that enhances a coupling force with the refrigerant tube 50 and facilitates alignment with the refrigerant tube 50.
  • the sacrificial sheet 90 may include a first region 92 and a second region 91 with a step between the first region 92 and the second region.
  • the width of the first region 92 may be greater than that of the second region 91.
  • the second region 91 is a region having a height difference from the first region 92.
  • the second region 91 may be formed by drawing a portion of the first region 92.
  • the second region 91 may protrude toward the refrigerant tube 50 contacting the sacrificial sheet 90.
  • the second region 91 may be formed by recessing a portion of the first region 92.
  • the second region 91 may be continuously or intermittently formed in the longitudinal direction (left-right direction) of the refrigerant tube 50.
  • the second region 91 may be continuously or intermittently formed in the width direction (front-rear direction) of the refrigerant tube 50.
  • the refrigerant tube 50 may further include a matching portion 50b corresponding to the second region 91.
  • the matching portion 50b is a portion matched with the second region 91.
  • the matching portion 50b may be inserted into the second region 91 or may be a space into which the second region 91 is inserted.
  • the matching portion 50b may be configured as a groove.
  • the thickness T3 of the sacrificial sheet 90 may be thicker than the thickness T1 of the fin 60.
  • the thickness of the refrigerant tube 50 may be thicker than the thickness T3 of the sacrificial sheet 90.
  • the thickness T3 of the sacrificial sheet 90 is too thin, it is rapidly corroded, thus shortening the lifespan of the heat exchanger. If the thickness T2 of the sacrificial sheet 90 is too thick, cost burden increases and thermal conductivity also deteriorates.
  • the thickness T2 of the sacrificial sheet 90 preferably has a value between the thickness T1 of the fin 60 and the thickness T3 of the refrigerant tube 50.
  • the heat exchanger of the present disclosure has one or more of the follow effects.
  • the present disclosure is advantageous in that a sacrificial sheet disposed between a fin and a refrigerant tube has a low corrosion potential, so that the sacrificial sheet is corroded prior to the refrigerant tube and the fin by external water or air, thus preventing the corrosion of the fin and the tube and preventing the fin from being separated from the tube.
  • the present disclosure is advantageous in that a sacrificial sheet covers both the upper and lower surfaces of a refrigerant tube to have a thick thickness, so that it can withstand corrosion for a long time, and consequently, sacrificial corrosion is performed for a long time, thus increasing the lifespan of a heat exchanger.
  • the present disclosure is advantageous in that a sacrificial sheet is attached to an outer surface of a refrigerant tube, and a fin is brazed on the sacrificial sheet, so that it facilitates manufacture, reduces manufacturing time, and reduces manufacturing cost compared to brazing by applying zinc particles, and zinc concentration around the fin becomes uniform.
  • the present disclosure is advantageous in that a region of a sacrificial sheet is inserted into a groove of a refrigerant tube, so that the refrigerant tube and the sacrificial sheet are easily aligned, and the separation of the refrigerant tube from the sacrificial sheet is prevented.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP23199837.8A 2022-09-29 2023-09-26 Wärmetauscher Pending EP4345407A1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
KR1020220124455A KR20240044900A (ko) 2022-09-29 2022-09-29 열교환기

Publications (1)

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EP4345407A1 true EP4345407A1 (de) 2024-04-03

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US (1) US20240110755A1 (de)
EP (1) EP4345407A1 (de)
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CN (1) CN117781516A (de)

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20070256822A1 (en) * 1999-08-06 2007-11-08 Denso Corporation Heat exchanger
WO2009101896A1 (ja) * 2008-02-12 2009-08-20 Kabushiki Kaisha Kobe Seiko Sho アルミニウム合金積層板
US20130292012A1 (en) * 2011-01-20 2013-11-07 Nippon Light Metal Company, Ltd. Aluminum alloy for small-bore hollow shape use excellent in extrudability and intergranular corrosion resistance and method of production of same
KR20150035416A (ko) 2013-09-27 2015-04-06 성균관대학교산학협력단 관통 저항성이 향상된 열교환기용 알루미늄 합금, 이를 포함하는 관통 저항성이 향상된 알루미늄 압출 튜브와 핀 재 및 이로 구성된 열교환기
JP5917786B2 (ja) * 2008-02-12 2016-05-18 株式会社神戸製鋼所 疲労特性に優れたアルミニウム合金積層板
US20170045316A1 (en) * 2014-04-22 2017-02-16 Uacj Corporation Aluminum cladding material, production method therefor, aluminum cladding material for heat exchangers, production method therefor, aluminum heat exchanger using said aluminum cladding material for heat exchangers, and production method therefor
US20210033346A1 (en) * 2018-01-31 2021-02-04 Daikin Industries, Ltd. Heat exchanger and air conditioning apparatus
US20210348858A1 (en) * 2018-12-19 2021-11-11 Carrier Corporation Aluminum heat exchanger with fin arrangement for sacrificial corrosion protection

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20070256822A1 (en) * 1999-08-06 2007-11-08 Denso Corporation Heat exchanger
WO2009101896A1 (ja) * 2008-02-12 2009-08-20 Kabushiki Kaisha Kobe Seiko Sho アルミニウム合金積層板
JP5917786B2 (ja) * 2008-02-12 2016-05-18 株式会社神戸製鋼所 疲労特性に優れたアルミニウム合金積層板
US20130292012A1 (en) * 2011-01-20 2013-11-07 Nippon Light Metal Company, Ltd. Aluminum alloy for small-bore hollow shape use excellent in extrudability and intergranular corrosion resistance and method of production of same
KR20150035416A (ko) 2013-09-27 2015-04-06 성균관대학교산학협력단 관통 저항성이 향상된 열교환기용 알루미늄 합금, 이를 포함하는 관통 저항성이 향상된 알루미늄 압출 튜브와 핀 재 및 이로 구성된 열교환기
US20170045316A1 (en) * 2014-04-22 2017-02-16 Uacj Corporation Aluminum cladding material, production method therefor, aluminum cladding material for heat exchangers, production method therefor, aluminum heat exchanger using said aluminum cladding material for heat exchangers, and production method therefor
US20210033346A1 (en) * 2018-01-31 2021-02-04 Daikin Industries, Ltd. Heat exchanger and air conditioning apparatus
US20210348858A1 (en) * 2018-12-19 2021-11-11 Carrier Corporation Aluminum heat exchanger with fin arrangement for sacrificial corrosion protection

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CN117781516A (zh) 2024-03-29
KR20240044900A (ko) 2024-04-05
US20240110755A1 (en) 2024-04-04

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