JPWO2018100738A1 - Heat exchanger and air conditioner - Google Patents

Abstract

A heat exchanger with improved drainage is provided. In the heat exchanger, the first plate fin (12a) is arranged at a first interval from the at least one heat transfer tube (11) in a second direction perpendicular to the first direction. The second plate fin (12b) is arranged at a second interval from the first plate fin (12a) in the second direction. The first plate fin (12a) and the first corrugated fin (13a) are connected by a plurality of first connection portions (24) arranged at a third interval in the first direction. The first plate fin (12a) and the second corrugated fin (13b) are connected by a plurality of second connection portions (25) arranged at a fourth interval in the first direction. The third interval and the fourth interval are larger than the first interval and the second interval.

Description

  The present invention relates to a heat exchanger and an air conditioner, and more particularly to a heat exchanger and an air conditioner including corrugated fins.

  2. Description of the Related Art Conventionally, a heat exchanger is known that includes a heat transfer tube through which a refrigerant circulates and a corrugated fin connected to the heat transfer tube (see, for example, JP-A-9-280754).

JP-A-9-280754

  In the heat exchanger described above, in order to ensure the drainage of the condensed water that condenses on the surface of the corrugated fins, measures such as forming a louver on the corrugated fins or forming a groove on the surface of the heat transfer tube have been taken. However, it was difficult to ensure sufficient drainage in the corrugated fins only by such measures.

  The objective of this invention is providing the heat exchanger which improved the drainage property in the corrugated fin.

  The heat exchanger according to the present disclosure includes at least one heat transfer tube, a first plate fin, a second plate fin, a first corrugated fin, and a second corrugated fin. The at least one heat transfer tube extends in a first direction intersecting the air flow direction, and the refrigerant flows therein. The first plate fin extends in the first direction. The first plate fin is arranged at a first interval from at least one heat transfer tube in a second direction perpendicular to the first direction. The second plate fin extends in the first direction. The second plate fin is disposed at a second interval from the first plate fin in the second direction. The first corrugated fin is disposed between the at least one heat transfer tube and the first plate fin. The second corrugated fin is disposed between the first plate fin and the second plate fin. The first plate fin and the first corrugated fin are connected by a plurality of first connection portions arranged at a third interval in the first direction. The first plate fin and the second corrugated fin are connected by a plurality of second connection portions arranged at a fourth interval in the first direction. The third interval and the fourth interval are larger than the first interval and the second interval.

  The air conditioning apparatus according to the present disclosure includes a compressor, a first heat exchanger, an expansion valve, and a second heat exchanger, and includes a refrigerant circuit in which the refrigerant circulates. At least one of the first heat exchanger and the second heat exchanger is the heat exchanger.

  According to the above, since the inclination angle of the inclined portion located between the first or second connection portions in the first and second corrugated fins can be increased, drainage of condensed water through the inclined portion. Can be improved.

It is a schematic diagram of the heat exchanger which concerns on Embodiment 1 of this invention. It is a partial expansion perspective schematic diagram in the area | region II of FIG. It is a front schematic diagram of the part of the heat exchanger shown in FIG. It is a partial cross section schematic diagram of the heat exchanger which concerns on Embodiment 2 of this invention. It is a partial cross section schematic diagram of the heat exchanger which concerns on Embodiment 3 of this invention. It is a partial perspective schematic diagram of the heat exchanger shown in FIG. It is a partial upper surface schematic diagram of the heat exchanger shown in FIG. It is a schematic diagram which shows the refrigerant circuit of the air conditioning apparatus which concerns on Embodiment 4 of this invention.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following drawings, the same or corresponding parts are denoted by the same reference numerals, and the description thereof will not be repeated. Moreover, in the following drawings including FIG. 1, the relationship of the size of each component may be different from the actual one. Furthermore, the forms of the constituent elements shown in the entire specification are merely examples, and are not limited to these descriptions.

Embodiment 1 FIG.
<Configuration of heat exchanger>
FIG. 1 is a schematic diagram of a heat exchanger according to Embodiment 1 of the present invention. FIG. 2 is a partially enlarged perspective schematic view of region II in FIG. FIG. 3 is a schematic front view of a portion of the heat exchanger shown in FIG.

  The heat exchanger 1 shown in FIGS. 1 to 3 includes a plurality of heat transfer tubes 11 that are flat tubes, a plurality of plate fins 12 disposed between the heat transfer tubes 11, and the heat transfer tubes 11 and the plate fins 12. A corrugated fin 13 disposed between or between adjacent plate fins 12, and an upper header 2 and a lower header 3 respectively connected to an upper end and a lower end of a heat transfer tube 11 disposed along the direction of gravity. Prepare. The main body 10 is constituted by the heat transfer tube 11, the plate fin 12 and the corrugated fin 13. The heat transfer tube 11 is provided so as to extend along a first direction that is a direction along the direction of gravity. A refrigerant circulates inside the heat transfer tube 11. Inside the heat transfer tube 11 having a flat tubular shape, a number of refrigerant flow paths may be formed along the extending direction (first direction).

  The plurality of heat transfer tubes 11 are arranged at intervals in a second direction indicated by an arrow 16 that intersects the first direction so as to have a predetermined pitch P1 as shown in FIG. In the heat exchanger 1 shown in FIGS. 1 to 3, first to third plate fins 12 a to 12 c are arranged between adjacent heat transfer tubes 11. Between the heat exchanger tube 11 and the 1st-3rd plate fins 12a-12c, the 1st-4th corrugated fins 13a-13d are arrange | positioned. The configuration between adjacent heat transfer tubes 11 is basically the same.

  Speaking from a different point of view, the heat exchanger 1 includes at least one heat transfer tube 11, a first plate fin 12a, a second plate fin 12b, and a third plate fin 12c. A first corrugated fin 13a, a second corrugated fin 13b, and third and fourth corrugated fins 13c, 13d. At least one heat transfer tube 11 extends in a first direction indicated by an arrow 15 that intersects the air flow direction. A refrigerant circulates inside the heat transfer tube 11. The first plate fin 12 a extends in the first direction indicated by the arrow 15. The first plate fin 12a is arranged with at least one heat transfer tube 11 and a first interval P21 in the second direction indicated by the arrow 16 perpendicular to the first direction. The second plate fin 12b extends in the first direction. The second plate fins 12b are arranged at a second interval P22 from the first plate fins 12a in the second direction indicated by the arrow 16. In addition, the space | interval between the 2nd plate fin 12b and the 3rd plate fin 12c in a 2nd direction may be the same as the said 2nd space | interval P22, and may differ. Further, the interval between the heat transfer tube 11 adjacent to the third plate fin 12c and the third plate fin 12c may be the same as or different from the first interval P21. Further, the first interval P21 and the second interval P22 may be the same or different.

  The first corrugated fin 13a is disposed between at least one heat transfer tube 11 and the first plate fin 12a. The second corrugated fin 13b is disposed between the first plate fin 12a and the second plate fin 12b. The third corrugated fin 13c is disposed between the second plate fin 12b and the third plate fin 12c. The fourth corrugated fin 13 d is disposed between the third plate fin 12 c and the other heat transfer tube 11. The first plate fins 12a and the first corrugated fins 13a are connected by a plurality of first connecting portions 24 arranged at a third interval P3 in the first direction indicated by the arrow 15. The first plate fins 12a and the second corrugated fins 13b are connected by a plurality of second connection portions 25 arranged with a fourth interval P4 in the first direction indicated by the arrow 15. Moreover, the 1st corrugated fin 13a and the heat exchanger tube 11 are connected by the some connection part arrange | positioned at intervals along the 1st direction. The interval between the connection portions may be the same as the third interval P3. Further, the second corrugated fin 13b and the second plate fin 12b are connected by a plurality of connecting portions arranged at intervals along the first direction. The interval between the connection portions may be the same as the fourth interval P4. The third interval P3 and the fourth interval P4 may be the same or different.

  Further, the configuration of the connecting portion between the third and fourth corrugated fins 13c, 13d, the second and third plate fins 12b, 12c and the other heat transfer tubes 11 is basically the same as the first corrugated fin 13a. And the configuration of the connection portion between the heat transfer tube 11 and the first plate fin 12a. The third interval P3 and the fourth interval P4 are larger than the first interval P21 and the second interval P22. If it says from a different viewpoint, the 1st direction between the some connection part to which the corrugated fin 13 is connected with the plate fin 12 from the width | variety of the space between the heat exchanger tube 11 and the several plate fin 12 in a 2nd direction. The distance at has increased. Louvers may be formed on the inclined portions 33 and 34 of the first to fourth corrugated fins 13a to 13d.

  In the heat exchanger 1, the hydrophilicity of at least part of the surfaces of the first plate fins 12a, the second plate fins 12b, the third plate fins 12c, and the at least one heat transfer tube 11 is the first corrugate. It may be higher than the hydrophilicity of the surface of the fin 13a, the second corrugated fin 13b, the third and fourth corrugated fins 13c, 13d. As described above, the hydrophilicity of the surfaces of the plate fins 12, the corrugated fins 13, and the heat transfer tubes 11, for example, changes the material of these members or forms a surface treatment layer having different hydrophilicity on the surface. It can be adjusted by an arbitrary method such as changing the surface roughness. For example, the surface roughness of the plate fins 12 and the heat transfer tubes 11 may be larger than the surface roughness of the corrugated fins 13. Alternatively, a hydrophilic or hydrophobic surface treatment layer may be formed on any of the plate fins 12 and the heat transfer tubes 11 and the corrugated fins 13.

  In the heat exchanger 1, the thickness W of at least one heat transfer tube 11 in the second direction indicated by the arrow 16 in FIG. 3 may be greater than the thickness of the first to third plate fins 12a to 12c. Good. The thickness of the first to third plate fins 12a to 12c may be thicker than the thickness of the first to fourth corrugated fins 13a to 13d.

  In the heat exchanger 1, the positions of the plurality of first connection portions 24 overlap the positions of the plurality of second connection portions 25 in the first direction indicated by the arrow 15. Here, the position of the plurality of first connection parts 24 overlaps with the position of the plurality of second connection parts 25 when at least the first connection part 24 is viewed from the second direction. It means that a part overlaps the second connection part 25.

<Effects of heat exchanger>
In the heat exchanger according to the present disclosure, the first and second corrugated fins are based on the first and second intervals P21 and P22 which are the widths of the regions where the first and second corrugated fins 13a and 13b are disposed. The third interval P3 and the fourth interval P4, which are the pitches of the plurality of connecting portions 24 and 25 connected to the first plate fin 12a, are increased by 13a and 13b. Further, as described above, the third and fourth corrugated fins also have a pitch of the plurality of connecting portions with the plate fin 12 larger than the first and second intervals P21 and P22. Therefore, the inclined portions 33 and 34 of the first and second corrugated fins 13a and 13b located between the connecting portions 24 and 25, and the inclined portions of the third and fourth corrugated fins 13c and 13d are the first. It can be tilted sufficiently with respect to the direction.

  For example, the inclination angle of the inclined portions 33 and 34 with respect to the first direction may be 70 ° or less (in other words, the inclination angle of the inclined portions 33 and 34 with respect to the second direction is 20 ° or more). The inclination angle of the inclined portions 33 and 34 with respect to the first direction may be 60 ° or less, may be 50 ° or less, and may be 45 ° or less. From a different point of view, the inclination angle of the inclined parts 33 and 34 with respect to the second direction may be 30 ° or more, 40 ° or more, or 45 ° or more. If the heat exchanger 1 is arranged so that the first direction is the vertical direction, dew condensation water is generated in the inclined portions 33 and 34 inclined with respect to the first direction in the first and second corrugated fins 13a and 13b. It can easily flow downward. Similarly, the dew condensation water can easily flow downward in the inclined portions of the third and fourth corrugated fins 13c and 13d. Therefore, the drainage at the corrugated fins 13 in the heat exchanger 1 can be enhanced.

  In the heat exchanger 1, the hydrophilicity of at least part of the surfaces of the first plate fins 12a, the second plate fins 12b, and the at least one heat transfer tube 11 is such that the first corrugated fins 13a and the second It is higher than the hydrophilicity of the surface of the corrugated fin 13b. For this reason, dew condensation water can be easily moved from the surface of the 1st and 2nd corrugated fin 13a, 13b to the 1st and 2nd plate fin 12a, 12b or the surface of the heat exchanger tube 11. And the dew condensation water which moved to the 1st and 2nd plate fins 12a and 12b or the heat exchanger tube 11 can move to the perpendicular downward direction easily, for example. For this reason, the drainage property in a heat exchanger can be improved.

  In the heat exchanger 1, the thickness W of at least one heat transfer tube 11 in the second direction indicated by the arrow 16 in FIG. 3 is thicker than the thickness of the first and second plate fins 12a and 12b. The thicknesses of the first and second plate fins 12a and 12b are thicker than the thicknesses of the first and second corrugated fins 13a and 13b. If it says from a different viewpoint, the thickness of the 1st-3rd plate fins 12a-12c is thicker than the thickness of the 1st-4th corrugated fins 13a-13d which are all the corrugated fins 13. FIG. Thus, since the thickness of the plate fin 12 is thicker than the thickness of the corrugated fin 13, the strength of the plate fin 12 can be increased and the shape of the heat exchanger can be stabilized.

  In the heat exchanger 1, the positions of the plurality of first connection portions 24 overlap the positions of the plurality of second connection portions 25 in the first direction. Also, in the second and third plate fins 13b and 13c, the second corrugated fin 13b and the third corrugated fin 13c or the third corrugated fin 13c and the fourth corrugated so as to sandwich each of them. The position of the connection portion between the fin 13d and the plate fin overlaps in the first direction. If it does in this way, the position of the connection part in the front and back in the plate fin 12 will overlap, and the shape of the plate fin 12 can be stabilized compared with the case where the position of the said connection part differs in the front and back.

Embodiment 2. FIG.
<Configuration of heat exchanger>
FIG. 4 is a partial cross-sectional schematic diagram of a heat exchanger according to Embodiment 2 of the present invention. FIG. 4 corresponds to a partial schematic cross-sectional view of the heat exchanger in a plane perpendicular to the first direction shown in FIG.

  The heat exchanger shown in FIG. 4 basically has the same configuration as the heat exchanger shown in FIGS. 1 to 3, but the first to third plate fins 12 a to 12 c and the first to fourth plates. The shape of the corrugated fins 13a to 13d is different from that of the heat exchanger shown in FIGS. Specifically, the width L2 of the first to fourth corrugated fins 13a to 13d is larger than the width L1 of the heat transfer tube 11 in the air flow direction indicated by the arrow 22. Moreover, the 1st-4th corrugated fins 13a-13d contain the part 27 which protrudes from the heat exchanger tube 11 toward the upstream of the distribution direction of air. Furthermore, in the air flow direction, the width L3 of the first to third plate fins 12a to 12c is larger than the width L2 of the first to fourth corrugated fins 13a to 13d. Moreover, the 1st-3rd plate fins 12a-12c contain the part 26 which protrudes from the 1st-4th corrugated fins 13a-13d toward the upstream of the distribution direction of air.

  Speaking from the different viewpoints of the configuration of the heat exchanger described above, in the heat exchanger 1, the air flow direction is a direction perpendicular to the first direction and the second direction, and is indicated by an arrow 22 in FIG. Direction. In the air flow direction, the width L3 of the first and second plate fins 12a, 12b is larger than the width L2 of the first and second corrugated fins 13a, 13b. From a different point of view, the width L3 of the first to third plate fins 12a to 12c, which are the plurality of plate fins disposed between the two heat transfer tubes 11, is disposed adjacent to the plurality of plate fins. It is larger than the width L2 of the first to fourth corrugated fins 13a to 13d which are a plurality of corrugated fins.

  In the heat exchanger 1, a part 26 of the first and second plate fins 12a and 12b protrudes more upstream in the air flow direction than the first and second corrugated fins 13a and 13b. Similarly, the third plate fin 12c includes a portion 26. That is, a portion 26 of the first to third plate fins 12a to 12c, which are a plurality of plate fins, is upstream of the first to fourth corrugated fins 13a to 13d, which are a plurality of corrugated fins, in the air flow direction. Protruding. Further, in the heat exchanger 1, the first and second corrugated fins 13 a, 13 b have a portion 27 that protrudes upstream from the at least one heat transfer tube 11 in the air flow direction. That is, a portion 27 of the first to fourth corrugated fins 13 a to 13 d which are a plurality of corrugated fins protrudes upstream from at least one heat transfer tube 11.

  A louver 23 is formed on the first to fourth corrugated fins 13a to 13d. The louver 23 is formed in the inclined parts 33 and 34 (refer FIG. 3) in the 1st-4th corrugated fins 13a-13d. The louver 23 is formed to extend linearly in a direction intersecting with the air flow direction, specifically, in a direction perpendicular to the air flow direction. The planar shape of the louver 23 is linear, but may be curved. For example, the louver 23 cuts the inclined portions 33 and 34 of the first to fourth corrugated fins 13a to 13d, and inclines part of the inclined portions 33 and 34 adjacent to the cut with respect to other portions. It may be formed by causing to. Further, a slit as a simple opening may be formed in place of the louver 23.

<Operation and effect of heat exchanger>
Consider the case where the heat exchanger 1 acts as an evaporator. In this case, a low-temperature refrigerant flows through the refrigerant flow path formed in the heat transfer tube 11. Therefore, the heat transfer tube 11, the first corrugated fin 13a joined to the heat transfer tube 11, the plate fin 12a joined to the first corrugated fin 13a, and the second corrugated fin joined to the plate fin 12a. Heat is transferred in the order of 13b and the second plate fin 12b joined to the second corrugated fin 13b. Since the low-temperature refrigerant flows through the heat transfer tube 11 as described above, the surface temperature of the heat exchanger increases as the distance from the heat transfer tube 11 increases.

  When air is supplied to the heat exchanger 1, the air passes from the windward side of the heat exchanger 1 through a gap formed by the heat transfer tubes 11, the plate fins 12, and the corrugated fins 13 of the heat exchanger 1. At this time, heat is exchanged in order from the part close to the windward, and the temperature decreases. When the temperature of the air decreases and falls below the dew point, moisture in the air condenses and adheres to the heat exchanger surface as condensed water. Here, condensed water begins to adhere from the first to third plate fins 12a to 12c having the longest distance from the heat transfer tube 11 of the heat exchanger and the highest temperature. Thereafter, the air temperature further decreases when the first to fourth corrugated fins 13a to 13d pass, and condensed water adheres to the first to fourth corrugated fins 13a to 13d.

  In the conventional heat exchanger, most of the condensed water is attached to the corrugated fins, whereas in the heat exchanger according to the present embodiment, most of the condensed water is the first to third plate fins 12a to 12a. 12c can be attached. The first to third plate fins 12a to 12c have a portion 26 that protrudes further to the windward side than the first to fourth corrugated fins 13a to 13d. Since the portion 26 does not have an obstacle below, the condensed moisture flows on the surface of the portion 26 of the first to third plate fins 12a to 12c and falls downward in a short time.

  On the other hand, the condensed water (moisture) condensed on the first to fourth corrugated fins 13a to 13d is guided downward by the louver 23 formed in the first to fourth corrugated fins 13a to 13d. Drops downward along the shape of In the conventional corrugated fin, since the inclination with respect to the 1st direction of the surface part in which the louver of the corrugated fin was formed is relatively small, the dew condensation water may not move sufficiently along the corrugated fin. However, in the heat exchanger according to the present embodiment, the inclination of the inclined portions 33 and 34 of the first to fourth corrugated fins 13a to 13d with respect to the second direction is ensured, for example, by 20 ° or more. For this reason, dew condensation water can be easily moved downward along the inclined portions 33 and 34.

  In the said heat exchanger 1, the effect similar to the heat exchanger in Embodiment 1 can be acquired. Furthermore, in the heat exchanger 1, the width L3 of the first to third plate fins 12a to 12c, which are a plurality of plate fins arranged between the two heat transfer tubes 11, is adjacent to the plurality of plate fins. It is larger than the width L2 of the first to fourth corrugated fins 13a to 13d, which are a plurality of corrugated fins arranged in a row.

  In this case, the first to third plate fins 12 a to 12 c include a portion 26 protruding from the first to fourth corrugated fins 13 a to 13 d in the air flow direction indicated by the arrow 22. The protruding portion 26 extends along the first direction, and can function as a drainage path for condensed water from the first to fourth corrugated fins 13a to 13d.

  Moreover, dew condensation water adheres early in the part 26 of the 1st-3rd plate fins 12a-12c protruded to the upstream in the distribution direction of air. Thereafter, the condensed water can be quickly moved below the first and second plate fins 12a and 12b via the portion 26 of the first and second plate fins 12a and 12b.

Embodiment 3 FIG.
<Configuration of heat exchanger>
FIG. 5 is a partial cross-sectional schematic diagram of a heat exchanger according to Embodiment 3 of the present invention. 6 is a partial perspective schematic view of the heat exchanger shown in FIG. FIG. 7 is a partial top schematic view of the heat exchanger shown in FIG.

  The heat exchanger shown in FIGS. 5 to 7 basically has the same configuration as that of the heat exchanger shown in FIG. 4, but the plate member 14 is provided upstream of the heat transfer tube 11 in the air flow direction. The connection point and the arrangement of the louvers 23 are different from the heat exchanger shown in FIG. Specifically, in the heat exchanger shown in FIGS. 5 to 7, the plate member 14 is disposed so as to be connected to the windward end portion 28 which is the upstream side in the air flow direction in the heat transfer tube 11. ing. The plate member 14 may be a hollow member, for example, but may be a solid member. The width of the plate member 14 in the second direction (the direction indicated by the arrow 16 in FIG. 3) may be the same as the width W of the heat transfer tube 11 (see FIG. 3). The total width of the heat transfer tube 11 and the plate member 14 in the air flow direction is the same as the width L3 of the first to third plate fins 12a to 12c. The total width of the heat transfer tube 11 and the plate member 14 may be different from the width L3 of the first to third plate fins 12a to 12c, for example, the width of the first to fourth corrugated fins 13a to 13d. It may be the same as L2.

  The first to fourth corrugated fins 13 a to 13 d include inclined portions 33 and 34. A plurality of louvers 23 are formed in the inclined portions 33 and 34. The inclined portions 33 and 34 are inclined with respect to the first direction which is the vertical direction. A plurality of louvers 23 extending linearly are formed on the inclined portions 33 and 34. The plurality of louvers 23 are formed to extend downward in the vertical direction toward the upstream side in the air flow direction indicated by the arrow 22. That is, as shown in FIG. 6, the louver 23 in the inclined portion 33 is formed so as to approach the protruding portion apex 36 from the connecting portion 25 as it goes upstream in the air flow direction. Moreover, although not shown in figure, the louver in the inclination part 34 is formed so that it may approach the connection part 25 from the protrusion part vertex 36 as it goes to the upstream of the distribution direction of air.

  From a different point of view, in the heat exchanger 1, the first direction is a direction along the direction of gravity. The 1st corrugated fin 13a is located between the some 1st connection parts 24 (refer FIG. 3), and contains the 1st inclination parts 33 and 34 inclined with respect to the perpendicular direction. The 2nd corrugated fin 13b is located between the some 2nd connection parts 25, and contains the 2nd inclination parts 33 and 34 inclined with respect to the perpendicular direction. At least one louver 23 extending linearly is formed on at least one of the first inclined portion and the second inclined portions 33 and 34. At least one louver 23 is formed to extend downward in the vertical direction as it goes upstream in the air flow direction indicated by arrow 22.

  In addition, although the louver 23 is formed in all the inclination parts 33 and 34 of the 1st-4th corrugated fins 13a-13d, it may be formed only in one part inclination part 33,34. Moreover, you may form in some 1st-4th corrugated fins 13a-13d.

<Effects of heat exchanger>
In the said heat exchanger 1, the effect similar to the heat exchanger in Embodiment 2 can be acquired. Furthermore, the heat exchanger 1 further includes a plate member 14 connected to a portion of the at least one heat transfer tube 11 located on the upstream side in the air flow direction. By connecting such a plate member 14 to the heat transfer tube 11, frost that has been attached to the heat transfer tube 11 in the past can be dispersed and attached to the plate member 14. For this reason, the amount of frost formation in the heat exchanger tube 11 can be reduced, and the drainage of the heat exchanger tube 11 can be improved as a result.

  Further, the louver 23 in the heat exchanger shown in FIGS. 5 to 7 is formed so as to extend downward in the vertical direction toward the upstream side in the air circulation direction. Condensed water adhering to the surface can be guided upstream in the air flow direction. Since the part 26 of the 1st-3rd plate fins 12a-12c is arrange | positioned in the said upstream side, the drainage property of a heat exchanger can be improved by utilizing the said part 26 as a drainage path.

Embodiment 4 FIG.
<Configuration of air conditioner>
FIG. 8 is a schematic diagram showing a refrigerant circuit of an air-conditioning apparatus according to Embodiment 4 of the present invention. The refrigerant circuit shown in FIG. 8 includes a compressor 41, a first heat exchanger 42 that acts as a condenser, a throttle device 43 that acts as an expansion valve, a second heat exchanger 44 that acts as an evaporator, and two blowers 45. Prepare. The two blowers 45 are each driven by a blower motor 46. The two blowers 45 blow gas (for example, air) to either the first heat exchanger 42 or the second heat exchanger 44, respectively. In the refrigerant circuit, the refrigerant circulates in the order of the compressor 41, the first heat exchanger 42, the expansion device 43, and the second heat exchanger 44. From a different point of view, the air-conditioning apparatus shown in FIG. 8 includes a compressor 41, a first heat exchanger 42, a throttle device 43 as an expansion valve, and a second heat exchanger 44, and the refrigerant in which the refrigerant circulates. Provide circuit.

  At least one of the first heat exchanger 42 and the second heat exchanger 44 illustrated in FIG. 8 is the heat exchanger described in any one of the first to third embodiments. The blower 45 blows gas to each heat exchanger along the third direction (the direction indicated by the arrow 22 in FIG. 4). In addition, by arranging a four-way valve or the like in the refrigerant circuit, the refrigerant flow direction in the first heat exchanger 42 and the second heat exchanger 44 in the refrigerant circuit is reversed from the direction shown in FIG. The exchanger may act as an evaporator and the second heat exchanger may act as a condenser.

<Operation effect of air conditioner>
Since the air conditioner according to the present disclosure is a heat exchanger according to any one of Embodiments 1 to 3 described above as a heat exchanger, it has sufficient drainage. Therefore, in the first and second heat exchangers 42 and 44, it is possible to suppress a decrease in efficiency and occurrence of problems due to insufficient discharge of condensed water.

  Although the embodiment of the present invention has been described above, the above-described embodiment can be variously modified. The scope of the present invention is not limited to the above-described embodiment. The scope of the present invention is defined by the terms of the claims, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

  The present invention can be applied to an air conditioner, a refrigeration cycle apparatus, a heat pump apparatus, and the like.

  DESCRIPTION OF SYMBOLS 1 Heat exchanger, 2 Upper header, 3 Lower header, 10 Main-body part, 11 Heat exchanger tube, 12 Plate fin, 12a 1st plate fin, 12b 2nd plate fin, 12c 3rd plate fin, 13 Corrugated fin, 13a 1st corrugated fin, 13b 2nd corrugated fin, 13c 3rd corrugated fin, 13d 4th corrugated fin, 14 plate member, 15, 16, 22 arrow, 23 louver, 24 1st connection part, 25 2nd connection part, 26, 27 part, 28 end part, 33 1st inclination part, 34 2nd inclination part, 36 protrusion part vertex, 41 compressor, 42 1st heat exchanger, 43 expansion device, 44 Second heat exchanger, 45 blower, 46 blower motor.

In the heat exchanger 1, the positions of the plurality of first connection portions 24 overlap the positions of the plurality of second connection portions 25 in the first direction. Also in the second and third plate fins 1 2 b, 1 2 c, the second corrugated fins 13b and the third corrugated fins 13c which are arranged so as to sandwich the respective or third corrugated fin 13c, and The position of the connection portion between the fourth corrugated fin 13d and the plate fin overlaps in the first direction. If it does in this way, the shape of the plate fin 12 can be stabilized more than the case where the position of the said connection part differs in front and back by the position of the connection part in the front and back in the plate fin 12 overlapping.

Claims (10)

At least one heat transfer tube extending in a first direction intersecting with the flow direction of the air and in which a refrigerant flows;
A first plate fin extending in the first direction and spaced apart from the at least one heat transfer tube in a second direction perpendicular to the first direction;
A second plate fin extending in the first direction and spaced apart from the first plate fin in the second direction by a second distance;
A first corrugated fin disposed between the at least one heat transfer tube and the first plate fin;
A second corrugated fin disposed between the first plate fin and the second plate fin;
The first plate fin and the first corrugated fin are connected by a plurality of first connecting portions arranged at a third interval in the first direction,
The first plate fin and the second corrugated fin are connected by a plurality of second connecting portions arranged at a fourth interval in the first direction,
The heat exchanger, wherein the third interval and the fourth interval are greater than the first interval and the second interval. The flow direction of the air is a direction perpendicular to the first direction and the second direction,
2. The heat exchanger according to claim 1, wherein a width of the first and second plate fins is greater than a width of the first and second corrugated fins in the air flow direction.   3. The heat exchanger according to claim 2, wherein a part of the first and second plate fins protrudes further upstream in the air flow direction than the first and second corrugated fins.   4. The heat exchanger according to claim 3, wherein a part of the first and second corrugated fins protrudes upstream of the at least one heat transfer tube in the air flow direction.   The heat exchanger according to any one of claims 2 to 4, further comprising a plate member connected to a portion located upstream of the at least one heat transfer tube in the air flow direction. The first direction is a direction along the direction of gravity;
The first corrugated fin is located between the plurality of first connecting portions, and includes a first inclined portion inclined with respect to the vertical direction,
The second corrugated fin is located between the plurality of second connecting portions, and includes a second inclined portion inclined with respect to the vertical direction,
At least one louver extending linearly is formed on at least one of the first inclined portion and the second inclined portion,
The heat exchanger according to any one of claims 1 to 5, wherein the at least one louver is formed so as to extend downward in the vertical direction toward an upstream side in a flow direction of the air. .   The hydrophobicity of at least part of the surfaces of the first plate fin, the second plate fin, and the at least one heat transfer tube is the hydrophobicity of the surfaces of the first corrugated fin and the second corrugated fin. The heat exchanger according to any one of claims 1 to 6, which is higher. A thickness of the at least one heat transfer tube in the second direction is greater than a thickness of the first and second plate fins;
The heat exchanger according to any one of claims 1 to 7, wherein the thicknesses of the first and second plate fins are thicker than thicknesses of the first and second corrugated fins.   9. The heat according to claim 1, wherein, in the first direction, positions of the plurality of first connection portions overlap positions of the plurality of second connection portions. Exchanger. A refrigerant circuit including a compressor, a first heat exchanger, an expansion valve, and a second heat exchanger, in which the refrigerant circulates;
The air conditioning apparatus in which at least one of the first heat exchanger and the second heat exchanger is the heat exchanger according to any one of claims 1 to 9.

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