WO2012098914A1 - Échangeur de chaleur et climatiseur - Google Patents

Échangeur de chaleur et climatiseur Download PDF

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Publication number
WO2012098914A1
WO2012098914A1 PCT/JP2012/000370 JP2012000370W WO2012098914A1 WO 2012098914 A1 WO2012098914 A1 WO 2012098914A1 JP 2012000370 W JP2012000370 W JP 2012000370W WO 2012098914 A1 WO2012098914 A1 WO 2012098914A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
flat
leeward
heat transfer
leeward side
Prior art date
Application number
PCT/JP2012/000370
Other languages
English (en)
Japanese (ja)
Inventor
正憲 神藤
好男 織谷
俊 吉岡
俊光 鎌田
Original Assignee
ダイキン工業株式会社
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 ダイキン工業株式会社 filed Critical ダイキン工業株式会社
Priority to BR112013018043A priority Critical patent/BR112013018043A2/pt
Priority to AU2012208120A priority patent/AU2012208120A1/en
Priority to KR1020137021756A priority patent/KR101313347B1/ko
Priority to CN201280005238.2A priority patent/CN103314269B/zh
Priority to EP12736904.9A priority patent/EP2667139A1/fr
Priority to US13/980,588 priority patent/US20130299153A1/en
Publication of WO2012098914A1 publication Critical patent/WO2012098914A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—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
    • F28F1/32—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
    • 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
    • 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
    • F28F1/325—Fins with openings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F17/00—Removing ice or water from heat-exchange apparatus
    • F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • 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
    • F28F2215/12—Fins with U-shaped slots for laterally inserting conduits

Definitions

  • the present invention relates to a heat exchanger that includes a flat tube and a plurality of fins, exchanges heat between fluid flowing through the flat tube and air, and an air conditioner including the heat exchanger.
  • heat exchangers having flat tubes and fins are known.
  • a plurality of flat tubes extending in the left-right direction are arranged one above the other at a predetermined interval, and plate-like fins are arranged at a predetermined interval from each other. They are arranged in the direction of extension.
  • a plurality of flat tubes extending in the left-right direction are arranged one above the other at a predetermined interval, and one corrugated fin is provided between adjacent flat tubes. It is provided one by one.
  • the air flowing while contacting the fins exchanges heat with the fluid flowing in the flat tube.
  • a louver for promoting heat transfer is formed on the fin of this type of heat exchanger.
  • the louver is formed by cutting and raising a part of the fin.
  • the refrigerant circuit of the air conditioner is provided with an outdoor heat exchanger that exchanges heat between the refrigerant and outdoor air.
  • the outdoor heat exchanger functions as an evaporator.
  • frost that is, ice
  • the outdoor heat exchanger falls below 0 ° C.
  • moisture in the air becomes frost (that is, ice) and adheres to the outdoor heat exchanger. Therefore, during the heating operation in a state where the outside air temperature is low, a defrosting operation for melting frost attached to the outdoor heat exchanger is performed, for example, every time a predetermined time elapses.
  • the high-temperature refrigerant is supplied to the outdoor heat exchanger, and the frost attached to the outdoor heat exchanger is heated by the refrigerant and melts. As a result, the frost adhering to the outdoor heat exchanger melts to become drain water and is discharged from the outdoor heat exchanger.
  • a heat exchanger in which flat tubes are lined up and down can be used as an outdoor heat exchanger of an air conditioner.
  • drain water tends to accumulate on the flat tube.
  • drain water enters and accumulates between the long and narrow cuts that are formed when the louvers are cut and raised. If the drain water stays in the vicinity of the fins in this manner, the transfer of heat from the refrigerant to the frost is hindered by the drain water, and there is a possibility that the time required for the frost to melt will be increased.
  • This invention is made
  • the objective is to shorten discharge
  • the first invention is arranged between a plurality of flat tubes (33), which are arranged one above the other so that the flat side faces each other, and in which a fluid passage (34) is formed, and between the adjacent flat tubes (33).
  • a plurality of fins (35, 36) that divide a plurality of ventilation paths (38) through which air flows, the plurality of fins (35, 36) extending from one of the adjacent flat tubes (33) to the other
  • a heat exchanger having side plate portions (42, 47) is an object.
  • the heat exchanger has a plurality of bulge portions (51, 52) that bulges toward the ventilation path (38) and extends in a direction intersecting the air passage direction in the plurality of heat transfer portions (37). , 53) are arranged in the air passing direction.
  • the heat exchanger (30) is provided with a plurality of flat tubes (33) and fins (35, 36). Between the flat tubes (33) arranged vertically, the heat transfer section (37) of the fins (35, 36) is arranged. Thereby, the ventilation path (38) is divided between the flat tubes (33). In the heat exchanger (30), heat is exchanged between the air flowing through the ventilation path (38) and the fluid flowing through the passage (34) in the flat tube (33).
  • a plurality of bulging sections (51, 52, 53) that bulge toward the ventilation path (38) are arranged in the ventilation direction of the ventilation path (38). .
  • the heat transfer performance of the heat transfer section (37) is increased by the plurality of bulge sections (51, 52, 53).
  • the bulging portions (51, 52, 53) of the heat transfer portion (37) of the present invention are not formed by cutting and raising the heat transfer portion (37) as in the conventional louver. That is, the swelled portion (51, 52, 53) of the present invention is not formed with a cut that accumulates drain water, so the drain water in the vicinity of the swelled portion (51, 52, 53) quickly To the leeward side. This drain water is discharged downward along the wall surface of the leeward side plate (42, 47).
  • the plurality of bulges (51, 52, 53) include an upwind bulge (51) formed on the windward side of the ventilation passage (38), A leeward bulge portion (53) formed on the leeward side of the ventilation path (38), and the heat transfer portion (37) includes the leeward bulge portion (51) and a lower flat tube (
  • the height of the flat portion (51a) formed between the flat portion (53a) formed between the leeward bulge portion (53) and the lower flat tube (33) is It is characterized by being larger than the height.
  • an upwind side bulge portion (51) near the leeward side and a leeward side bulge portion (53) near the leeward side are formed.
  • the leeward bulge section (51) is more in the leeward bulge section (53 )
  • the amount of frost increases. Therefore, during defrosting, the amount of drain water generated at the leeward bulge portion (51) is greater than the amount of drain water generated at the leeward bulge portion (53).
  • the height of the flat part (51a) formed on the lower side of the leeward bulge part (51) is set to the flat part (51a) formed on the lower side of the leeward bulge part (53). It is larger than 53a). For this reason, during defrosting, the drain water produced in a large amount in the vicinity of the windward bulge portion (51) flows down rapidly along the lower flat portion (51a).
  • a flat portion (51a, 52a) formed between the plurality of bulging portions (51, 52, 53) and the lower flat tube (33). , 53a) is characterized in that the height decreases from the leeward side toward the leeward side.
  • the height of the flat part (51a, 52a, 53a) formed in the lower side of a some bulging part (51,52,53) becomes small as it goes to the leeward from the windward side. . That is, between the adjacent heat transfer parts (37), the height of the gap formed along the flat part (51a, 52a, 53a) becomes smaller on the leeward side. For this reason, during defrosting, the drain water generated in the vicinity of the bulge portion (51) on the windward side is drawn to the leeward side of the heat transfer portion (37) by capillary action.
  • the bulging portion (51, 52, 53) has a lower end of the bulging portion (51, 52, 53). It is inclined with respect to the vertical direction so as to be located closer to the lee side than the upper end of (51, 52, 53).
  • the bulging portion (51, 52, 53) is inclined with respect to the vertical direction, and the lower end of the bulging portion (51, 52, 53) is located leeward than the upper end. Yes.
  • drain water generated in the vicinity of the bulging part (51, 52, 53) during defrosting flows down toward the leeward side as guided by the bulging part (51, 52, 53). Go.
  • At least one bulge portion (51,52) of the plurality of bulge portions (51,52,53), and the bulge portion The height of the flat part (51a, 51b) formed between the flat pipe (33) on the lower side of (51, 52) decreases from the leeward side toward the leeward side. .
  • the height of the flat part (51a, 52a) formed in the lower side of at least 1 bulge part (51,52) among several bulge parts (51,52,53) is high. It becomes smaller as it goes from the leeward side to the leeward side. That is, between the adjacent heat transfer parts (37), the height of the gap formed along the flat part (51a, 52a, 53a) gradually decreases toward the leeward side. For this reason, during defrosting, drain water generated in the vicinity of the bulging portion (51, 52) is drawn to the leeward side of the heat transfer portion (37) by capillary action.
  • the plurality of fins (36) have a plurality of notches (45) for inserting the flat tube (33) on the windward side.
  • the plate is formed in a plate shape, arranged at a predetermined interval in the extending direction of the flat tube (33), and sandwiches the flat tube (33) at the periphery of the notch (45).
  • the part between the notches (45) that are vertically adjacent constitutes the heat transfer part (37), and extends up and down continuously with the leeward side end of the heat transfer part (37).
  • the portion constitutes the leeward side plate portion (47).
  • the leeward side plate portion (47) is formed on the leeward side of the plurality of heat transfer portions (37) arranged vertically so as to be continuous with the plurality of heat transfer portions. Thereby, an integral vertically long fin (36) is formed. Since the flat tube (33) is sandwiched around the periphery of the notch (45) of the fin (36), a plurality of ventilations are provided between the adjacent flat tube (33) and each heat transfer unit (37).
  • the road (38) is demarcated.
  • the leeward side plate portion (47) is formed with a rib (57) extending along the leeward side end portions of the plurality of heat transfer portions (37). It is characterized by that.
  • each heat transfer section (37) flows to the leeward side plate section (47) during defrosting, the drain water is guided downward by the rib (57). run down.
  • the fin (36) is formed with a cut-and-raised portion (61, 62) cut and raised toward the ventilation path (38).
  • the cut and raised surfaces (61a, 62a) of the portions (61a, 62a) are inclined with respect to the horizontal plane.
  • cut-and-raised portions (61, 62) are formed in the fin (36).
  • a predetermined interval can be secured between the two adjacent fins (36) by bringing the tips of the cut and raised portions (61, 62) into contact with the adjacent fins (36).
  • drain water generated during defrosting may be held on the upper surface of the cut-and-raised part (61, 62).
  • the cut-and-raised portion (61, 62) of the present invention is inclined with respect to the horizontal plane, the drain water on the upper surface of the cut-and-raised portion (61, 62) flows down rapidly.
  • a ninth invention is directed to the air conditioner (10), and includes a refrigerant circuit (20) provided with the heat exchanger (30) according to any one of the first to eighth inventions, and the refrigerant circuit In (20), the refrigerant is circulated to perform the refrigeration cycle.
  • the heat exchanger (30) of any one of the first to eighth inventions is connected to the refrigerant circuit (20).
  • the refrigerant circulating in the refrigerant circuit (20) flows through the passage (34) of the flat tube (33) and exchanges heat with the air flowing through the ventilation path (39).
  • a part of the heat transfer section (37) is bulged toward the air passage (38) so that the plurality of bulge sections (51, 52, 53) are formed. Forming. For this reason, the heat transfer of air and fluid can be promoted by the bulging portion (51, 52, 53).
  • the bulging part (51, 52, 53) of this invention is not the shape which cuts and raises a heat transfer part like the louver of a prior art example. For this reason, in the bulging part (51, 52, 53), the drain water generated by melting of the frost at the time of defrosting is not easily collected, so that the drain water can be quickly flowed to the leeward side. As a result, the time required for defrosting can be shortened.
  • the height of the lower flat portion (51a) on the leeward bulge portion (51) is larger than the height of the lower flat portion (53a) on the leeward bulge portion (53). is doing.
  • the amount of frost formation increases, and drain water generated during defrosting also increases.
  • a gap formed along the flat portion (51a) is sufficiently secured below the upwind bulge portion (51), a large amount of drain water generated in the upwind bulge portion (51). Can be discharged quickly.
  • the drain water accumulated on the upper surface of the flat tube (33) on the lower side is drawn into the leeward side using the capillary phenomenon. Can do.
  • the bulging portion (51, 52, 53) is inclined so that the lower end of the bulging portion (51, 52, 53) is located leeward than the upper end. For this reason, the water melt
  • the flat tube (33) is formed by gradually reducing the height of the flat portion (51a, 52a) below the at least one bulging portion (51, 52) toward the leeward side.
  • the drain water collected on the upper surface of the can be drawn to the leeward side using capillary action.
  • the leeward side edge part of the heat-transfer part (37) arranged up and down is connected by the leeward side board part (47), and the rib (57) is formed in this leeward side board part (47). .
  • drain water that has flowed from the heat transfer section (37) to the leeward side plate section (47) is collected on the surface of the rib (57), and the drain water is guided downward through the rib (57). Can do.
  • the cut-raised portion (61, 62) can be used as a spacer between the adjacent fins (36). Moreover, it can also avoid that drain water accumulates on the upper side of a horizontal surface by inclining the raised surfaces (61a, 62a) of the raised portions (61, 62) with respect to the horizontal surface.
  • FIG. 1 is a refrigerant circuit diagram illustrating a schematic configuration of an air conditioner including the heat exchanger according to the first embodiment.
  • FIG. 2 is a schematic perspective view of the heat exchanger according to the first embodiment.
  • FIG. 3 is a partial cross-sectional view illustrating the front of the heat exchanger according to the first embodiment.
  • FIG. 4 is a cross-sectional view of the heat exchanger showing a part of the IV-IV cross section of FIG.
  • FIG. 5 is a cross-sectional view of the fin showing the VV cross section of FIG.
  • FIG. 6 is a perspective view of the fin according to the first embodiment.
  • FIG. 7 is a schematic perspective view of the heat exchanger according to the second embodiment.
  • FIG. 1 is a refrigerant circuit diagram illustrating a schematic configuration of an air conditioner including the heat exchanger according to the first embodiment.
  • FIG. 2 is a schematic perspective view of the heat exchanger according to the first embodiment.
  • FIG. 3 is a partial cross-sectional view
  • FIG. 8 is a partial cross-sectional view illustrating the front of the heat exchanger according to the second embodiment.
  • FIG. 9 is a cross-sectional view of the heat exchanger showing a part of the IX-IX cross section of FIG.
  • FIG. 10 is a cross-sectional view of the fin showing the XX cross section of FIG.
  • Embodiment 1 of the Invention A first embodiment of the present invention will be described.
  • the heat exchanger (30) of Embodiment 1 comprises the outdoor heat exchanger (23) of the air conditioner (10) mentioned later.
  • the air conditioner (10) includes an outdoor unit (11) and an indoor unit (12).
  • the outdoor unit (11) and the indoor unit (12) are connected to each other via a liquid side connecting pipe (13) and a gas side connecting pipe (14).
  • the refrigerant circuit (20) is formed by the outdoor unit (11), the indoor unit (12), the liquid side communication pipe (13), and the gas side communication pipe (14).
  • the refrigerant circuit (20) is provided with a compressor (21), a four-way switching valve (22), an outdoor heat exchanger (23), an expansion valve (24), and an indoor heat exchanger (25). ing.
  • the compressor (21), the four-way switching valve (22), the outdoor heat exchanger (23), and the expansion valve (24) are accommodated in the outdoor unit (11).
  • the outdoor unit (11) is provided with an outdoor fan (15) for supplying outdoor air to the outdoor heat exchanger (23).
  • the indoor heat exchanger (25) is accommodated in the indoor unit (12).
  • the indoor unit (12) is provided with an indoor fan (16) for supplying room air to the indoor heat exchanger (25).
  • the refrigerant circuit (20) is a closed circuit filled with refrigerant.
  • the compressor (21) has its discharge side connected to the first port of the four-way switching valve (22) and its suction side connected to the second port of the four-way switching valve (22). Yes.
  • the outdoor heat exchanger (23), the expansion valve (24), and the indoor heat exchanger are sequentially arranged from the third port to the fourth port of the four-way switching valve (22). (25) and are arranged.
  • the compressor (21) is a scroll type or rotary type hermetic compressor (21).
  • the four-way switching valve (22) includes a first state (state indicated by a solid line in FIG. 1) in which the first port communicates with the third port and the second port communicates with the fourth port; The port is switched to a second state (state indicated by a broken line in FIG. 1) in which the port communicates with the fourth port and the second port communicates with the third port.
  • the expansion valve (24) is a so-called electronic expansion valve (24).
  • the outdoor heat exchanger (23) exchanges heat between the outdoor air and the refrigerant.
  • the outdoor heat exchanger (23) is configured by the heat exchanger (30) of the present embodiment.
  • the indoor heat exchanger (25) exchanges heat between the indoor air and the refrigerant.
  • the indoor heat exchanger (25) is constituted by a so-called cross fin type fin-and-tube heat exchanger provided with a heat transfer tube which is a circular tube.
  • the air conditioner (10) performs a cooling operation.
  • the four-way switching valve (22) is set to the first state.
  • the outdoor fan (15) and the indoor fan (16) are operated.
  • Refrigeration cycle is performed in the refrigerant circuit (20). Specifically, the refrigerant discharged from the compressor (21) flows into the outdoor heat exchanger (23) through the four-way switching valve (22), dissipates heat to the outdoor air, and is condensed. The refrigerant flowing out of the outdoor heat exchanger (23) expands when passing through the expansion valve (24), then flows into the indoor heat exchanger (25), absorbs heat from the indoor air, and evaporates. The refrigerant that has flowed out of the indoor heat exchanger (25) passes through the four-way switching valve (22) and then is sucked into the compressor (21) and compressed. The indoor unit (12) supplies the air cooled in the indoor heat exchanger (25) to the room.
  • the air conditioner (10) performs heating operation.
  • the four-way selector valve (22) is set to the second state.
  • the outdoor fan (15) and the indoor fan (16) are operated.
  • Refrigeration cycle is performed in the refrigerant circuit (20). Specifically, the refrigerant discharged from the compressor (21) flows into the indoor heat exchanger (25) through the four-way switching valve (22), dissipates heat to the indoor air, and condenses. The refrigerant flowing out of the indoor heat exchanger (25) expands when passing through the expansion valve (24), then flows into the outdoor heat exchanger (23), absorbs heat from the outdoor air, and evaporates. The refrigerant that has flowed out of the outdoor heat exchanger (23) passes through the four-way switching valve (22) and then is sucked into the compressor (21) and compressed. The indoor unit (12) supplies the air heated in the indoor heat exchanger (25) to the room.
  • the outdoor heat exchanger (23) functions as an evaporator during the heating operation.
  • the evaporation temperature of the refrigerant in the outdoor heat exchanger (23) may be lower than 0 ° C.
  • the moisture in the outdoor air becomes frost and the outdoor heat exchanger (23 ). Therefore, the air conditioner (10) performs the defrosting operation every time the duration time of the heating operation reaches a predetermined value (for example, several tens of minutes).
  • the four-way switching valve (22) When starting the defrosting operation, the four-way switching valve (22) is switched from the second state to the first state, and the outdoor fan (15) and the indoor fan (16) are stopped.
  • the refrigerant circuit (20) during the defrosting operation the high-temperature refrigerant discharged from the compressor (21) is supplied to the outdoor heat exchanger (23).
  • the frost adhering to the surface In the outdoor heat exchanger (23), the frost adhering to the surface is heated and melted by the refrigerant.
  • the refrigerant that has radiated heat in the outdoor heat exchanger (23) sequentially passes through the expansion valve (24) and the indoor heat exchanger (25), and is then sucked into the compressor (21) and compressed.
  • the heating operation is resumed. That is, the four-way switching valve (22) is switched from the first state to the second state, and the operation of the outdoor fan (15) and the indoor fan (16) is resumed.
  • the heat exchanger (30) of the present embodiment includes one first header collecting pipe (31), one second header collecting pipe (32), and many flat tubes. (33) and a large number of fins (35).
  • the first header collecting pipe (31), the second header collecting pipe (32), the flat pipe (33), and the fin (35) are all made of an aluminum alloy and are joined to each other by brazing. .
  • the first header collecting pipe (31) and the second header collecting pipe (32) are both formed in an elongated hollow cylindrical shape whose both ends are closed.
  • the first header collecting pipe (31) is erected at the left end of the heat exchanger (30)
  • the second header collecting pipe (32) is erected at the right end of the heat exchanger (30). That is, the first header collecting pipe (31) and the second header collecting pipe (32) are installed in such a posture that their respective axial directions are in the vertical direction.
  • the flat tube (33) is a heat transfer tube whose cross-sectional shape is a flat oval or a rounded rectangle.
  • the plurality of flat tubes (33) are arranged in a posture in which the extending direction is the left-right direction and the flat side surfaces face each other.
  • the plurality of flat tubes (33) are arranged side by side at regular intervals.
  • Each flat tube (33) has one end inserted into the first header collecting tube (31) and the other end inserted into the second header collecting tube (32).
  • each flat tube (33) has a plurality of fluid passages (34).
  • Each fluid passage (34) extends in the extending direction of the flat tube (33).
  • the plurality of fluid passages (34) are arranged in a line in the width direction orthogonal to the extending direction of the flat tube (33).
  • One end of each of the plurality of fluid passages (34) formed in each flat pipe (33) communicates with the internal space of the first header collecting pipe (31), and the other end of each of the plurality of fluid passages (34) is the second header collecting pipe (32). ).
  • the refrigerant supplied to the heat exchanger (30) exchanges heat with air while flowing through the fluid passage (34) of the flat tube (33).
  • the fins (35) are corrugated fins meandering up and down, and are arranged between flat tubes (33) adjacent to each other in the vertical direction. As will be described in detail later, the fin (35) has a plurality of heat transfer portions (37) and a plurality of intermediate plate portions (41). In each fin (35), the intermediate plate portion (41) is joined to the flat tube (33) by brazing.
  • the fin (35) is a corrugated fin formed by bending a metal plate having a certain width, and has a corrugated shape that meanders up and down.
  • heat transfer portions (37) and intermediate plate portions (41) are alternately formed along the extending direction of the flat tube (33). That is, the fin (35) is provided with a plurality of heat transfer portions (37) arranged between adjacent flat tubes (33) and arranged in the extending direction of the flat tubes (33).
  • the fin (35) has a protruding plate (42) formed on the leeward side.
  • the heat transfer part (37) is a plate-like part extending from one to the other of the flat tubes (33) adjacent to each other in the vertical direction.
  • the heat transfer part (37) constitutes a side wall of the ventilation path (38) partitioned between the adjacent flat tubes (33).
  • the windward end is the leading edge (39).
  • the intermediate plate portion (41) is a plate-like portion along the flat side surface of the flat tube (33), and is continuous with the upper ends or lower ends of the heat transfer portions (37) adjacent to the left and right.
  • the angle formed by the heat transfer section (37) and the intermediate plate section (41) is substantially a right angle.
  • the protruding plate portion (42) is a plate-like portion formed continuously at the leeward end of each heat transfer portion (37).
  • the projecting plate portion (42) is formed in an elongated plate shape extending vertically, and projects further to the leeward side than the flat tube (33).
  • the upper end of the protruding plate part (42) protrudes above the upper end of the heat transfer part (37), and the lower end protrudes below the lower end of the heat transfer part (37).
  • the protruding plate portions (42) of the fins (35) that are vertically adjacent to each other across the flat tube (33) are in contact with each other.
  • the protruding plate portion (42) constitutes a leeward plate portion that forms a drain water drainage path by being connected vertically.
  • a plurality of waffle parts (51, 52, 53) are formed on the heat transfer part (37) and the protruding plate part (42) of the fin (35).
  • the waffle portion (51, 52, 53) constitutes a bulging portion that is vertically formed vertically.
  • the waffle portion (51, 52, 53) is formed in a mountain shape in which the ridge line intersects with the air ventilation direction by bulging toward the ventilation path (38) side.
  • the waffle part (51, 52, 53) is formed by plastically deforming a part of the heat transfer part (37) by press working or the like.
  • Each waffle portion (51, 52, 53) extends in a direction inclined obliquely with respect to the vertical direction so that its lower end portion is located closer to the lee than the upper end portion.
  • Each waffle part (51, 52, 53) has a pair of vertically long trapezoidal surfaces (54, 54) and a pair of flat triangular surfaces (55, 55).
  • the pair of trapezoidal surfaces (54, 54) are adjacent to each other in the ventilation direction so as to form a mountain fold (56) forming a ridgeline between them.
  • the pair of triangular surfaces (55, 55) are formed up and down across the mountain fold (56).
  • a plurality of waffle sections (51, 52, 53) are formed side by side from the leeward side to the leeward side.
  • These waffle parts (51, 52, 53) are formed on one leeward waffle part (51) formed on the windward side of the heat transfer part (37) and on the leeward side of the heat transfer part (37). It comprises two leeward waffle parts (53, 53) and one intermediate waffle part (52) formed between the leeward waffle part (51) and the leeward waffle part (53).
  • the windward waffle portion (51) constitutes the windward bulge portion formed on the most windward side among the plurality of waffle portions (51, 52, 53).
  • the leeward waffle portion (53, 53) constitutes the leeward bulge portion formed on the most leeward side among the plurality of waffle portions (51, 52, 53).
  • the upper end of the leeward waffle part (51) is lower than the upper end of the leeward waffle part (53). Further, the upper end of the intermediate waffle portion (52) and the upper end of the leeward waffle portion (53) are substantially at the same height.
  • the upper end of the windward waffle part (51), the upper end of the intermediate waffle part (52), and the upper end of the leeward waffle part (53) are substantially parallel to the flat surface of the upper flat tube (33).
  • the lower end of the leeward waffle part (51) is higher than the lower end of the leeward waffle part (53).
  • the lower end of the windward waffle portion (51) is inclined obliquely so that the leeward side is lower than the windward side.
  • the lower end of the intermediate waffle portion (52) is also inclined obliquely so that the leeward side is lower than the leeward side.
  • the lower end of the leeward waffle portion (53) is substantially parallel to the flat surface of the flat tube (33).
  • a water guiding rib (57) is formed downstream of the waffle portion (51, 52, 53). Specifically, one water guiding rib (57) is formed on each protruding plate (42). The water guiding rib (57) extends vertically along the leeward end of the protruding plate (42). As shown in FIG. 5, the water guiding rib (57) has a protrusion (57a) formed on one surface of the protruding plate portion (42) and a groove (57b) formed on the other surface.
  • each of the protruding plate portions (42) adjacent to each other in the vertical direction and the protruding plate portions (42) adjacent to each other in the extending direction of the flat tube (33) are respectively formed with ridges (57a) on the side surfaces on the same side.
  • the water guiding ribs (57) adjacent to each other in the vertical direction are arranged so as to substantially coincide with each other in the vertical direction.
  • the upper end of the water guiding rib (57) is slightly lower than the upper end of the protruding plate portion (42), and the lower end of the water guiding rib (57) is slightly lower than the lower end of the protruding plate portion (42). High position.
  • region where the waffle part (51,52,53) and the rib for water conveyance (57) are not formed among the side surfaces of the heat-transfer part (37) is a flat surface.
  • a flat part (51a, 51b, 51c) is formed between the lower end of each waffle part (51, 52, 53) and the flat tube (33) below the waffle part (51, 52, 53). Has been.
  • a first flat part (51a) is formed between the lower end of the windward waffle part (51) and the lower flat pipe (33), and the intermediate waffle part ( 52) and a lower flat tube (33), a second flat portion (52a) is formed between the lower end of the leeward waffle portion (53) and the lower flat tube (33).
  • a third flat portion (53a) is formed therebetween.
  • the height of the first flat part (51a) decreases from the windward side toward the leeward side.
  • the height of the second flat part (52a) also decreases from the leeward side toward the leeward side.
  • the lower end of two bulges (51,52) of the four bulges (51,52,53,53) and the bottom of these bulges (51,52) The height of the two flat portions (51a, 52a) between the flat tube (33) on the side decreases from the leeward side toward the leeward side. Furthermore, in the heat transfer part (37), the height of the first flat part (51a) is larger than the height of the third flat part (53a). In addition, the height of the lower flat part of only one of the four bulging parts (51, 52, 53, 53) may be reduced from the leeward side toward the leeward side. You may make the height of the above flat part small as it goes to the leeward side from the windward side, respectively.
  • the heat exchanger (30) of the present embodiment constitutes the outdoor heat exchanger (23) of the air conditioner (10).
  • the air conditioner (10) performs a heating operation. However, in an operation state where the evaporation temperature of the refrigerant in the outdoor heat exchanger (23) is lower than 0 ° C., moisture in the outdoor air becomes frost and the outdoor heat exchanger (23 ). For this reason, the air conditioner (10) performs a defrosting operation for melting frost attached to the outdoor heat exchanger (23). During the defrosting operation, drain water is generated by melting of the frost.
  • the height of the first flat part (51a) below the windward waffle part (51) is set to the second flat part (52a) or the third flat part.
  • the frost adhering to the heat exchanger (30) is warmed by the refrigerant and gradually melts.
  • the amount of frost formation on the surface of the windward waffle section (51) increases, the amount of water (drain water) that melts in this region also increases.
  • the height of the first flat portion (51a) on the lower side of the windward waffle portion (51) is larger than the heights of the other flat portions (52a, 53a). For this reason, the space
  • the time required for melting the frost on the surface of the windward waffle part (51) can be shortened, and the duration of the defrosting operation is also shortened.
  • the heat exchanger (30) immediately after the end of the defrosting operation there is no frost but drain water is present.
  • the drain water generated during the defrosting operation flows to the leeward side.
  • the height of the flat portion (51a, 52a, 53a) is reduced toward the leeward side, and particularly the height of the third flat portion (53a) on the leeward side is reduced. Yes.
  • the drain water collected on the upper surface of the flat tube (33) is drawn to the leeward side by capillary action. That is, during the defrosting operation, the outdoor fan (15) is stopped, and the drain water moves to the leeward side even though the upper surface of the flat tube (33) is substantially horizontal.
  • the plurality of waffle portions (51) are inclined with respect to the vertical direction so that the lower ends of the plurality of waffle portions (51) are located on the leeward side of the upper ends of the waffles. For this reason, the drain water melt
  • the drain water that has moved to the leeward side reaches the ribs (57) for the water guide of the protruding plate (42).
  • the drain water flows down through the surface of the ridge (57a) of the rib for guiding water (57) or the inside of the groove (57b) by gravity.
  • the drain water that has flowed down the protruding plate portion (42) is guided by the water guiding rib (57) of the lower protruding plate portion (42) and further flows downward. Thereby, drain water flows down to the fin (35) located in the lowest side, and is sent to drainage paths, such as a drain pan, after that.
  • the several waffle part (51,52,53) is formed in the heat-transfer part (37).
  • the waffle part (51, 52, 53) has a shape in which a part of the heat transfer part (37) is bulged toward the air passage (38).
  • a heat transfer part like a conventional louver. (37) is not configured to cut.
  • the height of the first flat portion (51a) on the lower side of the windward waffle portion (51) is set higher than that of the third flat portion (53a) on the lower side of the leeward waffle portion (53).
  • each waffle part (51, 52, 53) As shown in FIG. 4, drain water melted on the surface of each waffle part (51, 52, 53) can be promptly guided to the leeward side. it can.
  • the drain water discharge time during the defrosting operation can be shortened, the time required for frost melting can also be shortened.
  • the execution time of the defrosting operation can be shortened, the execution time of the heating operation can be extended accordingly.
  • Embodiment 2 of the Invention A second embodiment of the present invention will be described. Similarly to the heat exchanger (30) of the first embodiment, the heat exchanger (30) of the second embodiment constitutes an outdoor heat exchanger (23) of the air conditioner (10). Hereinafter, the heat exchanger (30) of the present embodiment will be described with reference to FIGS. 7 to 10 as appropriate.
  • the heat exchanger (30) of the present embodiment includes one first header collecting pipe (31), one second header collecting pipe (32), and a number of flat tubes. (33) and a large number of fins (36).
  • the first header collecting pipe (31), the second header collecting pipe (32), the flat pipe (33), and the fin (36) are all made of an aluminum alloy and are joined to each other by brazing. .
  • the configuration and arrangement of the first header collecting pipe (31), the second header collecting pipe (32), and the flat tube (33) are the same as those of the heat exchanger (30) of the first embodiment. That is, the first header collecting pipe (31) and the second header collecting pipe (32) are both formed in a vertically long cylindrical shape, one at the left end of the heat exchanger (30) and the other at the heat exchanger (30). 30) are arranged at the right end of each.
  • the flat tube (33) is a heat transfer tube having a flat cross-sectional shape, and is arranged side by side in a posture in which the flat side surfaces face each other. Each flat tube (33) has a plurality of fluid passages (34). One end of each of the flat tubes (33) arranged in the vertical direction is inserted into the first header collecting pipe (31), and the other end is inserted into the second header collecting pipe (32).
  • the fins (36) are plate-shaped fins, and are arranged at regular intervals in the extending direction of the flat tube (33). That is, the fin (36) is disposed so as to be substantially orthogonal to the extending direction of the flat tube (33).
  • the fin (36) is a vertically long plate-like fin formed by pressing a metal plate.
  • the fin (36) has a number of elongated notches (45) extending in the width direction of the fin (36) from the front edge (39) of the fin (36).
  • a large number of notches (45) are formed at regular intervals in the longitudinal direction of the fin (36).
  • the portion closer to the lee of the notch (45) constitutes the tube insertion portion (46).
  • the tube insertion portion (46) has a vertical width substantially equal to the thickness of the flat tube (33) and a length substantially equal to the width of the flat tube (33).
  • the flat tube (33) is inserted into the tube insertion portion (46) of the fin (36) and joined to the peripheral portion of the tube insertion portion (46) by brazing.
  • the fin (36) has a plurality of heat transfer portions (37) adjacent to each other up and down across the flat tube (33), and one leeward continuous to the leeward end of each heat transfer portion (37).
  • a side plate portion (47) is provided.
  • the heat transfer section (37) of the fin (36) is disposed between the flat tubes (33) arranged in the vertical direction, and the leeward side plate portion (47) is disposed in the flat tube (33 ) Protrudes further to the leeward side.
  • a plurality of waffle portions (51, 52, 53) are formed in the heat transfer portion (37) and the leeward side plate portion (47) of the fin (35) in the same manner as in the first embodiment. ing. That is, the waffle portion (51, 52, 53) bulges toward the ventilation path (38) and constitutes a bulge portion that is vertically formed vertically.
  • the waffle part (51, 52, 53) is formed by plastically deforming a part of the heat transfer part (37) by press working or the like.
  • Each waffle portion (51, 52, 53) extends in a direction inclined obliquely with respect to the vertical direction so that its lower end portion is located closer to the lee than the upper end portion.
  • Each waffle portion (51, 52, 53) has a pair of trapezoidal surfaces (54, 54), a pair of triangular surfaces (55, 55), and a mountain fold portion (56), as in the first embodiment. Yes.
  • the heat transfer part (37) has one windward waffle part (51), one intermediate waffle part (52), and two leeward waffle parts (53, 53). And are formed. Of the two leeward waffle portions (53, 53), the leeward waffle portion (53) is formed across the heat transfer portion (37) and the leeward side plate portion (47).
  • the flat portion (51a, 51b, between the lower end of each waffle portion (51, 52, 53) and the flat tube (33) below the waffle portion (51, 52, 53). 51c) is formed.
  • a first flat part (51a) is formed between the lower end of the windward waffle part (51) and the lower flat pipe (33), and the intermediate waffle part ( 52) and a lower flat tube (33), a second flat portion (52a) is formed between the lower end of the leeward waffle portion (53) and the lower flat tube (33).
  • a third flat portion (53a) is formed therebetween.
  • the height of the first flat part (51a) decreases from the windward side toward the leeward side.
  • the height of the second flat part (52a) also decreases from the leeward side toward the leeward side. That is, in this embodiment, the lower end of two bulges (51,52) of the four bulges (51,52,53,53) and the bottom of these bulges (51,52)
  • the height of the two flat portions (51a, 52a) between the flat tube (33) on the side decreases from the leeward side toward the leeward side.
  • the height of the first flat part (51a) is larger than the height of the third flat part (53a).
  • the height of the lower flat part of only one of the four bulging parts may be reduced from the leeward side toward the leeward side. You may make the height of the above flat part small as it goes to the leeward side from the windward side, respectively.
  • the leeward side plate portion (47) of the fin (36) extends in the vertical direction so as to form a drain water drainage path.
  • One riving rib (57) is formed on the leeward side plate portion (47).
  • the water guiding rib (57) is a long and narrow groove extending vertically along the leeward end of the leeward plate (47), and is formed from the upper end to the lower end of the leeward plate (47). .
  • the water guiding rib (57) has a ridge (57a) formed on one surface of the leeward side plate portion (47) and a groove (57b) formed on the other surface.
  • a ridge (57a) is formed on the side surface on the same side.
  • the fin (36) is formed with tabs (61, 62) for maintaining an interval between adjacent fins (36).
  • Each tab (61, 62) is a rectangular piece formed by cutting and raising a part of the fin (36).
  • an upwind tab (61) is formed at the upwind end of each heat transfer section (37).
  • the windward tab (61) is formed by raising a part of the heat transfer section (37) obliquely upward. That is, the cut-and-raised surface (61a) of the windward tab (61) is inclined obliquely with respect to the horizontal plane.
  • leeward side tabs (62) are formed in the leeward portions of the respective flat tubes (33).
  • the leeward side tab (62) is formed by raising a part of the leeward side plate portion (47) to the upwind side. That is, the cut-and-raised surface (62a) of the leeward tab (62) is orthogonal to the horizontal plane.
  • each tab (61, 62) is set to a height that allows contact with the adjacent fin (36). That is, each tab (61, 62) functions as a spacer for ensuring a predetermined interval between adjacent fins (36). In addition, after each fin (36) is brazed with the flat tube (33), each tab (61, 62) may be folded back to the fin (36) side and returned to the original position.
  • Embodiment 2 In the heat exchanger (30) of the second embodiment, the same effect as in the first embodiment can be obtained. That is, also in Embodiment 2, heat transfer performance can be improved by forming a plurality of waffle portions (51, 52, 53) in the heat transfer portion (37). Since this waffle part (51, 52, 53) does not require a cut like the conventional louver, drain water does not accumulate near the waffle part (51, 52, 53). In addition, by forming the first flat portion (51a) below the windward waffle portion (51), drain water generated on the surface of the windward waffle portion (51) can be quickly discharged downward.
  • drain water collected on the upper side of the flat tube (33) can be drawn into the leeward side from the gap on the third flat portion (53a) side using the capillary phenomenon. Furthermore, drain water generated on the surface of each waffle part (51, 52, 53) can be guided to the leeward side along the inclination direction of each waffle part (51, 52, 53).
  • the drain water that has moved to the leeward side plate portion (47) is collected on the surface of the ridge (57a) of the water guiding rib (57) and the inside of the groove (57b), and the water guiding rib ( 57) It flows down along the line.
  • drain water accumulated on the leeward side of the fin (36) can be quickly discharged to a drain pan or the like.
  • the cut-and-raised surfaces (61a, 62a) of the tabs (61, 62) of the second embodiment are inclined with respect to the horizontal plane. For this reason, it can avoid that the drain water produced
  • the present invention is useful for a heat exchanger that includes a flat tube and a plurality of fins, exchanges heat between the fluid flowing through the flat tube and air, and an air conditioner that includes this heat exchanger. is there.

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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)
  • Other Air-Conditioning Systems (AREA)

Abstract

Une pluralité de parties saillantes (51, 52, 53), faisant saillie vers un côté conduit d'air (38) et s'étendant dans une direction croisant la direction de passage d'air, sont agencées dans la direction de passage d'air dans une pluralité d'unités de conduction de chaleur (37).
PCT/JP2012/000370 2011-01-21 2012-01-23 Échangeur de chaleur et climatiseur WO2012098914A1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
BR112013018043A BR112013018043A2 (pt) 2011-01-21 2012-01-23 trocador de calor e ar condicionado
AU2012208120A AU2012208120A1 (en) 2011-01-21 2012-01-23 Heat exchanger and air conditioner
KR1020137021756A KR101313347B1 (ko) 2011-01-21 2012-01-23 열교환기 및 공기 조화기
CN201280005238.2A CN103314269B (zh) 2011-01-21 2012-01-23 热交换器及空调机
EP12736904.9A EP2667139A1 (fr) 2011-01-21 2012-01-23 Échangeur de chaleur et climatiseur
US13/980,588 US20130299153A1 (en) 2011-01-21 2012-01-23 Heat exchanger and air conditioner

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2011-011195 2011-01-21
JP2011011195 2011-01-21

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WO2012098914A1 true WO2012098914A1 (fr) 2012-07-26

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US (1) US20130299153A1 (fr)
EP (1) EP2667139A1 (fr)
JP (1) JP5177306B2 (fr)
KR (1) KR101313347B1 (fr)
CN (1) CN103314269B (fr)
AU (1) AU2012208120A1 (fr)
BR (1) BR112013018043A2 (fr)
WO (1) WO2012098914A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014030844A (ja) * 2012-08-06 2014-02-20 Hidaka Seiki Kk 扁平チューブ用フィンおよび扁平チューブ用フィンの製造金型と金属帯状体の送り装置
EP2840341A1 (fr) * 2013-07-30 2015-02-25 Samsung Electronics Co., Ltd Échangeur de chaleur
US20170030662A1 (en) * 2015-07-31 2017-02-02 Lg Electronics Inc. Heat exchanger

Families Citing this family (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012032111A (ja) * 2010-08-02 2012-02-16 Fuji Electric Co Ltd 熱交換器
EP2869015B1 (fr) * 2013-11-05 2017-09-20 MAHLE International GmbH Méthode d'utilisation d'ailettes ondulées asymétriques avec des persiennes
WO2015108289A1 (fr) * 2014-01-15 2015-07-23 삼성전자주식회사 Échangeur de chaleur et climatiseur l'utilisant
KR102227419B1 (ko) * 2014-01-15 2021-03-15 삼성전자주식회사 열교환기 및 이를 갖는 공기조화기
KR102188114B1 (ko) * 2014-01-28 2020-12-07 삼성전자주식회사 열교환기
CN103925742B (zh) * 2014-04-18 2016-06-29 丹佛斯微通道换热器（嘉兴）有限公司 换热器及其制造方法、换热模块、换热装置和热源单元
AU2015396674B2 (en) * 2015-05-29 2019-05-09 Mitsubishi Electric Corporation Heat exchanger
US10627175B2 (en) * 2015-05-29 2020-04-21 Mitsubishi Electric Corporation Heat exchanger and refrigeration cycle apparatus
US11041676B2 (en) * 2015-07-31 2021-06-22 Lg Electronics Inc. Heat exchanger
CN106705270B (zh) * 2015-11-12 2020-07-17 浙江盾安人工环境股份有限公司 换热器
CN205352165U (zh) * 2015-12-16 2016-06-29 杭州三花微通道换热器有限公司 换热器芯体和具有它的换热器
WO2018003123A1 (fr) * 2016-07-01 2018-01-04 三菱電機株式会社 Échangeur de chaleur et appareil à cycle frigorifique
CN106370045B (zh) * 2016-08-30 2019-07-23 杭州三花微通道换热器有限公司 翅片和具有该翅片的换热器
JP6294537B1 (ja) 2017-01-20 2018-03-14 三菱アルミニウム株式会社 ろう付け用混合組成物塗料
JP6692495B2 (ja) * 2017-05-11 2020-05-13 三菱電機株式会社 熱交換器及び冷凍サイクル装置
ES2885836T3 (es) 2017-06-22 2021-12-15 Mitsubishi Electric Corp Intercambiador de calor, dispositivo de ciclo de refrigeración y acondicionador de aire
JP6631608B2 (ja) * 2017-09-25 2020-01-15 ダイキン工業株式会社 空気調和装置
JP6865353B2 (ja) * 2018-01-09 2021-04-28 パナソニックＩｐマネジメント株式会社 熱交換器
JP6466631B1 (ja) * 2018-03-13 2019-02-06 日立ジョンソンコントロールズ空調株式会社 熱交換器およびこれを備えた空気調和機
JP7004814B2 (ja) * 2018-06-13 2022-01-21 三菱電機株式会社 熱交換器、熱交換器ユニット、及び冷凍サイクル装置
JP7272422B2 (ja) * 2019-03-26 2023-05-12 株式会社富士通ゼネラル 熱交換器、及び熱交換器を備える空気調和機
US11988462B2 (en) 2020-08-31 2024-05-21 Samsung Electronics Co., Ltd. Heat exchanger and air conditioner using the heat exchanger

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0560482A (ja) * 1991-08-29 1993-03-09 Showa Alum Corp 熱交換器の製造方法
JPH0590173U (ja) * 1992-04-20 1993-12-07 住友軽金属工業株式会社 フィン・チューブ式熱交換器
JPH09324995A (ja) * 1996-06-05 1997-12-16 Toshiba Corp 熱交換器
JPH11294984A (ja) 1998-04-09 1999-10-29 Zexel:Kk 並設一体型熱交換器
JP2003262485A (ja) 2002-03-07 2003-09-19 Mitsubishi Electric Corp フィンチューブ型熱交換器、その製造方法及び冷凍空調装置
JP2005201467A (ja) * 2004-01-13 2005-07-28 Matsushita Electric Ind Co Ltd 熱交換器
JP2007017042A (ja) * 2005-07-06 2007-01-25 Matsushita Electric Ind Co Ltd 熱交換器
JP2010002138A (ja) 2008-06-20 2010-01-07 Daikin Ind Ltd 熱交換器

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2427336A (en) * 1945-04-25 1947-09-16 Peerless Of America Heat transfer unit
US3437134A (en) * 1965-10-24 1969-04-08 Borg Warner Heat exchanger
US4328861A (en) * 1979-06-21 1982-05-11 Borg-Warner Corporation Louvred fins for heat exchangers
JPS61237995A (ja) * 1985-04-12 1986-10-23 Matsushita Electric Ind Co Ltd フイン付熱交換器
KR900006245B1 (ko) * 1985-04-19 1990-08-27 마쯔시다덴기산교 가부시기가이샤 열교환기
US4709753A (en) * 1986-09-08 1987-12-01 Nordyne, Inc. Uni-directional fin-and-tube heat exchanger
KR100290761B1 (ko) * 1995-01-23 2001-06-01 구자홍 핀 튜브형 열교환기
KR100210072B1 (ko) * 1996-07-09 1999-07-15 윤종용 공기조화기의 열교환기
US5752567A (en) * 1996-12-04 1998-05-19 York International Corporation Heat exchanger fin structure
US5975200A (en) * 1997-04-23 1999-11-02 Denso Corporation Plate-fin type heat exchanger
US5787972A (en) * 1997-08-22 1998-08-04 General Motors Corporation Compression tolerant louvered heat exchanger fin
US6964296B2 (en) * 2001-02-07 2005-11-15 Modine Manufacturing Company Heat exchanger
US7021370B2 (en) * 2003-07-24 2006-04-04 Delphi Technologies, Inc. Fin-and-tube type heat exchanger
KR100621525B1 (ko) * 2005-06-09 2006-09-11 위니아만도 주식회사 열교환기의 전열핀
US7540320B1 (en) * 2006-02-10 2009-06-02 Thomas Middleton Semmes High efficiency conditioning air apparatus

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0560482A (ja) * 1991-08-29 1993-03-09 Showa Alum Corp 熱交換器の製造方法
JPH0590173U (ja) * 1992-04-20 1993-12-07 住友軽金属工業株式会社 フィン・チューブ式熱交換器
JPH09324995A (ja) * 1996-06-05 1997-12-16 Toshiba Corp 熱交換器
JPH11294984A (ja) 1998-04-09 1999-10-29 Zexel:Kk 並設一体型熱交換器
JP2003262485A (ja) 2002-03-07 2003-09-19 Mitsubishi Electric Corp フィンチューブ型熱交換器、その製造方法及び冷凍空調装置
JP2005201467A (ja) * 2004-01-13 2005-07-28 Matsushita Electric Ind Co Ltd 熱交換器
JP2007017042A (ja) * 2005-07-06 2007-01-25 Matsushita Electric Ind Co Ltd 熱交換器
JP2010002138A (ja) 2008-06-20 2010-01-07 Daikin Ind Ltd 熱交換器

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014030844A (ja) * 2012-08-06 2014-02-20 Hidaka Seiki Kk 扁平チューブ用フィンおよび扁平チューブ用フィンの製造金型と金属帯状体の送り装置
EP2840341A1 (fr) * 2013-07-30 2015-02-25 Samsung Electronics Co., Ltd Échangeur de chaleur
US9863714B2 (en) 2013-07-30 2018-01-09 Samsung Electronics Co., Ltd. Heat exchanger and corrugated fin thereof
US20170030662A1 (en) * 2015-07-31 2017-02-02 Lg Electronics Inc. Heat exchanger

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AU2012208120A1 (en) 2013-08-01
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US20130299153A1 (en) 2013-11-14
BR112013018043A2 (pt) 2019-09-24
KR20130099254A (ko) 2013-09-05
KR101313347B1 (ko) 2013-10-01
EP2667139A1 (fr) 2013-11-27
CN103314269A (zh) 2013-09-18
JP5177306B2 (ja) 2013-04-03

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