EP2031335A2 - Échangeur thermique et appareil de cycle de réfrigération en disposant - Google Patents

Échangeur thermique et appareil de cycle de réfrigération en disposant Download PDF

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Publication number
EP2031335A2
EP2031335A2 EP08163152A EP08163152A EP2031335A2 EP 2031335 A2 EP2031335 A2 EP 2031335A2 EP 08163152 A EP08163152 A EP 08163152A EP 08163152 A EP08163152 A EP 08163152A EP 2031335 A2 EP2031335 A2 EP 2031335A2
Authority
EP
European Patent Office
Prior art keywords
refrigerant
refrigerant tubes
tubes
diameter
slits
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP08163152A
Other languages
German (de)
English (en)
Other versions
EP2031335A3 (fr
Inventor
Dong Hwi Kim
Yong Cheol Sa
Han Choon Lee
Sang Yeul Lee
Ju Hyok Kim
Hong Seong Kim
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 EP2031335A2 publication Critical patent/EP2031335A2/fr
Publication of EP2031335A3 publication Critical patent/EP2031335A3/fr
Withdrawn legal-status Critical Current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
    • 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
    • F28F1/325—Fins with openings
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • 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
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/08—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by varying the cross-section of the flow channels
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • 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
    • 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
    • F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05333—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
    • 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
    • F28D2021/007—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
    • 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
    • F28D2021/0071—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2210/00—Heat exchange conduits
    • F28F2210/08—Assemblies of conduits having different features
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/02—Arrangements of fins common to different heat exchange sections, the fins being in contact with different heat exchange media

Definitions

  • the present invention relates to a heat exchanger for exchanging heat between refrigerant and air and a refrigeration cycle apparatus having the same, and more particularly, to a heat exchanger in which a plurality of refrigerant tubes through which refrigerant passes are provided back and forth in an air flowing direction and a refrigeration cycle apparatus having the same.
  • a refrigeration cycle apparatus for cooling/heating the room using a refrigeration cycle generally includes a compressor, a condenser, an expander, and an evaporator. Further, a heat exchanger including the condenser and the evaporator has a refrigerant channel through which refrigerant passes.
  • FIG. 1 is a side view illustrating an enlargement of a part of a background art heat exchanger.
  • refrigerant flows in the inside of a plurality of columns of refrigerant tubes 102 and 104 and air A flows on the surface of a fin 106 that is an enlarged surface connected to external sides of the refrigerant tubes 102 and 104.
  • the heat exchanger has an optimal heat transfer area suitable for the characteristics of the refrigerant and the air.
  • the columns of refrigerant tubes 102 and 104 are arranged so that refrigerant tubes having the same diameter are positioned back and forth in an air flowing direction and that the latter columns of refrigerant tubes 104 are positioned in the rear between former columns of refrigerant tubes 102.
  • the row pitch of the refrigerant tubes 102 and 104 is set to have an enough heat transfer area and the optimal heat transfer area of the air varies in accordance with the diameter of the tubes.
  • the entire volume of the background art heat exchanger having the above structure is determined by the diameters of the refrigerant tubes 102 and 104 and the width L of the fin 106. Further, the heat exchanger is generally made to have a thin shape. However, because the diameters of the refrigerant tubes 102 and 104 are equal to each other in the heat exchanger having the above-described structure, the heat exchanger cannot be easily made to have a thin shape.
  • a dead zone 108 to which the air is not directly transferred exists in the rear parts of the refrigerant tubes 102 and 104 so that the actual heat transfer area is reduced.
  • one object of the present invention is to address the above-noted and other drawbacks.
  • Another object of the present invention is to provide a heat exchanger capable of being made thin and that minimizes a dead zone to which air and refrigerant are not transferred to improve the heat transfer performance of the heat exchange.
  • Yet another object of the present invention is to provide a refrigeration cycle apparatus having a heat exchanger capable of being made thin and that minimizes the pressure loss of refrigerant.
  • the present invention provides in one aspect a heat exchanger including a plurality of first refrigerant tubes, and a plurality of second refrigerant tubes separated from the plurality of first refrigerant tubes in an air flow direction. Further, a diameter of a respective refrigerant tube of the plurality of first refrigerant tubes is smaller than a diameter of a respective refrigerant tube of the plurality of second refrigerant tubes.
  • the present invention provides a refrigeration cycle apparatus including a compressor configured to compress a refrigerant, a condenser connected to the compressor and configured to condense the refrigerant, an expander connected to the condenser and configured to expand the refrigerant, and an evaporator connected to the expander and the compressor and configured to evaporate the refrigerant.
  • At least one of the condenser and the evaporator includes a plurality of first refrigerant tubes, and a plurality of second refrigerant tubes separated from the plurality of first refrigerant tubes in an air flow direction, a diameter of a respective refrigerant tube of the plurality of first refrigerant tubes is smaller than a diameter of a respective refrigerant tube of the plurality of second refrigerant tubes, and the at least one of the condenser and the evaporator further includes a connector configured to connect together the respective refrigerant tube of the plurality of first refrigerant tubes and the respective refrigerant tube of the plurality of second refrigerant tubes so that liquid refrigerant passes through the plurality of first refrigerant tubes and that gas refrigerant passes through the plurality of second refrigerant tubes.
  • FIG. 1 is a side view illustrating an enlargement of a part of a background art heat exchanger
  • FIG. 2 is an overview illustrating a heat exchanger according to an embodiment of the present invention
  • FIG. 3 is a side view illustrating an enlargement of a part of the heat exchanger according to an embodiment of the present invention
  • FIG. 4 is a perspective view illustrating an enlargement of a part of a fin of FIG. 3 ;
  • FIG. 5 is a partial sectional view illustrating a connector connecting the former and latter columns of refrigerant tubes of FIG. 3 ;
  • FIG. 6 is a graph illustrating a change in performance in accordance with a diameter ratio of the columns of refrigerant tubes of the heat exchanger according to an embodiment of the present invention
  • FIG. 7 is an overview illustrating a refrigeration cycle apparatus having the heat exchanger according to an embodiment of the present invention.
  • FIG. 8 is a graph schematically comparing a heat transfer performance of the heat exchanger according to an embodiment of the present invention with a heat transfer performance of the background art heat exchanger.
  • FIG. 2 is an overview illustrating a heat exchanger according to an embodiment of the present invention.
  • the heat exchanger includes a plurality of columns of refrigerant tubes 2 and 4 through which refrigerant passes and fins 10 coupling the plurality of columns of refrigerant tubes 2 and 4. Further, the plurality of fins 10 are coupled to the refrigerant tubes 2 and 4 by a predetermined distance.
  • the refrigerant tubes 2 and 4 are longitudinally arranged to be orthogonal to the flowing direction of air A and the fins 10 are arranged to run parallel to the flowing direction of the air A.
  • the refrigerant tubes 2 and 4 also include former columns of refrigerant tubes 2 positioned in the front in the air flowing direction and latter columns of refrigerant tubes 4 positioned in the rear.
  • the former columns of refrigerant tubes 2 and the latter columns of refrigerant tubes 4 are integrally connected to each other so that refrigerant that passes through the refrigerant tubes 2 and 4.
  • the refrigerant tubes 2 and 4 are formed so that the diameter D1 of the former columns of refrigerant tubes 2 is smaller than the diameter D2 of the latter columns of refrigerant tubes 4. That is, in the heat exchanger according to the present embodiment, the diameter of the former columns of refrigerant tubes 2 is different from the diameter of the latter columns of refrigerant tubes 4 such that the heat exchanger can be made thinner.
  • the refrigerant tubes 2 having a small diameter are used for the former columns to increase the flow rate of the refrigerant affected by the sectional area of the tubes and to increase the heat transfer coefficient of the refrigerant tubes, in particular, the heat transfer coefficient of the insides of the former columns of refrigerant tubes 2.
  • the heat transfer coefficient increases in accordance with an increase in the flow rate of the refrigerant.
  • the heat transfer area of the insides of the refrigerant tubes having the small diameter is reduced, when the refrigerant tubes having the small diameter are used for the former and latter columns of refrigerant tubes of the heat exchanger, the total heat transfer amount is reduced so that the pressure loss of the refrigeration apparatus is increased.
  • the pressure loss is reduced than when all of the former and latter columns of the refrigerant tubes 2 and 4 are formed of the tubes having the large diameter. That is, although the distance SP between the former and latter columns of refrigerant tubes 2 and 4 is reduced, the pressure loss of the air is not increased. Also, when the distance SP between the former and latter columns of refrigerant tubes 2 and 4 is reduced, the fin efficiency can be increased. In addition, due to the reduction in the pressure loss of the air, the noise is minimized and the power consumption of a fan for flowing the air to the heat exchanger is reduced.
  • a dead zone in the rear of the former columns of refrigerant tubes 2 is smaller than when the former columns of refrigerant tubes 2 have the same diameter as the diameter of the latter columns of refrigerant tubes 4.
  • the size of former columns of colars 12 coupled to the former columns of refrigerant tubes 2 is smaller than the size of latter columns of colars 14 coupled to the latter columns of refrigerant tubes 4.
  • the diameter of the latter columns of refrigerant tubes 4 is preferably set to be 3mm to 12mm and the former columns of refrigerant tubes 2 and the latter columns of refrigerant tubes 4 are formed so that the distance SP between the tubes is 15mm to 25mm in a direction perpendicular to the flowing direction of the air.
  • the sum of the width RP1 of the forward fin unit 16 and the width RP2 of the backward fin unit 18 is about 10mm to 30mm.
  • the fin 10 also includes slits 20 and 22 that increase the heat transfer area through which the air passes.
  • slits 20 and 22 that increase the heat transfer area through which the air passes.
  • at least three columns of forward slits 20 are formed in the forward fin unit 16 and at least three columns of backward slits 22 are formed in the backward fin unit 18.
  • the length SL1 of the forward slits 20 is preferably 0.3mm to 1.5mm and the length SL2 of the backward slits 22 is preferably 0.3mm to 1.5mm.
  • the forward slits 20 and the backward slits 22 are also asymmetrical with each other so that heat transfer performance is maximally improved.
  • the area of a space between the former columns of refrigerant tubes 2 in the forward fin unit 16 is larger when the diameter of the former columns of refrigerant tubes 2 is different from the diameter of the later columns of refrigerant tubes 4 than when the diameter of the former columns of refrigerant tubes 2 is equal to the diameter of the latter columns of refrigerant tubes 4.
  • the length SL1 of the forward slits 20 is longer than the length SL2 of the backward slits 22.
  • the width d1 of the forward slits 20 and the width d2 of the backward slits 22 are preferably 0.5mm to 2mm.
  • the slits 20 and 22 are also formed in the same or opposite directions as to the direction in which the colars 12 and 14 protrude and the minimum distance between adjacent slits is preferably 0.5mm.
  • the length SL1, the width d1, and the number of former columns of slits 20 are designed to be optimal in accordance with the area of the latter columns of slits 22 and the area of the parts excluding the slits 20 and 22 so as to maximally secure the heat transfer performance.
  • the distance between the slits is also designed so that condensed water can be easily discharged to actively transfer heat.
  • the length SL2, the width d2, and the number of the latter columns of slits 22 are designed in accordance with the fin area different from the fin area of the former columns of slits 20 so that it is possible to maximally transfer the heat.
  • flat units 17 and 19 are formed between the slits in the forward fin unit 16 and the backward fin unit 18 and the widths d3 and d4 of the flat units 17 and 19 are made large so that the condensed water can be easily discharged.
  • a U-shaped connector 24 connected to a former column of refrigerant tube 2 and a latter column of refrigerant tube 4 is provided to connect the refrigerant tubes 2 and 4.
  • the connector 24 is also formed so that the diameter D3 of a part 26 connected to the former column of refrigerant tube 2 is smaller than the diameter D4 of a part 28 connected to the latter column of refrigerant tube 4.
  • the connector 24 is formed so that the area of a channel increases from the part connected to the former column of refrigerant tube 2 toward the part 28 connected to the latter column of refrigerant tube 4.
  • FIG. 6 is a graph illustrating a change in performance in accordance with the diameter ratio of the former and latter columns of refrigerant tubes of the heat exchanger according to an embodiment of the present invention.
  • FIG. 6 illustrates a heat transfer performance in accordance with the ratio D1/D2 of the tubes 2 and 4.
  • FIG. 6 illustrates an embodiment when the diameter of the latter columns of refrigerant tubes 4 is 3mm to 12mm, the distance SP between the former columns of refrigerant tubes 2 and the distance SP between the latter columns of refrigerant tubes 4 are 15mm to 25mm and when the width of the air flowing direction of the fin is 10 mm to 30mm.
  • the ratio D1/D2 is 0.3 to 0.95. Further, the heat transfer performance rapidly deteriorates when the ratio D1/D2 is less than 0.3. That is, in the heat exchanger according to an embodiment of the present embodiment, the ratio D1/D2 is 0.3 to 0.95.
  • the diameter D2 of the latter columns of refrigerant tubes 4 is 7mm
  • the diameter of the former columns of refrigerant tubes 2 is set to be 2.1mm to 6.65mm.
  • FIG. 7 is an overview illustrating a refrigeration cycle apparatus having the heat exchanger according to an embodiment of the present invention.
  • the refrigeration cycle apparatus includes a compressor 32 for circulating refrigerant, a condenser 34, an expander 36 and an evaporator 38. Also included is a condenser fan 35 for blowing the air to the condenser 34 rotatably provided around the condenser 34. An evaporator fan 39 for blowing the air to the evaporator 38 is also rotatably provided around the evaporator 38.
  • the evaporator 38 functions as an indoor heat exchanger for extracting heat from the indoor air and evaporating the refrigerant
  • the condenser 34 functions as an outdoor hear exchanger for discharging heat to the outdoor air and condensing the refrigerant.
  • At least one of the condenser 34 and the evaporator 38 is formed of the heat exchanger illustrated in FIGs. 2 to 5 . That is, at least one of the condenser 34 and the evaporator 38 is formed so that the diameter of the former columns of refrigerant tubes 2 is smaller than the diameter of the latter columns of refrigerant tubes 4 in the flowing direction of the air. In the next description, both of the condenser 34 and the evaporator 38 are formed of the heat exchanger illustrated in FIGs. 2 to 5 .
  • the condenser 34 and the evaporator 38 are connected to each other so that liquid refrigerant passes through the former columns of refrigerant tubes 2 and that gas refrigerant passes through the latter columns of refrigerant tubes 4, the condenser 34 and the evaporator 38 can be made thin and the pressure loss of the refrigerant is minimized.
  • the latter columns of refrigerant tubes 4, the former columns of refrigerant tubes 2, and the expander are sequentially connected to each other in a refrigerant flowing direction so that the refrigerant compressed by the compressor 32 passes through the latter columns of refrigerant tubes 4, passes through the former columns of refrigerant tubes 2, and flows to the expander.
  • the former columns of refrigerant tubes 2 and the latter columns of refrigerant tubes 4 are sequentially connected to each other in a refrigerant flowing direction so that the refrigerant expanded by the expander 36 passes through the former columns of refrigerant tubes 2, passes through the latter columns of refrigerant tubes 4, and flows to the compressor 32.
  • FIG. 8 is a graph schematically comparing a heat transfer performance of the heat exchanger according to an embodiment of the present invention with a heat transfer performance when the diameters of the background art heat exchanger.
  • the heat transfer performance is illustrated when the diameter of the former columns of refrigerant tubes 2 is 5mm, the diameter of the latter columns of refrigerant tubes 4 is 7mm, the sum of the width RP1 of the forward fin unit 16 and the width RP2 of the backward fin unit 18 is about 20mm, the distance between the center of the former column of refrigerant tube 2 and the center of the latter column of refrigerant tube 4 is 9.5mm, and the heat exchanger is used as the evaporator and the condenser and is compared with the heat transfer performance when the diameter of the former columns of refrigerant tubes 2 and the diameter of the latter columns of refrigerant tubes 4 are 7mm, the sum of the width RP1 of the forward fin unit 16 and the width RP2 of the backward fin unit 18 is about 25.4mm, the distance between the center of the former column of refrigerant tube 2 and the center of the latter column of refrigerant tube 4 is 10.5mm, and the heat exchanger is used as the
  • the heat transfer performance of the present invention is greater than that of the background art. That is, in the heat exchanger according to the present embodiment, as illustrated in FIG. 5 , although the width RP1 of the forward fin unit 16 of the fin 10 and the width RP2 of the backward fin unit 18 of the fin 10 are smaller, when the heat exchanger is used as the evaporator and the condenser, the heat transfer performance is higher than when the diameter of the former columns of refrigerant tubes 2 and the diameter of the latter columns of refrigerant tubes 4 are 7mm.
  • the diameter of the former columns of refrigerant tubes is smaller than the diameter of the latter columns of refrigerant tubes in the air flowing direction. Therefore, the heat exchanger can be made thin in the air flowing direction and a dead zone in which air and heat are not exchanged among the refrigerant tubes of the heat exchanger can be minimized to improve the heat transfer performance.
  • liquid refrigerant flows through the former columns of refrigerant tubes having the small diameter and gas refrigerant flows through the latter columns of refrigerant tubes having the large diameter so that the condenser and the evalporator can be made thin and the pressure loss of the refrigerant can be minimized.
  • the heat exchanger includes the plurality of columns of refrigerant tubes and the diameter of the former columns of refrigerant tubes is smaller than the diameter of the latter columns of refrigerant tubes in the air flowing directioin. Therefore, the heat exchanger can be made thin and can be used for a refrigeration cycle apparatus capable of minimizing the pressure loss of the refrigerant. The dead zone and pressure loss can also be minimized.

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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)
EP08163152A 2007-08-31 2008-08-28 Échangeur thermique et appareil de cycle de réfrigération en disposant Withdrawn EP2031335A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
KR1020070088489A KR20090022840A (ko) 2007-08-31 2007-08-31 냉동장치의 열교환기

Publications (2)

Publication Number Publication Date
EP2031335A2 true EP2031335A2 (fr) 2009-03-04
EP2031335A3 EP2031335A3 (fr) 2011-04-13

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP08163152A Withdrawn EP2031335A3 (fr) 2007-08-31 2008-08-28 Échangeur thermique et appareil de cycle de réfrigération en disposant

Country Status (4)

Country Link
US (1) US20090084129A1 (fr)
EP (1) EP2031335A3 (fr)
KR (1) KR20090022840A (fr)
CN (1) CN101377368A (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
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DE102008049896A1 (de) * 2008-10-03 2010-04-08 Solarhybrid Ag Luftwärmepumpe und Lamellenluftwärmetauscher sowie Verfahren zu deren Betrieb
WO2011061072A3 (fr) * 2009-11-23 2012-01-26 BSH Bosch und Siemens Hausgeräte GmbH Échangeur thermique comportant un canal de fluide frigorigène
EP3062037A4 (fr) * 2013-10-25 2017-07-19 Mitsubishi Electric Corporation Échangeur thermique et dispositif à cycle de réfrigération utilisant ledit échangeur thermique
EP3117162A4 (fr) * 2014-03-11 2017-11-29 Brazeway, Inc. Modèle de tube pour évaporateur de réfrigérateur
EP2498039A4 (fr) * 2009-11-04 2018-01-03 Daikin Industries, Ltd. Échangeur de chaleur et unité interne équipée de celui-ci

Families Citing this family (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100974717B1 (ko) * 2007-12-04 2010-08-06 현대자동차주식회사 연료전지차량용 ｃｏｄ 겸용 가열장치
KR101520484B1 (ko) * 2008-07-04 2015-05-14 엘지전자 주식회사 열교환기
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US20090084129A1 (en) 2009-04-02
KR20090022840A (ko) 2009-03-04
EP2031335A3 (fr) 2011-04-13

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