WO2014207785A1 - Échangeur de chaleur, structure d'échangeur de chaleur, et ailette destinée à un échangeur de chaleur - Google Patents

Échangeur de chaleur, structure d'échangeur de chaleur, et ailette destinée à un échangeur de chaleur Download PDF

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Publication number
WO2014207785A1
WO2014207785A1 PCT/JP2013/004041 JP2013004041W WO2014207785A1 WO 2014207785 A1 WO2014207785 A1 WO 2014207785A1 JP 2013004041 W JP2013004041 W JP 2013004041W WO 2014207785 A1 WO2014207785 A1 WO 2014207785A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
heat transfer
heat
fin
tubes
Prior art date
Application number
PCT/JP2013/004041
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English (en)
Japanese (ja)
Inventor
秀哲 立野井
芳裕 波良
克弘 齊藤
陽一 上藤
青木　泰高
Original Assignee
三菱重工業株式会社
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.)
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Application filed by 三菱重工業株式会社 filed Critical 三菱重工業株式会社
Priority to PCT/JP2013/004041 priority Critical patent/WO2014207785A1/fr
Priority to EP13888478.8A priority patent/EP3015808B1/fr
Priority to JP2015523665A priority patent/JPWO2014207785A1/ja
Publication of WO2014207785A1 publication Critical patent/WO2014207785A1/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
    • F28F17/00—Removing ice or water from heat-exchange apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • 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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins

Definitions

  • the present invention relates to a heat exchanger used in an air conditioner.
  • one heat exchanger functions as a condenser during cooling operation and functions as an evaporator during heating operation.
  • the heat exchanger of the outdoor unit functions as an evaporator when heating operation is performed.
  • the evaporator is in the air when the outside air temperature decreases to, for example, about 5 ° C. below freezing point.
  • a frosting phenomenon occurs in which moisture adheres to the evaporator as frost.
  • frost formation occurs from the windward side of the heat exchanger and gradually grows toward the leeward side.
  • the heat exchanger is frosted, the fin heat transfer area that directly exchanges heat with air decreases, and the heating capacity decreases.
  • the ventilation path between fins narrows by frost formation, and heating capacity also falls even if air volume falls. Therefore, during the heating operation when the outside air temperature is low, the defrosting operation is performed periodically, for example, in order to remove the attached frost. During the defrosting operation, the heating operation is stopped, which may impair the comfort for the user of the air conditioner. Therefore, various techniques for making it difficult for frost to form on the windward side of the heat exchanger (evaporator) have been proposed.
  • a typical example of the defrosting operation is a method in which a refrigeration cycle is used as a circuit during cooling operation, the outdoor heat exchanger functions as a condenser, and high-temperature refrigerant is flowed to melt frost.
  • the water generated by the frost melting by the defrosting operation (hereinafter referred to as melted water) is not drained during the defrosting operation, but on the fins. Sometimes it remains. If the heating operation is resumed after the defrosting operation while the molten water remains, the molten water is frozen and frosted again, and the ventilation path is likely to narrow.
  • the present inventors have proposed a heat exchanger capable of suppressing frost formation during heating operation and promoting drainage of molten water generated when the defrost operation is performed.
  • a heat conduction suppressing portion extending along the direction in which the outside air flows is formed in the fin.
  • the proposal of patent document 1 can suppress the fall of the temperature of the windward side part of the flow direction of the external air of a fin, and can suppress frost formation, when the heat exchanger of an outdoor unit functions as an evaporator.
  • the heat exchanger of patent document 1 can drain
  • the present invention can maintain the ventilation path even if frost is formed on the windward side of the heat exchanger from a viewpoint different from Patent Document 1. It aims at providing the heat exchanger which can improve drainage more.
  • the heat exchanger according to the present invention includes a plurality of tubes in which flow paths through which refrigerant flows are formed, and a plurality of heat transfer walls extending from one to the other of adjacent tubes in the tube extending direction.
  • the heat transfer wall according to the present invention includes a first heat transfer piece connected to the first edge located on the windward side of the passing air flow, and a second retreating to the leeward side of the air flow direction from the first edge. And the first heat transfer piece is arranged at least every other layer of the array.
  • the heat transfer wall includes a first edge and a second edge that recedes leeward from the first edge, and the first edge and the second edge transfer heat. At least every other layer is arranged in the direction of the wall arrangement. Therefore, the fin pitch between the 1st edge parts adjacent to the direction of an arrangement
  • the heat transfer wall is interrupted on the windward side of the second edge portion.
  • the heat exchanger according to the present invention is more effective than the molten water flowing down while meandering through the fins. Can be discharged to the outside of the heat exchanger in a short time.
  • the heat exchanger of the present invention since the boundary portion with the tube in which the molten water is particularly likely to stay is reduced due to the interruption of the heat transfer wall, the amount of the retained molten water is reduced. Therefore, even if the molten water solidifies after restarting the heating operation, the heat transfer area of the fins can be secured.
  • Each of the heat transfer walls in the present invention includes a first heat transfer piece connected to the first edge located on the windward side of the passing air flow, and a first heat transfer wall receding to the leeward side of the air flow direction from the first edge.
  • the first heat transfer piece can be alternately arranged on the side of one adjacent tube and the side of the other tube.
  • the heat transfer wall includes a first edge and a second edge that recedes leeward from the first edge, and the first edge and the second edge transfer heat. Alternating in the direction of the array of walls. Therefore, between the first edges adjacent to each other in the arrangement direction, there is a portion where the heat transfer wall does not exist because the second edge is retracted to the leeward side, so that the fin pitch is widened. Therefore, even if frost is concentrated on the first edge located at the tip of the fin on the windward side, heat exchange can be maintained on the leeward side by securing the ventilation path.
  • the heat transfer wall is provided with heat transfer promoting means on the windward side.
  • the heat transfer performance of the heat transfer wall can be promoted on the windward side.
  • a heat transfer wall is provided with a heat transfer promotion means on the leeward side.
  • each heat transfer wall includes a second heat transfer piece connected to the third edge located on the leeward side of the air flow, a fourth edge that recedes further to the windward side than the third edge, It is preferable that the second heat transfer pieces are alternately arranged on the side of one adjacent tube and the side of the other tube, every other layer in the arrangement. Since there is a region where no heat transfer wall exists on the leeward side, the drainage of the molten water can be improved also on the leeward side. Furthermore, even if the remaining molten water is solidified, in addition to ensuring the heat transfer area of the fins used for heat exchange directly with air, it is possible to prevent the ventilation path from becoming narrow.
  • the heat exchanger structure of the present invention is a corrugated type that is arranged along a predetermined direction and is provided between a plurality of tubes each having a flow path through which a refrigerant flows, and between adjacent tubes, and is capable of exchanging heat with the tubes.
  • a heat exchanger assembly comprising a plurality of heat exchangers arranged in the direction of air flow passing therethrough, wherein the heat exchanger arranged at the furthest upstream side in the direction of air flow is It consists of a heat exchanger.
  • the fin for a heat exchanger used in the heat exchanger of the present invention described above is preferably a corrugated fin provided between adjacent tubes and capable of exchanging heat with the tube.
  • the corrugated fin has a wide fin pitch even if the fin pitch on the tip side located on the windward side is widened so that frost is concentrated on the first edge as the tip of the fin. Since the portion is secured as a ventilation path, heat exchange can be continued on the leeward side of the fin. Therefore, in the air conditioner using the heat exchanger of the present invention, the time until performing the defrosting operation becomes longer, and the frequency of the defrosting operation can be reduced.
  • the first edge and the second edge are alternately arranged in the direction of the heat transfer wall arrangement, the molten water can be excluded from the heat exchanger in a short time. Since it is possible, the drainage of molten water can be improved. Furthermore, according to the present invention, since the amount of retained molten water is reduced, the heat transfer area of the fin can be secured even if the molten water solidifies after restarting the heating operation.
  • FIG. 1 It is a perspective view which shows the heat exchanger concerning embodiment of this invention. It is a partial exploded perspective view showing the heat exchanger concerning a 1st embodiment of the present invention.
  • the heat exchanger of 1st Embodiment is shown, (a) is a top view which shows between adjacent tubes, (b) is a figure which shows the cross section of a fin typically, (c) is an expanded view of a fin. It is a schematic diagram for demonstrating the effect of 1st Embodiment.
  • FIG. 1st Embodiment It is a schematic diagram for demonstrating the effect of 1st Embodiment, (a) shows the cross section of the fin of embodiment, (b) shows the cross section of the conventional fin, (c) is embodiment of the embodiment The cross section of a heat exchanger is shown, (d) has shown the cross section of the conventional heat exchanger. It is a perspective view which shows the modification of the fin of 1st Embodiment. It is a cross-sectional view showing another modification of the fin of the first embodiment. It is a cross-sectional view showing another modification of the fin of the first embodiment.
  • FIG. 1 It is a partial exploded perspective view which shows the heat exchanger concerning 2nd Embodiment of this invention, (a) provides a louver on the leeward side, (b) provides undulation on the leeward side and louver on the leeward side, (c ) Shows an example in which louvers are provided on both the leeward side and the leeward side.
  • the heat exchanger concerning 3rd Embodiment of this invention is shown, (a) is a partial exploded perspective view, (b) is a top view which shows between adjacent tubes, (c) shows the expanded view of a fin. It is a perspective view which shows the heat exchanger structure concerning 4th Embodiment of this invention. It is a figure which shows the example of a change of this invention.
  • the heat exchanger 10 in the present embodiment is connected to the core 20 formed by alternately laminating a plurality of tubes 21 and a plurality of fins 22 through which refrigerant flows, and the ends of the tubes 21 are connected.
  • a pair of header tubes 30 that perform heat exchange between the outside air and the refrigerant.
  • the heat exchanger 10 is applied to an outdoor heat exchanger of a heat pump type air conditioner. In this case, the heat exchanger 10 is incorporated in the outdoor unit of the air conditioner with the tube 21 standing in the vertical direction Y.
  • the heat exchanger 10 receives an air flow A generated by a fan (not shown), and the air flow passes through an air passage 27 that is a gap formed between the tube 21 and the fin 22 of the core 20. Exchanges heat with the outside air.
  • the tube 21 is a member having a flat cross section provided with a refrigerant flow path penetrating in the axial direction.
  • the tube 21 is produced by extruding copper or copper alloy having excellent thermal conductivity, aluminum or aluminum alloy, or roll-molding a plate-like material.
  • both ends in the axial direction are joined to the header tube 30 by brazing, for example, and a refrigerant channel 21a formed inside along the axial direction communicates with a refrigerant channel of the header tube 30 described later.
  • the circulation of the refrigerant between the tube 21 and the header tube 30 is ensured.
  • the fin 22 is a corrugated fin formed by alternately repeating mountain folding and valley folding.
  • the fin 22 includes a heat transfer wall 23 and a turn-back 24 that connects the adjacent heat transfer walls 23 and 23 with a space therebetween, and meanders at both ends in the width direction X.
  • interval of the heat-transfer walls 23 and 23 ... in which a some layer is arranged in the perpendicular direction Y is set substantially equal. It is assumed that one heat transfer wall 23 forms one layer.
  • an example in which the folding 24 is rectangular is shown, but the folding 24 may have another shape such as a V-shape.
  • the fins 22 are integrally formed by bending a plate-like material made of the same material as the tube 21.
  • the fin 22 has a feature in the windward side configuration, which will be described later.
  • the core 20 is configured by alternately stacking the above tubes 21 and fins 22 in the width direction X of the heat exchanger 10.
  • the fins 22 arranged between the tubes 21 and 21 adjacent to each other in the width direction X are joined to the tubes 21 and 21 by, for example, brazing, so that the fins 22 and the tubes 21 can exchange heat with each other. It is said.
  • the core 20 is provided with side plates 26 at both ends in the width direction X.
  • the side plate 26 functions as a reinforcing member for the core 20, and both end portions in the vertical direction are supported by the header tube 30.
  • the header tube 30 is a member in which a coolant channel (not shown) is formed.
  • a refrigerant inlet is provided on one end side in the width direction X of the header tube 30 (lower header tube 32) arranged on the lower side in the figure, and is supplied to the inlet from refrigerant piping constituting the refrigeration cycle.
  • the refrigerant flows through the flow path of the lower header tube 32 and flows into the plurality of tubes 21.
  • a refrigerant outlet is provided on one end side in the width direction X, and the refrigerant flowing through the tube 21 flows into the upper header tube 31. It flows out from the outlet toward the refrigerant pipe constituting the refrigeration cycle.
  • the header tube 30 is made of the same material as the tube 21.
  • the tube 21 can be manufactured integrally or by combining a plurality of members.
  • the air conditioner provided with the heat exchanger 10 as an outdoor heat exchanger is performing a heating operation when the outside air temperature is low, frosting occurs on the fin 22 on the windward side of the air flow A.
  • the windward side of the airflow A may be simply referred to as the windward side.
  • the air conditioner performs a defrosting operation, for example, periodically to remove the attached frost.
  • the defrosting operation if the molten water remains without being sufficiently drained from the heat exchanger 10, heating is performed. After resuming operation, the molten water may freeze and frost again.
  • the heat exchanger 10 widens the fin pitch on the windward side of the fins 22 from the leeward side, thereby extending the time until the defrosting operation is performed by maintaining the heat exchange on the leeward side even if frost formation occurs. . Moreover, the heat exchanger 10 improves the drainage of molten water.
  • FIGS. 3B the fin 22 has a cross section in the leeward range U indicated by a solid line and a cross section in the leeward range D indicated by a broken line. The same applies to FIGS. 5 and 7 to 9.
  • the fin 22 has a fin pitch P1 in a predetermined range U on the windward side (FIG. 3A) wider than the fin pitch P2 in the range D on the leeward side. Is set.
  • the heat transfer wall 23 of the fin 22 has the following two conditions. The first condition is that either side of the width direction X is cut out with the middle point M of the heat transfer wall 23 as a boundary. Due to the formation of the notch, the front edge 23b on the side that is not cut back is retracted to the leeward side from the front edge 23a on the side that is not cut.
  • Heat transfer pieces 23 ⁇ / b> L and 23 ⁇ / b> R that protrude to the windward side of the front edge 23 b are provided on the side that is not cut out.
  • the second condition is that the heat transfer pieces 23L and 23R are alternately arranged in the width direction X every other layer of the heat transfer wall 23 with the middle point M as a boundary.
  • This condition is equivalent to that the notches are alternately arranged in the width direction X every other layer of the heat transfer wall 23 with the middle point M as a boundary when the notches are mainly used.
  • the fins 22 are arranged with the heat transfer pieces 23L every other layer on the one side L (left side of FIG. 3B) with the midpoint M as a boundary.
  • the heat transfer pieces 23R are arranged every other layer. Moreover, on one side L and the other side R, the phase of the fin pitch P1 is shifted by 1 ⁇ 2 (half cycle).
  • turnback which opposes the tube 21 of the heat-transfer pieces 23L and 23R is notched, and the fin 22 is not provided with the return
  • the edge which opposes the tube 21 may be joined by brazing so that the heat transfer pieces 23L and 23R may be heat-exchanged, or may be separated from the tube 21.
  • the fin material 25 used to configure the fin 22 is a plate made of a rectangular metal material as described above, but when the fin 22 is assembled to the heat exchanger 10 as the fin 22.
  • a plurality of rectangular cutouts 25a are formed at equal intervals on the edge corresponding to the windward side.
  • the material portion 25b remaining between the adjacent cutouts 25a and 25a constitutes the heat transfer pieces 23L and 23R.
  • the fin material 25 is formed by alternately repeating notches 25a and material portions 25b at the end edges.
  • the fin 22 has a fin pitch P1 in the range U located on the leeward side wider than the fin pitch P2 in the range D on the leeward side.
  • the frost Fa is concentrated on the front edge 23a of the heat transfer wall 23 located on the windward side
  • the ventilation path 27 is narrowed, but the fin pitch P1 is wide so that the windward side is frosted. It is possible to lengthen the time until closing with Fa.
  • the heat exchanger 10 can maintain the heat exchange in the range D which is the leeward side of the fin 22 over a long time, the air conditioner using the heat exchanger 10 is defrosting. The frequency of driving can be reduced.
  • the fins 22 can minimize a decrease in the efficiency of heat exchange.
  • the improvement of drainage in the present invention includes reducing the amount of retained molten water in addition to promoting the drainage itself.
  • the promotion of drainage will be explained. Since the heat exchanger 10 is provided with the front edge portion 23b that recedes to the leeward side, the heat transfer wall 23 is interrupted on the windward side (range U) of the fins 22, so that the frost F is melted during the defrosting operation.
  • the resulting molten water W flows down from both ends of the heat transfer pieces 23R, 23L in the width direction X as indicated by arrows Wf in FIG.
  • the molten water W flows down through the tube 21 on the side facing the tube 21 (not shown in FIG.
  • the heat exchanger 10 has the front edge portion 23b retracted to the leeward side, and the inner side IN of the turn-back 24 does not exist in the leeward range U where frost formation is likely to occur. As shown in FIG. 5 (c), it is only above the boundary between the heat transfer pieces 23 ⁇ / b> L and 23 ⁇ / b> R and the tube 21. Therefore, according to the heat exchanger 10, since the amount of the molten water W staying in the fin 22 can be reduced, even if the molten water W solidifies after restarting the heating operation, a wider heat transfer area of the fin 22 is secured. In addition to this, it is possible to prevent the ventilation path from becoming narrow.
  • the heat exchanger 10 can ensure heat transfer performance in the range U if the heat transfer pieces 23L and 23R are connected to the tube 21 so as to be able to exchange heat.
  • the shape of the notch of the fin 22 in plan view is rectangular, but the shape of the notch is arbitrary as long as the object of the present invention can be achieved.
  • a circular cutout FIG. 6A
  • a triangular cutout FIG. 6B
  • a polygonal cutout FIG. 6C
  • a stepped shape Various forms such as a notch (FIG. 6D) can be adopted.
  • the folding pattern of the fins 22 is arbitrary as long as the object of the present invention can be achieved.
  • 7 and 8 show some patterns that can be used in the present invention, and the present invention can adopt these patterns.
  • FIG. 7A the lower side of the heat transfer wall 23 connected to the turn 24 is cut away, whereas FIG. 7B is opposite to FIG.
  • the upper side of the hot wall 23 is cut off. 7A and 7B, compared with the conventional corrugated fin in which the heat transfer wall 23 is provided over almost the entire area between the tubes 21 and 21, the molten water flows downward due to the shortcut. Therefore, the drainage of molten water can be promoted.
  • the heat transfer wall 23 is formed along the horizontal direction, but as shown in FIG. 7C, the heat transfer wall 23 faces upward toward the center in the width direction of the fin 22. Can be tilted.
  • the heat transfer wall 23 can be inclined downward toward the center of the fin 22 in the width direction, as shown in FIG. 7D. By inclining the heat transfer wall 23 in this way, the drainage of the molten water can be further promoted.
  • the heat transfer piece 23L provided on one side in the width direction X and the heat transfer piece 23R provided on the other side are viewed in the vertical direction (in plan view).
  • the present invention is not limited to this.
  • the fin pitch P1 of the heat transfer pieces 23L, 23L, and the fin pitch P1 of the heat transfer pieces 23R, 23R, ... are as wide as twice the fin pitch P2 in the range D.
  • this invention is the center part of the width direction X of the fin 22, between the heat transfer piece 23L provided in one side, and the heat transfer piece 23R provided in the other side.
  • a gap G in the width direction can be provided.
  • the fin 22 of 1st Embodiment expands the fin pitch P1 of the range U by notching a part of fin raw material 25, this invention is not limited to this.
  • a region corresponding to the notch can also be formed by bending the heat transfer pieces 23L and R downward.
  • the fin pitch P1 in the range U can be made larger than the fin pitch P2 in the range D, as with the fins 22 of the first embodiment.
  • the drooping piece 23e generated by the bending may contact the surface of the heat transfer wall 23 located at the lower layer as shown in FIG. 8C, or as shown in FIG.
  • the tip may be separated from the surface of the heat transfer wall 23 located in the lower layer.
  • the drooping piece 23e constitutes a path for guiding the molten water downward and contributes to promoting drainage.
  • the bending angle is arbitrary.
  • the fins 22 can be provided with means for improving the heat conductivity of one or both of the windward side and the leeward side.
  • a louver 28 can be formed on the leeward side of the fin 22 (heat transfer wall 23) (second type 2-1). If the heat transfer performance of the fins 22 on the leeward side is made higher than that on the leeward side, dehumidification on the leeward side can be suppressed, so that dehumidification can also be performed on the leeward side.
  • frost formation is caused by dehumidification by the fins 22, so if the heat transfer performance on the leeward side is increased as in the case of the embodiment 2-1, the idea is concentrated on the leeward side. Since it is suppressed, it is easy to ensure the ventilation path 27.
  • the heat exchange on the leeward side can be continued, so the time during which the heating operation can be continued can be lengthened.
  • the upwind side of the fin 22 does not require processing, an increase in processing cost can be suppressed.
  • the louver 28 is formed by cutting and raising the heat transfer wall 23, and the heat transfer between the air and the heat transfer wall 23 is promoted by disturbing the flow of air passing through the louver 28. Note that the louver 28 has a greater effect of promoting heat transfer than the undulation 29 described later. Moreover, the area
  • the present invention can also improve the heat transfer on the windward side.
  • a undulation 29 can be formed on the windward side of the fin 22 (heat transfer wall 23) (second type 2-2).
  • This undulation 29 has a waveform in the longitudinal section of the heat transfer wall 23, and has a shape in which mountains, valleys, mountains,... Are repeated from the windward side toward the leeward side.
  • the heat transfer area on the windward side is increased, so that the heat transfer performance can be improved compared to fins made of flat plates.
  • heat transfer can be improved by generating eddy currents in the process of airflow passing through the undulations 29.
  • not only the undulation 29 but also a louver 28 can be provided as shown in FIG.
  • the same configuration as the front end side of the windward fin 22 of the first embodiment can be provided on the front end side of the leeward fin 22. That is, as shown in FIG. 10, one side of the width direction X is notched with the middle point M of the heat transfer wall 23 as a boundary. Due to the formation of the cutout, the front edge portion 23d on the side that is not cut away from the front edge portion 23c on the side that is not cut out is retracted to the windward side. Heat transfer pieces 23L and 23R are provided on the non-notched side to protrude leeward from the front edge 23d.
  • the heat transfer pieces 23L and 23R are alternately arranged in the width direction X every other layer of the heat transfer wall 23 with the middle point M as a boundary.
  • frost formation is less on the leeward side
  • the frost formation also occurs on the leeward side of the fins 22, so that when the defrosting operation is performed, the molten water may stay on the leeward side of the fins 22. Therefore, the third embodiment reduces the amount of molten water staying on the leeward side by adopting a configuration in which the fin pitch is widened also on the leeward side.
  • the air conditioner may arrange a plurality of (here, two) heat exchangers 10 (10a, 10b) in the direction in which the wind flows in order to obtain high heat transfer properties.
  • the present invention can be applied to an air conditioner including a plurality of heat exchangers 10.
  • the present invention should be applied to the heat exchanger 10a disposed on the leeward side, the necessity for application is small for the heat exchanger 10b disposed on the leeward side.
  • the airflow that has passed through the windward heat exchanger 10a flows into the leeward heat exchanger 10b, and this airflow passes through the windward heat exchanger 10a.
  • the application of the present invention to the leeward heat exchanger 10b is not excluded, but the leeward heat exchanger 10b can secure the heat transfer area of the fins and suppress the heat transfer loss as much as possible. It fits the purpose of providing a plurality of heat exchangers. Even if it is a case where not only two but three or more heat exchangers are provided, the present invention may be applied to a heat exchanger arranged on the furthest side.
  • the “application of the present invention” mentioned here includes all the individual elements disclosed in the first to third embodiments described so far.
  • the configuration described in the above embodiment can be selected or modified as appropriate to another configuration without departing from the gist of the present invention.
  • the heat-transfer piece 23L and the heat-transfer piece 23R can also be arrange

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  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
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  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Other Air-Conditioning Systems (AREA)

Abstract

La présente invention concerne un échangeur de chaleur susceptible de maintenir un échange de chaleur dans des ailettes sur le côté sous le vent de l'échangeur de chaleur et d'améliorer l'évacuation d'eau de fonte en assurant un passage de ventilation même lorsque du givre se forme sur le côté au vent de l'échangeur de chaleur. Cet échangeur de chaleur (10) comprend une pluralité de tubes (21) dans lesquels est formé un canal (21a) de fluide frigorigène à travers lequel circule un fluide frigorigène, et des ailettes ondulées (22) qui peuvent échanger la chaleur avec les tubes (21) et dans lesquelles est disposée une pluralité de parois (23) de transfert de chaleur qui s'étendent depuis un côté des tubes (21) adjacents vers l'autre côté, dans une direction s'étendant depuis les tubes (21). De plus, chaque paroi (23) de transfert de chaleur possède une partie (23R (L)) de transfert de chaleur qui est continue avec une section bord avant (23a) positionnée sur le côté au vent du flux d'air (A) qui passe à travers, et une section bord avant (23b) qui rentre davantage sur le côté sous le vent que la section bord avant (23a) dans la direction du flux d'air (A). Une première partie de transfert de chaleur est disposée de façon alternée sur toutes les deux couches sur un tube (21) et un autre tube (21) adjacent.
PCT/JP2013/004041 2013-06-28 2013-06-28 Échangeur de chaleur, structure d'échangeur de chaleur, et ailette destinée à un échangeur de chaleur WO2014207785A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
PCT/JP2013/004041 WO2014207785A1 (fr) 2013-06-28 2013-06-28 Échangeur de chaleur, structure d'échangeur de chaleur, et ailette destinée à un échangeur de chaleur
EP13888478.8A EP3015808B1 (fr) 2013-06-28 2013-06-28 Échangeur de chaleur, structure d'échangeur de chaleur, et ailette destinée à un échangeur de chaleur
JP2015523665A JPWO2014207785A1 (ja) 2013-06-28 2013-06-28 熱交換器、熱交換器構造体、及び、熱交換器用のフィン

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JP2018009743A (ja) * 2016-07-14 2018-01-18 日立ジョンソンコントロールズ空調株式会社 熱交換器
JPWO2018008134A1 (ja) * 2016-07-07 2019-03-14 三菱電機株式会社 熱交換器
JP6734002B1 (ja) * 2019-11-11 2020-08-05 三菱電機株式会社 熱交換器および冷凍サイクル装置
JPWO2021095538A1 (fr) * 2019-11-11 2021-05-20
US11035623B2 (en) 2018-03-02 2021-06-15 Hitachi-Johnson Conrols Air Conditioning, Inc. Heat exchanger, outdoor unit, refrigeration cycle device, and heat exchanger manufacturing method

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JP6766723B2 (ja) 2017-03-27 2020-10-14 ダイキン工業株式会社 熱交換器又は冷凍装置
EP3604974A4 (fr) 2017-03-27 2020-04-22 Daikin Industries, Ltd. Échangeur de chaleur et dispositif frigorifique
JP6766722B2 (ja) 2017-03-27 2020-10-14 ダイキン工業株式会社 熱交換器又は冷凍装置
JP6880901B2 (ja) 2017-03-27 2021-06-02 ダイキン工業株式会社 熱交換器ユニット

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JPWO2018008134A1 (ja) * 2016-07-07 2019-03-14 三菱電機株式会社 熱交換器
JP2018009743A (ja) * 2016-07-14 2018-01-18 日立ジョンソンコントロールズ空調株式会社 熱交換器
US11035623B2 (en) 2018-03-02 2021-06-15 Hitachi-Johnson Conrols Air Conditioning, Inc. Heat exchanger, outdoor unit, refrigeration cycle device, and heat exchanger manufacturing method
JP6734002B1 (ja) * 2019-11-11 2020-08-05 三菱電機株式会社 熱交換器および冷凍サイクル装置
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