EP3279598A1 - Échangeur de chaleur et climatiseur - Google Patents

Échangeur de chaleur et climatiseur Download PDF

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Publication number
EP3279598A1
EP3279598A1 EP16772077.0A EP16772077A EP3279598A1 EP 3279598 A1 EP3279598 A1 EP 3279598A1 EP 16772077 A EP16772077 A EP 16772077A EP 3279598 A1 EP3279598 A1 EP 3279598A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
corrugated
flat tubes
fin
lug
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.)
Granted
Application number
EP16772077.0A
Other languages
German (de)
English (en)
Other versions
EP3279598B1 (fr
EP3279598A4 (fr
Inventor
Susumu Yoshimura
Ryota AKAIWA
Takashi Matsumoto
Akira Ishibashi
Yuki UGAJIN
Takumi NISHIYAMA
Satoshi Ueyama
Aya KAWASHIMA
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.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Publication of EP3279598A1 publication Critical patent/EP3279598A1/fr
Publication of EP3279598A4 publication Critical patent/EP3279598A4/fr
Application granted granted Critical
Publication of EP3279598B1 publication Critical patent/EP3279598B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/14—Heat exchangers specially adapted for separate outdoor units
    • F24F1/18—Heat exchangers specially adapted for separate outdoor units characterised by their shape
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F17/00—Removing ice or water from heat-exchange apparatus
    • F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F25B39/02—Evaporators
    • 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
    • F25B39/02—Evaporators
    • F25B39/022—Evaporators with plate-like or laminated elements
    • 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
    • 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
    • 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
    • F28F1/128—Fins with openings, e.g. louvered 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
    • 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
    • F28F1/30—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 being attachable to 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
    • 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
    • F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
    • 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

Definitions

  • the present invention relates to a heat exchanger that is to be used in air-conditioning apparatuses such as a room air-conditioning apparatus and a package air-conditioning apparatus, and to an air-conditioning apparatus including the heat exchanger.
  • the present invention has been made to solve the above-mentioned problem and has an object to provide a heat exchanger and an air-conditioning apparatus that are capable of preventing degradation of defrosting performance while promoting heat transfer.
  • a heat exchanger including a plurality of flat tubes arranged in a right-and-left direction orthogonal to a front-and-back direction, the front-and-back direction being an airflow direction of the heat exchanger, a corrugated fin sandwiched by adjacent ones of the plurality of flat tubes and thermally connected to the adjacent ones of the plurality of flat tubes at each of apexes of the corrugated fin, an inlet header connected to one end of each of the plurality of flat tubes, and an outlet header connected to the other end of each of the plurality of flat tubes, the plurality of flat tubes extending along an up-and-down direction of the heat exchanger, the corrugated fin including a protruding portion protruding to a front side with respect to a front-side end portion of each of the plurality of flat tubes, the protruding portion including a first lug portion oriented obliquely to the front-and-back direction, the corrugated fin further including
  • the corrugated fin includes the protruding portion protruding to the front side with respect to the front-side end portion of each of the flat tubes.
  • the protruding portion includes the (first) lug portion to promote heat transfer.
  • the lug portion is oriented obliquely to the front-and-back direction that is the airflow direction.
  • a heat transfer passage is less likely to be divided by the lug portion during a defrosting operation as compared to a case where the lug portion is formed in the airflow orthogonal direction.
  • heat can sufficiently be transferred to the protruding portion and the lug portion of the corrugated fin, thereby being capable of preventing the degradation of the defrosting performance.
  • FIG. 1 is a perspective view for illustrating a corrugated-fin heat exchanger 10 according to Embodiment 1 of the present invention.
  • FIG. 2 is an enlarged front view of flat tubes 1 and corrugated fins 2 of the corrugated-fin heat exchanger 10 according to Embodiment 1 of the present invention.
  • the arrow WF in FIG. 1 indicates a flow of air (airflow direction) generated by a fan 31 (see FIG. 4 and FIG. 5 described later) or other units, and the arrow RF indicates a flow of refrigerant.
  • the same arrows are used in the drawings described later.
  • the expressions “up”, “down”, “left”, “right”, “front”, and “back” used in Embodiment 1 indicate directions that are given when the corrugated-fin heat exchanger 10 is viewed from the front side unless otherwise noted.
  • the corrugated-fin heat exchanger 10 includes the plurality of flat tubes 1 arranged in an airflow orthogonal direction (right-and-left direction) orthogonal to the airflow direction (front-and-back direction) indicated by the arrow WF, the meandering corrugated fins 2 each sandwiched by the adjacent flat tubes 1 and thermally connected to the flat tubes 1 at each apex 2a, an inlet header 3 connected to one end (lower end) of each flat tube 1, and an outlet header 4 connected to the other end (upper end) of each flat tube 1.
  • the corrugated-fin heat exchanger 10 exchanges heat between refrigerant flowing through the flat tubes 1 and air flowing through spaces each surrounded by the adjacent flat tubes 1 and the corrugated fin 2 (hereinafter referred to as "heat-exchanger air passages").
  • Each flat tube 1 extends along an up-and-down direction.
  • the corrugated fins 2 are each a metal thin plate shaped to have peaks and troughs that are apexes 2a alternately as viewed from one side.
  • the peaks of the corrugated fin 2 are joined to a surface of one flat tube 1 of the two flat tubes 1 adjacent in the airflow orthogonal direction (right-and-left direction), and the troughs of the corrugated fin 2 are joined to a surface of the other flat tube 1.
  • the peaks and the troughs of the corrugated fin 2 have a shape extending in the airflow direction (front-and-back direction).
  • joined portions between the corrugated fin 2 and the flat tube 1 each have a linear shape being continuous in the airflow direction (front-and-back direction).
  • the joined portions each have a width enough for the joining.
  • the joined portions between the corrugated fins 2 and the flat tubes 1 each have a wide linear shape.
  • FIG. 3 is a sectional view of the corrugated-fin heat exchanger 10 according to Embodiment 1 of the present invention that is taken along the line A-A of FIG. 2 .
  • FIGS. 6 are views for illustrating first lug portions 7 of the corrugated-fin heat exchanger 10 according to Embodiment 1 of the present invention.
  • a part (a) is a perspective view of the first lug portions 7, and a part (b) is a sectional view taken along the line B-B of the part (a).
  • each of the corrugated fins 2 there is formed a protruding portion 5 protruding to a windward side (front side) with respect to windward-side end portions (front-side end portions) 1a of the flat tubes 1. Further, a plurality of lug portions are formed in the corrugated fin 2 to promote heat transfer (promote heat transfer between fin and air).
  • the first lug portions 7 are formed in the protruding portion 5 in a radial direction extending from the flat tubes 1 toward a center portion of a windward-side end portion (front-side end portion) of the protruding portion 5. Those first lug portions 7 formed to be inclined (oblique) to the airflow direction (front-and-back direction) are provided such that the two first lug portions 7 are arranged in a bilaterally symmetrical manner.
  • the first lug portions 7 are each of a louver type in which two slits (cut lines) are formed in the surface of the protruding portion 5 (hereinafter referred to as "protruding surface") of the corrugated fin 2, and the first lug portions 7 are each lugged from the two slits in the protruding surface of the corrugated fin 2 in both the up and down directions.
  • second lug portions 6 formed in the airflow orthogonal direction (right-and-left direction), and the five second lug portions 6 are formed to be arrayed in the airflow direction (front-and-back direction).
  • FIG. 4 is a schematic view for illustrating an outdoor unit (side-flow type) of an air-conditioning apparatus according to Embodiment 1 of the present invention.
  • FIG. 5 is a schematic view for illustrating an outdoor unit (top-flow type) of the air-conditioning apparatus according to Embodiment 1 of the present invention.
  • FIG. 4 and FIG. 5 are also referred to in Embodiment 2 described later.
  • the corrugated-fin heat exchanger 10 is mounted to the outdoor unit of the air-conditioning apparatus including the fan 31, thereby constructing a refrigeration cycle for circulating refrigerant between the outdoor unit and an indoor unit connected to the outdoor unit by pipes.
  • FIG. 4 As the outdoor unit in which the corrugated-fin heat exchanger 10 is mounted, a side-flow type illustrated in FIG. 4 and a top-flow type illustrated in FIG. 5 are given.
  • an air outlet 32a is provided in a side surface of an outdoor-unit main body 30a on a front surface side.
  • a corrugated-fin heat exchanger 10a having an L-shape in plan view is mounted to the outdoor unit, and air inlets 33a are provided in side surfaces of the outdoor-unit main body 30a that are opposed to the corrugated-fin heat exchanger 10a.
  • the air With a flow of air that is generated by the fan 31, the air is sucked into the outdoor-unit main body 30a through the air inlets 33a, and flows through the corrugated-fin heat exchanger 10a. At this time, heat is exchanged between the air and refrigerant sent from the indoor unit (not shown), compressed in a compressor 34, and then flowing through the flat tubes of the corrugated-fin heat exchanger 10a. Subsequently, the air is blown out through the air outlet 32a to the outside of the outdoor-unit main body 30a.
  • an air outlet 32b is provided in an upper surface of an outdoor-unit main body 30b.
  • a corrugated-fin heat exchanger 10b having a U-shape in plan view is mounted to the outdoor unit, and air inlets 33b are provided in side surfaces of the outdoor-unit main body 30b that are opposed to the corrugated-fin heat exchanger 10b.
  • the air With a flow of air that is generated by the fan 31, the air is sucked into the outdoor-unit main body 30b through the air inlets 33b, and flows through the corrugated-fin heat exchanger 10b. At this time, heat is exchanged between the air and refrigerant sent from the indoor unit (not shown), compressed in the compressor 34, and then flowing through the flat tubes of the corrugated-fin heat exchanger 10b. Subsequently, the air is blown out through the air outlet 32b to the outside of the outdoor-unit main body 30b.
  • the air flows into the corrugated-fin heat exchanger 10, exchanges heat with the refrigerant flowing through the flat tubes 1 when the air flows through the heat-exchanger air passages, and flows out from the corrugated-fin heat exchanger 10.
  • refrigerant that is returned after exchanging heat with air in the indoor unit to transfer heat to be liquefied and then being decompressed into a low-temperature and low-pressure two-phase gas-liquid state flows into the corrugated-fin heat exchanger 10 serving as an evaporator, which is mounted to the outdoor unit, through the inlet header 3.
  • the refrigerant flows through the flat tubes 1, exchanges heat with air flowing through the heat-exchanger air passages to receive heat to be evaporated, then flows out through the outlet header 4, and flows into the indoor unit again. In this manner, the refrigerant circulates in the refrigeration circuit.
  • the heat of the air flowing through the heat-exchanger air passages is removed by the flat tubes 1 through the corrugated fins 2, and water vapor in the air is brought into a supersaturated state. Then, the supersaturated water vapor is condensed on surfaces of the flat tubes 1 and the corrugated fins 2 to turn into water.
  • the first lug portions 7 are formed in the radial direction extending from the flat tubes 1 toward the center of the windward-side end portion (front-side end portion) of the protruding portion 5.
  • FIG. 7 is a perspective view for illustrating drainage passages of the corrugated-fin heat exchanger 10 according to Embodiment 1 of the present invention.
  • the arrows DFa and DFb in FIG. 7 indicate flows of water in a drainage process.
  • the corrugated-fin heat exchanger 10 has two drainage passages.
  • the first passage is a passage for water flowing through the slits, which are formed in the protruding surface of the corrugated fin 2 in the course of forming the first lug portions 7, as indicated by the arrows DFb.
  • the second passage is a passage for water flowing from the protruding portion 5 through the vicinity of the apex 2a of the corrugated fin 2 along the flat tube 1, as indicated by the arrows DFa.
  • the first lug portions 7 are formed in the radial direction extending from the flat tubes 1 toward the center of the windward-side end portion (front-side end portion) of the protruding portion 5.
  • drainage of water flowing along the flat tubes 1 is promoted by the air guiding action of the first lug portions 7.
  • the fan 31 is stopped and the refrigeration cycle is switched to a cooling operation, or other measures are taken so that high-temperature refrigerant is caused to flow into the corrugated-fin heat exchanger 10. In this manner, the frost adhering to each of the surfaces of the flat tubes 1 and the corrugated fins 2 is melted.
  • the melted frost turns into water and flows along the surfaces of the flat tubes 1. Further, the water flows through the slits, which are formed in the protruding surface of the corrugated fin 2 in the course of forming the first lug portions 7, to thereby be drained to the lower part of the corrugated-fin heat exchanger 10. After the defrosting is completed, the heating operation is started again.
  • the lug portions when the lug portions are formed in the corrugated fins 2, the lug portions, specifically, the slits formed in the course of forming the lug portions divide heat transfer passages from a leeward side (back side) that is a side at the position of the flat tube 1, through which the refrigerant flows, to the windward side (front side), with the result that the fin efficiency (thermal conductivity in the fins) is lowered.
  • the first lug portions 7 are formed in the protruding portion 5 in the radial direction extending from the flat tubes 1 toward the center portion of the windward-side end portion (front-side end portion) of the protruding portion 5. Consequently, the heat transfer passages are less likely to be divided by the lug portions as compared to the case where the lug portions are formed in the airflow orthogonal direction (right-and-left direction).
  • an interval is secured between the right and left first lug portions 7.
  • FIG. 8 is a view for illustrating a modification example of the corrugated-fin heat exchanger 10 according to Embodiment 1 of the present invention.
  • FIG. 8 is a sectional view taken along the line A-A of FIG. 2 similarly to FIG. 3 .
  • the number of the first lug portions 7 is two. However, the number of the first lug portions 7 is not limited to two, and the number of the first lug portions 7 may be one. Further, as illustrated in FIG. 8 , three or more first lug portions 7 may be formed in the radial direction extending from the flat tubes 1 toward the center portion of the windward-side end portion (front-side end portion) of the protruding portion 5.
  • the drainage performance is enhanced with the action of guiding air to the flat tubes 1 serving as the drainage passages during the heating operation. Further, the heat transfer is promoted during the normal operation by the effect of front edges of the lug portions without degrading the defrosting performance during the defrosting operation, thereby being capable of enhancing the heating performance.
  • FIGS. 9 are views for illustrating a first modification example of the first lug portions 7 of the corrugated-fin heat exchanger 10 according to Embodiment 1 of the present invention.
  • FIGS. 10 are views for illustrating a second modification example of the first lug portions 7 of the corrugated-fin heat exchanger 10 according to Embodiment 1 of the present invention.
  • FIGS. 11 are views for illustrating a third modification example of the first lug portions 7 of the corrugated-fin heat exchanger 10 according to Embodiment 1 of the present invention.
  • FIGS. 12 are views for illustrating a fourth modification example of the first lug portions 7 of the corrugated-fin heat exchanger 10 according to Embodiment 1 of the present invention.
  • a part (a) is a perspective view of a modification example of the first lug portions 7, and a part (b) is a sectional view taken along the line B-B of the part (a).
  • the first modification example of the first lug portions 7 according to Embodiment 1 is of a slit type of being lugged (raised) in one direction (upward direction) from the protruding surface of the corrugated fin 2.
  • the heat transfer performance is degraded as compared to the louver type illustrated in FIGS. 6 .
  • the second modification example of the first lug portions 7 according to Embodiment 1 is of a type of being simply folded back in in one direction (upward direction) from the protruding surface of the corrugated fin 2 and lugged into a rectangular shape in plan view.
  • the heat transfer performance is degraded as compared to the louver type illustrated in FIGS. 6 and the slit type illustrated in FIGS. 9 .
  • the slits can be formed relatively easily, thereby attaining simplification of manufacture.
  • the third modification example of the first lug portions 7 according to Embodiment 1 is of a type of being folded back in the one direction (upward direction) from the protruding surface of the corrugated fin 2 and lugged into a triangular shape in plan view, in which the lugged portions are reduced in height toward the windward-side end portion (front-side end portion) of the protruding portion 5.
  • the first lug portions 7c illustrated in FIGS. 11 are increased in area to promote heat transfer by the effect of the front edges of the lug portions, that is, the first lug portions. Consequently, in the third modification example, the effect of promoting the heat transfer by the lug portions can be obtained more than the second modification example.
  • the fourth modification example of the first lug portions 7 according to Embodiment 1 is of a slit type in which one slit is formed in the protruding surface of the corrugated fin 2, and the protruding surface of the corrugated fin 2 is not raised with the slit or is raised with the slit to a small extent to form a cutout.
  • the first lug portions 7d illustrated in FIGS. 12 are small lug portions, and hence the effect of the heat transfer promotion by the lug portions is small. However, intervals formed by the fin can be prevented from being small, thereby being capable of preventing the degradation of the heating performance due to closure of the heat-exchanger air passages caused by the frost formation.
  • water generated during the defrosting operation can be drained to the lower part of the corrugated-fin heat exchanger 20 through the slits that are formed in the protruding surface of the corrugated fin 2 in the course of forming the first lug portions 7d. That is, drainage passages for water to be drained can be secured with the slits.
  • the slits of the first lug portions 7d are small, and hence the heat transfer passages are less likely to be divided. As a result, heat can sufficiently be transferred to the windward-side end portion (front-side end portion) of the protruding portion 5 and the first lug portions 7d during the defrosting operation, thereby being capable of preventing the degradation of the defrosting performance. That is, the time period required for the defrosting can be prevented from being prolonged.
  • FIG. 13 is a view for illustrating a fifth modification example of the first lug portions 7 of the corrugated-fin heat exchanger 10 according to Embodiment 1 of the present invention.
  • FIGS. 14 are enlarged front views of the flat tubes 1 and the corrugated fins 2, for illustrating a modification example of the corrugated fins 2 of the corrugated-fin heat exchanger 10 according to Embodiment 1 of the present invention.
  • FIG. 13 is a front view of the corrugated fin 2 and the first lug portions 7 of the corrugated-fin heat exchanger 10.
  • the corrugated fins 2 are each sandwiched by the adjacent flat tubes 1 and thermally connected to the flat tubes 1 at each apex 2a.
  • the fifth modification example of the first lug portions 7 according to Embodiment 1 corresponds to the two first lug portions 7e formed on the right and left sides of the center portion (of the protruding portion 5) of the corrugated fin 2 in the airflow orthogonal direction (right-and-left direction).
  • the first lug portion 7e1 on the left side is lugged from the surface of the corrugated fin 2 in the downward direction
  • the first lug portion 7e2 on the right side is lugged from the surface of the corrugated fin 2 in the upward direction. That is, the first lug portions 7e are lugged toward an outer peripheral side at the vicinity of each apex 2a of the corrugated fin 2.
  • the intervals formed by the fin are smaller on the inner peripheral side at the vicinity of each apex 2a.
  • the first lug portions 7e are lugged toward the outer peripheral side on which the intervals formed by the fin are larger, so that air flows satisfactorily at portions at which the first lug portions 7e are formed. That is, by forming the first lug portions 7e toward the outer peripheral side at the vicinity of each apex 2a of the corrugated fin 2, increase in airflow resistance can be prevented as compared to a case where the first lug portions 7e are formed toward the inner peripheral side, thereby being capable of preventing the degradation of the heating performance.
  • an interval is secured between the right and left first lug portions 7e.
  • the two first lug portions 7 are formed in the protruding portion 5 on the right and left sides to promote heat transfer. Further, the first lug portions 7 are formed in the radial direction extending from the flat tubes 1 toward the center portion of the windward-side end portion (front-side end portion) of the protruding portion 5.
  • the first lug portions 7 are oriented obliquely to the airflow direction (front-and-back direction).
  • the lug portions are formed in the airflow orthogonal direction (right-and-left direction)
  • water is easily drained with the action of guiding air to the flat tubes 1 serving as the drainage passages, and further, the heat transfer passages are less likely to be divided by the lug portions.
  • the drainage performance is enhanced during the heating operation.
  • heat can sufficiently be transferred to the windward-side end portion (front-side end portion) of the protruding portion 5 and the first lug portions 7, thereby being capable of preventing the degradation of the defrosting performance. That is, the time period required for the defrosting can be prevented from being prolonged.
  • an interval is secured between the right and left first lug portions 7.
  • the flat tubes 1 serving as the drainage passages extending in the up-and-down direction and the meandering corrugated fins 2 each sandwiched by the adjacent flat tubes 1 and thermally joined to the flat tubes 1.
  • the shape of each of the apexes of the corrugated fins 2 that are joined to the flat tubes 1 is an arc shape.
  • the shape may be a flat shape, and in this case, the joined area is increased to promote thermal conduction.
  • the corrugated fins 2 may each have a shape having surfaces perpendicular to the flat tubes 1, that is, a shape having the surfaces perpendicular to the flat tubes 1 and parallel to one another. With this shape, the pitches of the corrugated fins 2 (interval between the adjacent apexes 2a) can be reduced to increase the mounting area, thereby enhancing the heat exchange performance.
  • Embodiment 2 of the present invention is described below. Description of the same components as those of Embodiment 1 is omitted or partly omitted. The parts same as or corresponding to those of Embodiment 1 are denoted by the same reference signs.
  • FIG. 15 is a perspective view for illustrating a corrugated-fin heat exchanger 20 according to Embodiment 2 of the present invention.
  • FIG. 16 is an enlarged front view of the flat tubes 1 and the corrugated fins 2 of the corrugated-fin heat exchanger 20 according to Embodiment 2 of the present invention.
  • FIG. 17 is a sectional view taken along the line C-C of FIG. 16 .
  • the plurality of flat tubes 1 that are arranged in the airflow orthogonal direction (right-and-left direction) orthogonal to the airflow direction (front-and-back direction) indicated by the arrow WF are provided in two rows in the airflow direction (front-and-back direction).
  • Each flat tube 1 extends along the up-and-down direction.
  • the meandering corrugated fins 2 each sandwiched by the adjacent flat tubes 1 in the airflow orthogonal direction (right-and-left direction) and thermally connected to the flat tubes 1 at each apex 2a.
  • the inlet header 3 is connected to one end (lower end) of each flat tube 1 on the windward side (front side)
  • the outlet header 4 is connected to one end (lower end) of each flat tube 1 on the leeward side (back side).
  • An intermediate header 11 is connected to the other end (upper end) of each flat tube 1 on the windward side (front side) and the other end (upper end) of each flat tube 1 on the leeward side (back side). Heat is exchanged between refrigerant flowing through the flat tubes 1 and air flowing through the spaces in each of the fins of the corrugated fins 2.
  • each of the corrugated fins 2 there is formed the protruding portion 5 protruding to the windward side (front side) with respect to the windward-side end portions (front-side end portions) 1a of the flat tubes 1. Further, the plurality of lug portions are formed in the corrugated fin 2 to promote heat transfer.
  • the two first lug portions 7 that are formed to be inclined (oblique) to the airflow direction (front-and-back direction) are provided on the right and left sides.
  • the first lug portions 7 are oriented obliquely in the same direction with respect to the airflow direction (front-and-back direction).
  • the second lug portions 6 formed in the airflow orthogonal direction (right-and-left direction), and the five second lug portions 6 are formed to be arrayed in the airflow direction (front-and-back direction).
  • the corrugated-fin heat exchanger 20 is mounted to the outdoor unit of the air-conditioning apparatus including the fan 31, thereby constructing a refrigeration cycle for circulating refrigerant between the outdoor unit and an indoor unit connected to the outdoor unit by pipes.
  • the air flows into the corrugated-fin heat exchanger 20, exchanges heat with the refrigerant flowing through the flat tubes 1 when the air flows through the heat-exchanger air passages, and flows out from the corrugated-fin heat exchanger 20.
  • refrigerant that is returned after exchanging heat with air in the indoor unit to transfer heat to be liquefied and then being decompressed into a low-temperature and low-pressure two-phase gas-liquid state flows into the corrugated-fin heat exchanger 20 serving as an evaporator, which is mounted to the outdoor unit, through the inlet header 3.
  • the refrigerant flows through the flat tubes 1 on the windward side (front side), flows through the flat tubes 1 on the leeward side (back side) through the intermediate header 11, exchanges heat with air flowing through the heat-exchanger air passages to receive heat to be evaporated, then flows out through the outlet header 4, and flows into the indoor unit again. In this manner, the refrigerant circulates in the refrigeration circuit.
  • FIG. 18 is a view for illustrating a state of frost formation on the flat tubes 1 and the corrugated fins 2 during the heating operation in the corrugated-fin heat exchanger 20 according to Embodiment 2 of the present invention.
  • FIG. 19 is a view for illustrating a state of frost formation on the flat tubes 1 and the corrugated fins 2 during the defrosting operation in the corrugated-fin heat exchanger 20 according to Embodiment 2 of the present invention.
  • FIG. 20 is a perspective view for illustrating drainage passages of the corrugated-fin heat exchanger 20 according to Embodiment 2 of the present invention.
  • FIG. 18 and FIG. 19 are sectional views taken along the line C-C of FIG. 16 similarly to FIG. 17 .
  • the arrows DFa, DFb, DFc, and DFd of FIG. 20 indicate the flows of water during the defrosting operation.
  • the amount of formed frost is small at a portion on the corrugated fin 2 at which the airflow velocity is low in the airflow velocity distribution, and the amount of formed frost is large at a portion on the corrugated fin 2 at which the airflow velocity is high in the airflow velocity distribution.
  • the airflow velocity distribution is formed in a direction to which an airflow direction is slightly bent toward the airflow orthogonal direction (right-and-left direction) with the air guiding action by the first lug portions 7.
  • frost is formed to be dispersed in the front-and-back direction (airflow direction).
  • the amount of formed frost is small.
  • the first lug portions 7 are inclined to the airflow direction (front-and-back direction) and extend along with an inclination direction of each surface of the meandering corrugated fin 2, and the first lug portions 7 are alternately inclined to directions horizontally opposite to each other in the up-and-down direction. That is, a first lug portion 7 ⁇ that is inclined in the left direction from the windward side (front side) to the leeward side (back side) is formed in a surface of the corrugated fin 2 that is inclined from the right side to the left side. Further, a first lug portion 7 ⁇ that is inclined in the right direction from the windward side (front side) to the leeward side (back side) is formed in a surface of the corrugated fin 2 that is inclined from the left side to the right side.
  • the frost on the frost formation portion 40 illustrated in FIG. 18 is melted into water during the defrosting operation. Consequently, to drain the water to the lower part of the corrugated-fin heat exchanger 10, the drainage passages are formed in the corrugated-fin heat exchanger 20 as illustrated in FIG. 20 .
  • the two drainage passages are provided.
  • the first passage is a passage for water flowing through the slits formed in the protruding surface of the corrugated fin 2 in the course of forming the first lug portions 7, as indicated by the arrow DFc and the arrow DFd.
  • the second passage is a passage for water flowing from the protruding portion 5 to the vicinity of the apex 2a of the corrugated fin 2 and flowing through a part between the flat tube 1 on the windward side (front side) and the flat tube 1 on the leeward side (back side), as indicated by the arrow DFa and the arrow DFb.
  • the first lug portions 7 are provided to be inclined to the airflow direction (front-and-back direction) and to extend along with the inclination direction of the meandering corrugated fin 2.
  • the gravity water is easily guided to the part between the flat tube 1 on the windward side (front side) and the flat tube 1 on the leeward side (back side).
  • the flat tubes 1 are provided in two rows in the airflow direction (front-and-back direction). Consequently, in addition to the passage for water flowing through the slits and the passage for water flowing along the flat tube 1, there is formed the passage for water flowing through the part between the flat tube 1 on the windward side (front side) and the flat tube 1 on the leeward side (back side).
  • the drainage performance can further be enhanced with the above-mentioned air guiding action.
  • the enhancement of the drainage performance with the air guiding action exerts the effect to promote drainage of water to the flat tubes 1 not only during the defrosting operation but also during the normal heating operation even in a case where dew condensation occurs on the surfaces of the flat tubes 1 or the corrugated fins 2.
  • the amount of formed frost is relatively small, and hence the influence of the degradation of the defrosting performance is small. Further, the air guiding action is promoted as compared to Embodiment 1, and an effect of being capable of prolonging a time period until the defrosting operation is performed is more significant.
  • FIG. 21 is a sectional view taken along the line D-D of FIG. 17 .
  • the thickness of the center portion of the corrugated fin 2 in the airflow orthogonal direction is formed larger than those of other portions (both right and left end portions).
  • the thickness of the corrugated fin 2 is varied only at the windward-side end portion (front-side end portion) of the protruding portion 5 as described above is most efficient.
  • the thickness of the corrugated fin 2 may be entirely varied in the same manner in the airflow direction (front-and-back direction).
  • frost is formed on a part of the corrugated fin 2 on the leeward side (back side)
  • the defrosting performance can be enhanced.
  • the two first lug portions 7 are formed in the protruding portion 5 on the right and left sides to promote heat transfer.
  • the first lug portions 7 are oriented obliquely in the same direction with respect to the airflow direction (front-and-back direction).
  • the air guiding action is promoted as compared to Embodiment 1, thereby being capable of prolonging the time period until the defrosting operation is performed.
  • the flat tubes 1 are provided in two rows in the airflow direction (front-and-back direction).
  • the passage for water flowing through the part between the flat tube 1 on the windward side (front side) and the flat tube 1 on the leeward side (back side) is formed.
  • the thickness of the center portion of the corrugated fin 2 in the airflow orthogonal direction is formed larger than those of other portions (both right and left end portions), and hence, during the defrosting operation, the fin efficiency can be enhanced substantially equally to that in the case where the entire thickness of the fin is increased. Consequently, heat can sufficiently be transferred to the windward-side end portion (front-side end portion) of the protruding portion 5 and the first lug portions 7, thereby being capable of preventing the degradation of the defrosting performance. That is, the time period required for the defrosting can be prevented from being prolonged.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Geometry (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Other Air-Conditioning Systems (AREA)
EP16772077.0A 2015-03-30 2016-03-03 Échangeur de chaleur et climatiseur Active EP3279598B1 (fr)

Applications Claiming Priority (2)

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JP2015069429 2015-03-30
PCT/JP2016/056675 WO2016158193A1 (fr) 2015-03-30 2016-03-03 Échangeur de chaleur et climatiseur

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JPWO2016158193A1 (ja) 2017-04-27
JP6165360B2 (ja) 2017-07-19
WO2016158193A1 (fr) 2016-10-06
EP3279598B1 (fr) 2022-07-20
US20180100659A1 (en) 2018-04-12
CN107407534A (zh) 2017-11-28
EP3279598A4 (fr) 2019-01-02

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